TORQUE LIMITING SERVOMECHANISM

Abstract: It comprises a mechanical power input (1, 55) receiving the power preferably from an electric motor and a mechanical power output (3, 67), as well as transfer means (2, 2', 2'', 2''', 4, 64) for transferring this power from the input to the output, and control means (2, 5, 6, 7, 59, 60, 61) for controlling the transfer means (2, 4, 64) to make sure that the power transferred at the output does not exceed a predetermined level. There are provided means to break down the power received at the input into a power applied at the output (3, 67) and excess power which is used to produce the cut-off of power supplied by the motor. This excess power is controlled by the pressure of element (6, 7, 61) whose tension is adjustable which actuates against a movable surface which defines a cam profile, thereby increasing the force or torque during the angular or linear motion of the cam (2, 2', 2'', 2'''). The transfer mechanism includes a basic group with four different output alternatives (C1, C2, C3 and C4).

Description: OBJECT OF THE INVENTION The present invention refers to a mechanical-kinetic servomechanism for instant limitation and retention of torque or stress transmitted from an input shaft or mechanism to an output, which, applied to operations of valves or other uses, makes it possible to control the problems of electric or electronic signal delay and of accumulated inertia, even managing to take advantage of them for other uses. This invention is mainly developed directed towards bypass and fluid shutoff valves, where the variety of the same and circunstances of the process require certain characteristics. However, this does not mean that we limit the possible scope of application to said field, but rather said invention or any dervivation of the same can be applied to any other technical field in which a limitation of torque transmitted with certain characteristics (explained hereinafter) is required. Said servomechanism has a series of relevant and advantageous features with regard to other mechanism used at this time for the same purpose, and it has the following particularities: a) The conversion of manual power (by means of a handwheel, lever, etc.) or electric, pneumatic, hydraulic power (by means of cylinders, turbines or motors depending on the case) into mechanical power, adjusting and/or limiting the latter in a very precise manner. This precision allows, whatever the speed is, not to exceed the specific pressure of the seat in seated valves and gate valves and, additionally, in the latter, not to create any variability in the shutoff valves. b) The use of a gear planetary mechanism wherein the movement which enters through one of the center wheels while the other one is braked, comes out through the planetary member holder arm, or when the planetary member holder is breaked, comes out through one of the wheels controlling the excess power. Upon reaching a predetermined torque, the planetary member holder wheels stop or vice versa and the breaked wheel is released, causing the applied power to be put off.A shaft provided with thread or the like may be used. The shaft moves axially and acts on a truncated-cone shaped cam portion that causes the cutoff of the energy when a predetermined torque is exceeded.As of then, it is possible that the power of the motor, as well as the associated kinetic and elastic energies, do not have any effect on the element on which said energies have been applied up to then.This initially predetermined torque attained is the sum of a mechanical torque supplied by the motor, and the available kinetic torque due to the inertia of the motor itself and of the masses in movement, which makes it possible to apply much smaller motors; even to add additional inertia masses so as to increase said available kinetic energy. c) The use of an auxiliary flywheel or lever, in the case of an emergency or for sporadic needs, in such a way that the normal energy supply has preference over the manual supply and with the particularity that the engaging and disengaging lever is not necessary, which not only avoids accidents due to lacks of synchronism, but also it reduces in critical emergency circumstances, the idle times for preparing the operation. d) The centrifugal clutch which, aside from having the flywheel connected in a state of rest of the motor, when the latter is connected the clutch disconnects the flywheel and, passing through neutral, connects the motor with the input shaft of the planetary element of the mechanism almost at a rated speed. d') Taking advantage of the centifugal clutch or similar centrifugal mechanism to achieve self-regulation of the locking of the torque limiting and regulating group. Thus it is achieved that in terms of the speed more or less torque is given in order to achieve the instant release of the circumstantially movable part. e) Using a high yield irreversibility mechanism in those cases in which said irreversibility is not ensured in the rest of the actuator-valve mechanism, or in those cases in which it is desired to have ensured irreversibility. This irreversibility mechanism makes it possible to keep a general high yield upon allowing the reversibility of other elements of the actuator-valve unit. f) Using the mechanical control locking, either manual, or else automatic mechanical or electric, electronic, magnetic, pneumatic, hydraulic, or in combination of the first of them with each one of the remaining ones, to bridge the mechanical torque limiters. The function of manual locking, in emergencies, is that of using the maximum available torque once or twice, to accumulate through the irreversibility mechanism as much of said maximum torque as required. The task of mechanical automatic control locking is that of bridging the mechanical torque limiter so that selectively, the available maximum torque can be used during the preestablished period or periods. g) In the event that the flywheel, clutch and locking are going to be mounted simultaneously in the servomechanism, that it is possible to obtain powers higher than those produced by the maximum torque of the motor, without the need of successive starting, due to use of the centrifugal clutch. In effect, upon reaching the maximum torque and reducing the number of revolutions, the motor is disengaged and without stopping, although it is already rotating off-circuit, it recovers the speed until it is engaged again, providing again kinetic energy aside from the maximum mechanical torque.This operation can be repeated as many times as required, being limited by the heating of the motor. h) The general checking of torques, in all of the intermediate elements, by means of the circumstantially movable part and upon that one being released, obtaining data by direct mechanical, electric, electronic measuring, or else by means of a microprocessor, a computer and a printer. i) The specific and very precise checkings of stresses on the outlet rod of the mechanism, for direct actuation of the valve or other actuated element, by including in the mechanism a charging cell for direct mechanical, electric, electronic, measuring etc., or by indirect measuring and graphing by means of a microprocessor, a computer and a printer. j) Converting circular movements into rectilinear movements by coupling the outlet nut of the mechanism in an intermediate spindle with double thread (male and female, one inside and the other outside), until the integral stop of both, wherein the thread of this spindle acts as a helicoidal cottwerway of the spindle of the valve or other actuated element, threaded with a smaller diameter and pitch than the thread of the nut, whereby upon reducing the speed of movement, with the same output torque a stress four or five times greater is achieved, in other words, multiplying power is achieved. k) Automatic retightening of the packing, in all the equipment or apparatus where it is so required, by means of including two elastic elements between which is installed, in a floating manner, the output nut of the mechanism (charging cell), which turning in one direction or the other depending on the direction of movement of the spindle, the nut moving proportionally to the force produced by the pressure of the packing. With the progressive wear of the packing there is a reduction of the passive force and with this, a signal to the electric clutch or to another second actuator mechanism, the latter being responsible for automatic retightening of the packing, the grip torque having the possibility of being limited and adjusted, as we will see later on. l) As accidental breakage of the microswitch of the torque limiting mechanism not affects the integrity of the actuator mechanism as well as of the element actuated by the latter, there is no need of any additional limit switch. This is due to the particularity mentioned above in point b) upon mechanically disconnecting (without any electric, electronic, magnetic dependency, etc.) the application of power of the motor and the associated kinetic energy, to the element to which such energies are applied. These excess energies are absorbed as work by torques equal to or smaller than the maximum cutoff torque, and they can be used for other purposes, (signalling, self-checking, etc.)Thus, in the event that the microswitch of the torque limiting mechanism breaks, the motor will continue to work, with the associated kinetic energies thereof, but without managing at any moment to transmit them to the final or output element.It will be this way until the thermal switches of the motors disconnect it due to overheating.Given that the latter would greatly shorten the life of the actuator or mechanism to transfer mechanical power, it is why a torque limiting mechanism microswitch is used. Its purpose is only to protect the motor against heating up and thus to reduce times between consecutive operations; but without thus protecting the integrity of the entire actuating mechanism. The valve or actuated element already remains assured by said damping and control of the above mentioned excess energies (motor power and kinetic energy).As it is inferred from the above, the mechanism of the proposed invention is useful in industry in general and particularly in the operation of flow control valves and fluid shutoff valves, robotics, machine-tools, conveyor belts and pushing cylinders, among others. These operations can be done directly or else by reducers, couplings, nuts, transmissions and other known devices. m) Having a regulated maximum torque that is self-adjustable in terms of the speed that said mechanism requires. As it will be seen in the description of the invention, several embodiments are possible to obtain a servomechanism that has such characteristics. BACKGROUND OF THE INVENTION The actuators or actuation mechanisms to transfer mechanical power from one input to an output, existing on the market, generally include a floating endless worm system, resting on its ends by elastic elements and a wheel that, upon turning, when it comes up against an obstacle or reaches the end of its run, the worm moves cutting off the current from the motor. The actuation mechanisms have a series of inconveniences that will be stated hereinafter, determined by the basic concept of embodiment that they apply and which have been tried to be solved in very different ways, though without attacking said basic concept of embodiment. As it is specified in WO-A-92/01884, upon sizing an action regulator (actuator) for valves it is necessary to take into account certain factors. On the one hand, due to defects, aging or defective maintenance (such as corrosion of the spindle, wear or excess tightening of the packing etc.) the turning torque needed to close the valve may increase considerably (for example from 30 to 80 Nm.) On the other hand, upon sizing the action regulator (actuator) said value (80 Nm) must be taken into account in unfavorable operating conditions of the actuator itself (a voltage drop in the line, tolerances, temperature of the motor, etc.) In this way the actuator in oppositely unfavorable conditions, there may be a supply of 10 times more theoretical turning torque than that which is needed (30 to 300 Nm), in the event that the dependent torque disconnection were to fail. This may seriously affect the actuated mechanism (valve, in this case), even managing to make it unserviceable. The solution provided by WO-A-92/01884 is that of a braking frame of the spindle of the valve that acts from a given maximum torque, preventing this to reach the extreme of 300 Nm in the event of failure of the control switches. With this solution the effect is reduced but the problem that causes said effect is not solved. In order to try to overcome this effect (aside from others), actuator manufacturers include an additional microswitch, with a path (intentionally) synchronized (path limiter) with the torque limiter. Said synchronization disappears as soon as there are minimal temperature variations, once again posing the problem of destroying the valve. In the event that there is no failure in the control switches, these actuators have two inconveniences that can lead, at average and high output speeds (100 to 300 nm/min., according to the type of valve), to reach excess output torque values much higher than the values pre-set by said control switches. This excess output torque likewise manages to cause significant damage to the actuated valve. As is stated in "Bulletin FC-77 of Limitorque Corp., said inconveniences are: 1) It does not provide for a release of inertia from the mechanism. In this way excess pressure in the seat of the valve and excess stresses on the rod are created. These anomalies are increased up to significant values when the output speed of the actuator increases. This all makes it necessary to limit the output speeds of actuators. For example in ON/OFF (open loop) valves the speeds of the rod are limited to 300 mm/min for gate valves and to 100 mm/min for globe valves, running the risk of damaging the valve, despite said limitations. At times, it is even essential to equip the actuator with a second high speed motor, so that in the cases of a serious emergency, the output speed increases considerably, even knowingly that this will lead to the destruction of the seat and great damage to the valve. In adjustment and shutoff valves, the need of very powerful motors for the shutting itself, involves an increase of the inertia, which requires a reduction of the speed to maintain the precision of the adjustment, sacrificing the response speed, even in some cases, requiring the need of two valves, an adjustment valve and a. shutoff valve, for said tasks. 2) These problems of excess pressures are increased upon additionally considering the electric signal delay of between 20 and 50 ms, that exists between the signal of the switch of the torque limiter and the energization of the motor operating and stopping contactors. Besides, this anomaly is inevitable and does not depend on the output speed of ther actuator but rather on the electric system used. Its effect (increase of torque above the adjusted one) simply is significant at average and high actuator output speeds (100 to 300 mm/min.). These two anomalies are produced upon the motor and the other elements of the actuator being permanently mechanically linked up to the output, either by worm-wheel embodiment or else in other embodiments used less but also with the same principles. Within all of them the main problem is that of deflecting and/or absorbing the excess power from the instant of the jump of the torque limitation and to dissipate it in a sure manner and without affecting the limited torque.Within these embodiments is Bernard's French patent FR 2699983-A1 that uses a planetary reducing mechanism to limit, in its outside crown and by means of adjustable springs, the transmitted torque.Despite the novelty of this actioning against the "classic" worm-wheel, it does not solve its problems. The inertias accumulated at high speeds are still not released and the signal delay times keep affecting it in the same way.In the moment that the torque control switch is actuated, previously adjusted to a maximum necessary torque, the signal delay and the inertia (if they are important) make the regulating springs continue to tighten accumalatively and thus a torque greater than the adjusted one to the output shaft of the actuator is transmitted.Practically the same solutions, when limiting the transmitted torque, are applied by German patent DE-A-3010019.U.S. patent US-A-3921264 also deals with a mechanism formed by two planetary reducers. In one of them the outside crown remains fixed by means of a solenoid that is energized in parallel with the motor. When the motor is disconnected, the current stops reaching said solenoid and, therefore, it totally releases the crown or outer wheel of the planetary element. In this way no torque is transmitted by means of the planetary reducer as of this moment.This embodiment does not solve the problem of electric delay but rather it even makes it worse by using an electrically excited solenoid. Once this delay has taken place, the torque transmission is totally disconnected, the problem of accumulated inertia being avoided. In any case, this would only serve to "absorb" accumulated inertia of limitated value since, on the contrary, the outside crown would be kept turning with too much accumulated kinetic energy and the electric signal delay would be even greater than the normal one, with the problems that this involves.Other inconveniences and anomalies, other than the above cited ones, that said actuators generally have are: 3) Needing an additional manual engaging-disengaging lever to carry out the same functions. In this group Japanese patent JP-60 018 679, that needs a lever that turns its coupling-decoupling element, would be included. 4) The operator needs to use both hands together, having to feel out the above cited lever with one hand, while turning the flywheel with the other hand trying to fit the spaces of the flywheel with the teeth of the intermediate wheel, after having deblocked the motor. After having fit the teeth in the spaces, it is then possible to operate with the flywheel.The flywheel is likewise used to tune up the position limiter of the actuator mechanism with which the mechanical power is transferred from an input to an output.This position limitation needs great precision since in the event that the microswitch of the torque limiting mechanism becomes unservicable, theoretically, the microswitch of the position limiting mechanism is the one responsible for disconnecting the motor to prevent the deterioration of the valve and/or of the actuator mechanism itself. 5) There is no mechanical manual nor automatic blocking. In the event that this were installed, in conventional actuators, it could not be used because of the permanent mechanical link, already described above, between the motor and the remaining components of the actuator. 6) Stresses higher than those produced by the maximum torque cannot be obtained, without stopping the motor, as there is no centrifugal clutch or multiplier. 7) There is no irreversibility mechanism. This irreversibility, in most motorized valves is ensured by the rod and/or nut of the valve (or of the actuator mechanism) that tends to be irreversible and with a low mechanical efficiency. This limits the overall efficiency of the unit and prevents use of more efficient rods and nuts (longer pitches and ball spindles) that, by definition would be reversible. 8) The need of costly preparation times of the valve and of the actuator mechanism to be able to make timely checks of the stresses in the spindle. 9) Likewise, these costly preparation times are needed to be able to check the actuator internally. 10) The need to sacrifice the high speed to obtain great torques at the output of the actuator, or else, the need to use a two speed motor or one with an electric brake. 11) The sporadic and cyclic presence of an operator to retighten the packing by hand and to control these tightening pressures; being able to destroy the packing by exceeding its limit tightening pressure, being able to even ,at times, brake the movement of the spindle, increasing in these cases the passive stresses that would regulate the correct operation of the actuator-valve unit preventing the correct closing of the valve and thus its wear and tear. 12) Having a regulated maximum torque that is independent of the turning speed of the mechanism. GB-A-655 956 discloses a mechanism substantially corresponding to the preamble of claim 1 of the instant patent. DESCRIPTION OF THE INVENTION In broad outline, the mechanical-kinetic servomechanism for instant limitation and retention of the torque or stress transmitted by an input shaft or mechanism to an output one, as defined in claim 1 of the instant patent, can be described as follows: Mechanical power and its corresponding kinetic energy is received from a motor or input shaft, transferring one part of the energy received to an output and there being some control means so that the power transferred to the output does not exceed a certain level. According to the invention, the power received at the input is broken down into: energy applied to an output to actuate equipment such as a valve or other device and excess power that is used to achieve a relative movement between a contact element and a surface with a suitable geometric profile of a circumstantially movable part. The contact element transmits a pressure assisted by a torque limiting and regulating group and the movement of the outside configuration of the circumstantially movable part (angular, axial or compound depending on the constitution thereof) determines a more or less progressive increase of the pressure depending on the form adopted for said configuration braking the excess power, once there has been a cutoff of the power of the motor as a result of this movement beginning. Said power cutoff at the input of the output of the mechanism is instant and sudden. This mechanism can be considered comprised of three parts or modules. The first and most important part is the input of the mechanism. The second one is between the first one and the motor and can optionally include a centrifugal clutch and manual control. Finally, the third part corresponds to the output of the mechanism and connection with the actuated element, it being able to have four different variants. These three considered parts have independent functionality of their own and can comprise perfectly differentiated modules, while when they are presented grouped together, for reaons of manufacturing and practical use, basically, they comprise a single module. To the same independent or grouped parts one can add a series of additional devices, in multiple combinations that will be described later on, which also have in turn the particularity of being able to comprise independent modules. Although hereinafter and in connection with the attached figures one will be clearly able to see the structure of the three component parts and their corresponding additional devices, they are diagrammed hereinafter, with the respective breaking down into groups and the descriptions of the main parts comprising the latter, all of them identified with letters and numbers (diagram 1). The numbers and letters here correspond with those of the figures shown in the examples of the preferred embodiment to provide a better understanding of the diagram and figures that are selected as an example and for a better understanding of the description though they must not be considered as restrictive but rather the interpretation thereof must be considered in the broadest sense. Due to the integrating nature of this this mechanism proposed by the invention, it is possible to use it individually or all the possible logical combinations between modules, basic groups and additional devices, such as to form a manual as well as motorized actuator mechanism, for the individual application thereof or for combined use with other types of actuators already known, giving them therefore an integrating nature, considering all the possibilities in the broadest and never restrictive manner. As to the irreversibility mechanism, we can say that it defines a irreversibility module that can be placed in different positions within the combined transfer mechanism. Thus, it can be included in the input module, or between said module and the intermediate module, or between the intermediate module and the output module or inside the output module. Said irreversibility module is used to retain the circumstantial or final stopping, as well as the transmitted stress. Said irreversibility mechanism, combined with the centrifugal clutch, also makes it possible to obtain higher stresses due to successive accumulations of kinetic energy in the motor; this curve being higher than the one produced by the maximum torque. In the input module there are different solutions regarding how to limit the transmission of the torque from the input shaft or mechanism to the output one. All of them are based on a circumstantially movable part that is normally braked by a fixed or movable torque limiting and regulating group. This torque limiting and regulating element is formed by some elastic elements that apply their pressure against the outside configuration of said circumstantially movable part by means of one or several contact elements, in such a way tnat upon exceeding a pre-set torque said circumstantially movable part is released, beginning its relative movement and, due to its configuration, causing the instant cutoff of input power by means of a device included for said purpose. The (geometric) outside configuration of said circumstantially movable part may vary greatly, said configuration depending on the way that one wishes to dampen, take advantage of or measure the excess energy of the mechanism. The different solutions for said input module vary in what regards the shape of the circumstantially movable part and the relative movement that the part acquires upon being released. Maintaining the same instant breakdown concept of the transmitted torque, releasing or taking advantage of the excess energy, upon said circumstantially movable part being released by said torque limiting group. In the first solution, the circumstantially movable part is the idle wheel of a planetary gear mechanism whose planetary elements or members gear in the inside part of said idle wheel. The idle wheel is normally braked by said torque limiting and regulating group. In the second solution said circumstantially movable part is the planetary element holder of a planetary gear mechanism, dragged by said planetary members and remaining normally braked by said torque limiting and regulating group. In these two solutions the movement that said circumstantially movable part acquires is a turn with regard to its own shaft and the torque limiting and regulating element applies its stress against the outside configuration of both parts. In a third solution the circumstantially movable part is a part with a predetermined shape that can only acquire longitudinal movement along its shaft, never rotation movement, being normally braked by said torque limiting and regulating group. In the last of the solutions presented, the circumstantially movable part is provided with a predetermined shape, similar to that of the previous solution. In this case its movement is normally turning movement, with longitudinal displacement when said part is released by the torque limiting and regulating group, that only prevents said longitudinal movement and not the turning movement, given that this element turns integrally with said part. With said particularity of the torque limiting and regulating group turning integrally with the circumstantially movable part, there is self-adjustment of said torque limiting and regulating group, upon varying the stress that the latter exerts on the circunstantially movable part in terms of the turning speed of both (in starting up, shutting off, clogging, etc.). A series of auxiliary or secondary devices that are activated upon said circumstantially movable part moving upon being released by the torque limiting and regulating group, have been provided for, depending on whether said movement is turning or not (current cutoff device, damping, measuring devices, etc.) A device that allows circumstantial locking of the movable part, avoiding its relative movement, has also been provided for. In the cases in which there is turning movement applied there is also an increase of the kinetic energy by means of including an inertia flywheel. It is also possible to include a locking adjustment mechanism that makes it possible to vary (and therefore adjust) the stress that the torque limiting and regulating group exerts on said circumstantially movable part in terms of a series of parameters. Hence, for example, it is achieved that when starting up there is a higher regulated torque than in other moments. Including an automatic centrifugal clutch connected to the motor, disengaging the energy flywheel and simultaneously carrying out the connection with the motor upon reaching the rated revolutions has been provided for. The irreversible element transmits the torque of the input shaft to the output shaft and during this transmission any movement of the output shaft is blocked in the contrary direction of rotation. It also foresees the inclusion of a group with a bushing that permits a checking of the output torque capturing of a signal by means of two concentric bushings with reversible thread, acting likewise as a helocoidal cotterway. The inside bushing rests on the elastic elements that allow it to move, this movement being used to generate a signal that indicates the variation of the passive forces. An increase of this force corresponds to a shorter run, that indicates an anomaly in the actuator mechanism or in the actuated equipmment, while a longer run corresponds to a reduction of the passive force. In the actuated equipment that has packing, this signal is taken advantage of to order retightening by means of an electroclutch or auxiliary actuator mechanism. Instead of the group with bushing one can add a floating nut group that allows checking of the thrust of the pressure exerted longitudinally by the spindle on the nut that commands it, the nut being floating in one or both ends, upon one or two elastic elements that allow it to move. Also by means of a multiplier group it is possible to achieve that, with the same output torque and revolutions of the actuator or reducer, one can convert circular movement of the main nut into linear movement, by means of a doubly threaded sleeve, the male in the main nut and the female in the end of the spindle, this being able to move but not turn. In this way, the threads can function alternatively as such, or else, as helicoidal cotterways depending on a rigid or flexible linking element, as well as some stops, resulting in greater speed and less stress in the linear movement of the spindle when the smaller thread acts as a helicoidal cotterway and the larger one as a thread and a smaller speed and greater force when both function reciprocally. Upon reversing the turning of the main nut the spindle is retracted by means of the smaller thread, and upon this thread stopping the speed of the spindle increases in its movement through the larger thread, until reaching its prefixed position remaining displaced to repeat the cycle completely or partially. To provide a better understanding of the features of the invention and forming an integral part of this specification, a series of drawings in whose figures the object of the invention has been represented in an illustrative and non-restrictive manner are attached hereto. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1a is a partially sectioned plan view of the input module. Figure 1b is a cross-section view of that which is shown in figure 1a. Figure 1c is cross-section view of the input module (a.1.) with the irreversiblility module (w) and the output module (f) assembled. Figure 2a is a sectioned view of the entire mechanism, on an actuated equipment. Figure 2b is a section along the B-B cut line of figure 2a. Figure 3.1. is a partial longitudinal view of the rotating output module (C1). Figure 3.2 is a sectioned view similar to that of figure 3.1 of the threaded output module (C2). Figure 3.3a is a longitudinal and corss-section partial view of the output module with the multiplier I (h), one being able to see how the greater thrust effect has been produced and the mechanism is ready to start the backward movement. Figure 3.3.b. is a view similar to that of figure 3.3a in which one can see how the thread with a smaller diameter becomes a helicoidal cotterway. Figure 3.3.c. is a view similar to figures 3.3a and 3.3b wherein one can see the instant in which the thread of the main nut becomes a helicoidal cotterway, while the thread of the small nut is no longer a cotterway and in its turning it moves the spindle longitudinally. Figure 3.4. is a sectioned view of the output module with a multiplier (II)-(C4). Figure 4.a. is a cross-section of the input module (a.2.) Figure 4.b. is a sectioned view of the whole mechanism, adopting said input module (a.2.). Figure 4.c. is a section along V-V line of figure 4b. Figure 5.a. is a cross-section of the input module (a.3.) including the motor (100) as a power input element of the mechanism. Figure 5.b. is a sectioned view of the mechanism unit, adopting input module (a.3.), multiplier 1 (h), irreversibility module (w), checking of the rod force (ϕ) and packing retightening signal (ε). Figure 5.c. is a cross-section view of the input module (a.3.), taking a shaft (71) as an input element instead of the motor (100). Figure 5.d. is a section along the A-A cut line of figures 5a and 5c. Figure 6.a. is a cross-section of the input module (a.4). Figure 6.b. is a sectioned view of the mechanism,adopting said input module (a.4.), the irreversibility module (w) and the motor (100). Figure 6.c. is a section along the Z-Z cut line of figure 6.b. Figure 6.d. is a section along the X-X cut line of figure 6.b. Figure 7.a. is a sectioned view of a unit in which a worm-wheel reducing mechanism has been adapted to the output of the input module (a.3.) DESCRIPTION OF THE PREFERRED EMBODIMENTS Making reference to the numbering used in the figures, we can see how the mechanism to tranfer mechanical power from an input to an output in a controllable manner, which the invention proposes, includes: INPUT MODULE A It is comprised of three basic components or groups: planetary group (a), torque limiting group (b) and driving power cutoff group (c). The planetary transmission group (a.1) consists of a planetary gear mechanism that has two (or more) center wheels (in figure 1, the pinion (1) and idle wheel (2), and at least a planetary element or member holder arm (3), with its corresponding planetary members (4) whose locations and functional characteristics (when the functional complexity thereof so requires) are described hereinafter. 1 - Pinion: pressed on the motor and gearing directly with the planetary pinions (4). 2- Idle wheel of the planetary mechanism, normally braked by one or several contact elements (pawls; in figure 1, only one, part (5) that is housed in a configuration (in figure 1, a notch) placed for this purpose in this idle wheel (2)) Other configurations of the periphery of this idle wheel (2) (in figure 1, an eccentric), that can be projections, grooves, etc., actuate one or several microswitches (9) by means of a pushing ball (8) and of the signalling stop (10). These latter configurations can be replaced by any mechanism and/or device that is capable of producing a signal (by means of cells, sensors or other systems.) Likewise, it can have other configurations or linking elements that produce the same effect and that are described as examples upon specifying in detail the additional devices of this figure 1. The outside configuration of the idle wheel (2) may be toothed, so that one or several of the pinions can acts as this idle wheel (2) with at least one curved surface either concentric, or eccentric, or in combination of both, cylindrical (or not) coaxial with the shaft thereof (or not), new configurations, notches and projections being able to be inserted in them; housings as well as notches and projections can be flat, circular, curved or with any other shape. The geometric outside configuration of the idle wheel may vary greatly, said configuration depending on the way that one wishes to dampen, take advantage of or measure the excess energy of the mechanism. 3 - Planetary element holders: Part (circular in the drawing) where planetary elements (4) are mounted and through which, in this case, the movement and the torque resulting from the planetary mechanism come out to the output shaft or element. The planetary group can include one or several arms. 4- Planetary elements: wheels or pinions mounted on the planetary element holder arm (3), geared on the pinion (1) and in the idle wheel (2). The second input module (a.2) is a planetary gear group that is comprised of two planetary gear mechanisms (fig 4.a.b.c.): a second planetary gear mechanism, in this case straight, that has a pinion (1), some planetary members (4), a center idle wheel (3) and a planetary member holder (2') that is the circumstantially movable part of this input module (a.2.) a first planetary gear mechanism, in this solution conical, that is comprised of a pinion (92), some planetary elements (91), a output wheel (90) and a planetary element holder (93), that is threaded inside with a thread (70). Said input module (a.2.) also includes a centrifugal clutch group (19, 20, 23, 24, 25) as it will be described hereinafter in this specification. This centrifugal clutch makes it possible to adjust, in terms of the speed of rotation, the locking adjustment mechanism formed by references (60) and (61); in terms of the outside shape of the part (23) that acts in contact with the contact element (60). Said locking adjustment mechanism is described in more details in modules (a.3) and in (a.4.), that also use it in their operation, with the particularity that in this module (a.2.) its operation is strictly linked to the speed of rotation of the mechanism. This input module (a.2) differs mainly from the simpler input module (a.1.) in that it includes said first planetary conic gears (90, 91, 92, 93), in that the circumstantially movable part (2') of said second planetary gear is the planetary element holder and not the idle wheel, and in that it includes the torque adjustment mechanism (60, 61, 23, 19, 20, 24, 25) dependent on the speed of rotation of the mechanism. All of that which has been said about the confirmation of the idle wheel of the input module (a.1.) and about the auxiliary elements that it includes is also applicable to this module (a.2.) It likewise includes a manual control module (e), though in this solution it does not need the centrifugal clutch group (d) (of figure 2.b.) for its connection or disconnection from the mechanism. Instead, it uses some straight gears that gear with the toothed outside part of the idle wheel (3) of the second planetary gear. The output shaft (73) (fig. 4.b.) includes a threaded part (70) that allows during starting of the motor (100) that not enough torque is transmitted to start the movement in the output, but to move the shaft (73) axially, from the conical planetary element holder (93) threaded inside to said thread (70), said thread (70) having a long pitch (or even balls) and permitting low friction. To recover and return it to its initial position, once it has been stopped, the mechanism includes an elastic element (94) that is weak enough to not to impede movement of the shaft in starting, but strong enough to overcome friction upon returning it to its initial position. The movement is transmitted from the motor (100) to the input element or shaft (71) and from this shaft to the center wheel (92) of said (conical) planetary gear. As long as the other center wheel (90) of said first planetary gear is kept stationary, the movement will pass through said center wheel (92) and from the planetary elements (91) to the planetary element holder (93) and from the latter to the output shaft (73). Said center wheel (90) will be kept stationary while said second straight planetary gear is braked in its movement, given that it moves together with the pinion (1) of said second straight planetary gear. If the manual control group (e) remains stationary, the idle wheel (3) will not move and, therefore, the only possibility of movement of said straight planetary gear will be through the planetary element holder (2'). This will be kept stationary as long as the adjusted torque in the torque limiting group (b) and by the locking regulating mechanism is not exceeded. In this way, upon exceeding said adjusted torque, said planetary element holder (2') is released and during its rotation the excess energy thereof is absorbed or taken advantage of in the same way as in the input module (a.1.) the idle wheel (2) did so. Hence, at no times the torque transmitted to the shaft (73) exceeds the torque regulated in the torque limiting group (b), given that any excess is transmitted to the straight planetary gear by means of the pinion (1) and absorbed by the planetary element holder (2'). The transmission group may have another configuration, in a predetermined way (a.3.) (figure 5.a., b. c.). In this configuration, the movement of the circumstantially movable part (2") is longitudinal (never turning movement.) This transmission group (a.3.) consists of a circumstantially moveable part (2") with a determined shape (in figure 5, hollow cylindric with a suitable cam profile) where the contact elements (5) (in the figure, only one) of the torque limiting group are locked, with, at least, two ball bearings (78) to allow good turning of the inside shaft (72) or (73) to part (2"). Said part (2") can likewise have a locking adjustment device () formed by two contact elements (in the figures, two balls) (60) and an elastic element (in the figures, Belleville rings) (61) between them. Said contact elements (60) are located between said pawl (5) of the torque limiting group and the surface of the shaft (73) or (72) inside (2") in the figures a projection (68). The locations and functional features (when the functional complexity thereof so requires) are described hereinafter. 2"- Circumstantially movable part with a predetermined shape, normally braked in its longitudinal movement by one or several contact elements (5) (pawls; in figure 1, only one, that is housed in a configuration suitable for that part (5) in said part (2")). Said part with a predetermined shape can have different configurations and shape in the cam profile (59) upon which said pawl (5) is moved when the pre-set torque is exceeded, depending on the greater or smaller progessiveness and durability that is to be given to said movement. It is clear that said shape of the cam profile (59) does not affect the instant breakdown of the transmission of torque when the pre-set torque is exceeded. 77 -At least two keys that prevent the rotation movement of part (2") fastening it to any stationery element (in figure 5, to the frame (O)). 78 - At least two ball bearings, that allow free and well guided turning of the shaft (72) or (73) inside said part (2"). 60 - At least two contact elements (in figure 5, two balls) that are kept in contact, each one, with the pawl (5) of the torque limiting group and with the projection (68) of the inside shaft. 61 - An elastic element, at least (in figure 5, Belleville rings) that keeps said balls (60) in contact with both surfaces. 68 - A projection in the shaft (72 or 73) inside part (2") with a configuration or shape so that upon moving, in the starting up, the ball (60) is forced into contact with it and towards the elastic element (61), thus reducing the torque threshold at which movement of the part (2") is allowed. Said configuration or shape can vary depending on the operating needs. In this case, references 60, 61 and 68 form the locking regulating group. Finally, the input module (a) can have a more developed configuration, in a predetermined form (a.4.) (somewhat similar to (a.3)), with turning as well as longitudinal movement. Said configuration consists of a unit formed by the torque limiting group (b) and the circumstantially moveable part (2''') with a predetermined form similar to the one used in module (a.3), that turns together with the speed and torque that the input shaft or mechanism (71) transmits to them. Integral to this unit the parts 88, 68. 81, 82 and 83 likewise turn thanks to the key (85). This turning movement of the torque limiting group (b) applied on (2''') in terms of the speed at which they turn, generally determined by the input element (71), usually contacted to a motor (100) or the like. Thus, by means of the regulating element (7), keeping said speeds in mind, it is possible to adjust the elastic element (6) that tightens the contact element (5) against the (cam) surface (59) of the truncated-cone-shaped part (2'''). In this case, the driving power cutoff group (c) as well as the auxiliary elements are placed upon another part (86), characterized in that it only has longitudinal movement, integral to part (2), its turning movement being prevented by the key (77). In this way said auxiliary elements are activated in the same way and have the same configurations as in module (a.3.) Hence, when the output shaft (73) encounters some obstacle (for example, the seat of the actuated valve), the transmitted torque increases and the speed of rotation drops. When the maximum stress regulated by grup (b) on part (2''') is exceeded, the latter remains instantly released and begins to move longitudinally; the characteristics of said movement depending on the shape of the cam curve (59) of part (2'''), upon which the contact element (5) of the group (b) will move. Upon producing said release of part (2), the part will drag part (86) in its longitudinal movement, therefore, actuating all the mechanisms associated to said part (86). This input module (a.4) likewise includes a locking adjustment mechanism () formed by references (60, 61 and 68). With the particularity that in this solution the inside curve that part (68) exposes to reference (60) in contact with it can be varied. In order to do so, one need only turn, in its position of rest, part (81) that, by means of the pin (82) turns part (83) that, in turn, by means of the key (85) turns said part (68), the latter showing a configuration different from the contact element (60) and as a result different torque adjustment. Said parts are not described due to the simplicity thereof. In this way one achieves that the locking regulating element () acts on the contact element (5) in a different way, depending on the need. (b): The torque limiting group (b) is a mechanism for regulating and limiting the output torque, breaking down the input torque into two, by means of the circumstantially movable part (2, 2', 2'', 2'''), one that is used in the output and the other, excess, that is released (in general not only this release is produced but also the excess torque is damped) and used to cutoff driving power as well as to carry out checks. It has a contact element (in figure 1, a pawl), an elastic element ( in the figures, some conical elastic Belleville washers) and an adjustment element (in figure 1, a micrometric screw) which are described hereinafter using this figure 1 as a model: 5 - Pawl: Circumstantial immobilizing or braking part housed, on the one hand, in the notch of of the idle wheel (2) and on the other, in the screw (7); remaining between the pawl and the screw an elastic element (6). 6 - Elastic element: Any type of elastic element (Belleville washers in the drawing) located between the outside of the rod of the pawl (5) and the inside of the screw (7) that presses it, varying the stress applied and therefore the transferable torque. 7 - Adjustment element: It is a device (in the figures, a micrometric screw) fastened to the body that adjusts the torque of the idle wheel (2): In its outside there are some marks with different output torques and an index. In solution (a.4) said torque limiting group(b) turns integral to the truncated-cone-shaped part (2'''); in this way, though it is formed by the same elements (5, 6,7), its operation will depend on the speed at which both elements turn (centrifugal force), (c): the driving power cutoff group, is a direct cutoff mechanism (or indirect cutoff, giving the cutoff signal) of the power, by means of contact, approximation or any other process (in figure 1, by contact and actuated by an eccentric (2)). It has in the figures a microswitch (8), a pushing ball (9) and signalling stop with a support spring (10) that are not described as they are very well known elements. Likewise, it can include other cutoff groups (secondary, tertiary, etc.) for greater safety in the event that the primary cutoff group were to fail. Besides, of the three basic elements or groups described, this input module can include one, two or three additional devices that will now be described: (α): Mechanical locking: Antagonistic device of the torque limiter, for locking of the circumstantially movable part (2), actuated manually or by any other means, that is abutted to the body of the input module or any other intermediate element with the latter and consisting of a rod, latch or any other element capable of being housed in a hole or notch placed for this purpose in the idle wheel (2), that serves to brake it circumstantially, cancelling with this the action of the pawl. This locking action can also be done by placing a screw or other immobilizing element of the torque limiter. The rod (11) with its corresponding spring and the position sleeve (12) of the case of the figure, are not described as they are also known. (β): General check: Device that makes use of the excess power and measuring it in a continuous or discrete way, in such a way that,wihout previous modification of the conditions of the torque limiter, its reduction means an increase of absorbed energy, which implies an anomaly in the unit formed by the actuator and the actuated element. If, on the contrary, the excess energy increases, it detects wear of any retainer or packing within the actuator-actuated element unit. Measuring the variation of the excess energy can be done mechanically, electrically, electronically, optically, vertically, etc. Said measuring of the variation of the excess energy can be done for the movement of the circumstantially movable part in one direction, in another or in both directions of movement (opening, closing or both). In the figures, this measuring of the variation of excess energy is solved by one of the many possible electric procedures, by a microswitch (13), an action ball (14) and an adjustment screw with a built-in spring (15),an indicator lighting up in situ or on the control desk by means of any electronic position sensor that can pick up this measurement. This checking signal can be picked up for recording and analysis by a microprocessor and come out on a printer. This checking action can also be done by measuring the stress of excess power through the torque limiter itself. (χ): Auxiliary damping. The damping device of the excess power, directly, or using the torque limiter itself (case of the figures) and/or increasing the force of the springs mounted on the signalling stop (10), or by means of a braking device of the part (2). It can also be damped by increasing by any means the absorbed energy. In the case of figure 1, this device is comprised of an elastic element (16), a contact element (a ball, for example) (17) and a sleeve (18), which do not require further description. INTERMEDIATE MODULE B It is comprised of two basic components or groups: the centrifugal clutch group (d) and the manual control group (e). This intermediate module has enough individuality so as to be included not only between the input module and the motor group of this mechanism object of the invention, but also between the motor group and the rest of the components of any conventional actuator. Likewise, this actuation mechanism may not include this intermediate module, in those cases in which the advantages of the flywheel and centrifugal clutch are not considered necessary or are not advantageous or are not compatible with the configuration of the input module (A), or else, it can include only the centrifugal clutch group and not include the flywheel and replace the latter by a disk placed in the shaft of the ventilator, in which one can insert a removable small handle, normally placed in the motor and allowing the continuity of current in the same, until the moment in which it is removed to insert it outside the disk that replaces the flywheel. This latter system can also be used in any actuator in which case an intermediate module is not included. (d): a centrifugal clutch group. Inserted between the motor group and the input of the planetary group consisting of a centrifugal clutch, which in addition to having a dead point, in its state of rest remains engaged in a flywheel and after the motor group starts moving, the flywheel is disengaged, the clutch passing through the dead point and automatically engaging the motor. With such a centrifugal clutch group, whether or not it is completed with the manual control group, within the intermediate module, this serves to obtain higher stresses due to successive accumulations of kinetic energy in the motor, whose sum is higher than that produced by the maximum torque, as long as there is irreversibility at the output. In the example of figure 2 this group (d) is comprised of the following elements: 19 - Movable pistons - Cylindrical pistons with transversal housing for the pushing balls (20) and a longitudinal groove for constant alignment thereof upon housing the guide supports (25) in them. 20 - Pushing balls - The centrifugal force thereof and that of the movable pistons (19) causes them to move along the inclined plane of the guide support (25) pushing the sliding bushing (23). 21 - Main body - It couples to the movable part of the motor and circumstantially to the pinion (1) of the input of the planetary group. In its top part it has some cylindrical housing for insertion of the movable pistons (19) and fastened to it the base of the guide supports (25). In the bottom outside part thereof there are some circular section housings to include the drag balls (22), while in the bottom inside part there is a bearing for better alignment of the shaft of the flywheel (26). 22 -Drag balls - They are placed in two groups. In the first group there is coupling and decoupling in the grooves of the main body (21) existing for this purpose. The second group carries out the same function in the grooves of the end of the shaft of the flywheel (26). Both groups are always housed in the drilled holes of the pinion (1). 23 - Sliding bushing - It slides by its inside part in the outside of the pinion (1), which limits its run. In its bottom part it has a O-ring cylindrical housing for inclusion of the drag balls (22) when the the corresponding clutch is released. This inside cylindrical part, in accordance with its position, prevents the alternative centrifugal deblocking of these balls. First, in the position of rest thereof, the balls that fit in the end of the main body (21) are released; in the dead point the two groups of balls are housed in this cylindric housing, and when then the bushing slides to its stop, the group of balls that drags the flywheel remains housed in it, remaining coupled by the contact thereof with the sliding bushing (23), in the bushing with housing (28). 24 - Resisting spring - It has the task of returning the entire mechanism to its starting position, upon reduction of the centrifugal force, by reduction of the revolutions of the motor. 25 - Guide supports - They are fastened to the main body (21) and they have the task of guiding the movable pistons (19) and forcing the pushing balls (20) to move. The drag balls (22) and the channels can be replaced by keys, dragging teeth, friction cone, etc., considering these elements in a broad and never restrictive manner. (e): the manual control group consists of an actuation system alternative to the motor, without ever losing the preference of the motor, when in cases of emergency (such as the lack of electric power, for example) there is the need to actuate the actuator. This group consists of a flywheel (26), a center shaft (27), which in turn acts as a guide support of part of the wheels of the mechanism and finally, a bushing with housing (28) for one of the drag ball groups (22). These components are not defined as they are very well known. (w): IRREVERSIBILITY MODULE It is comprised of a mechanism that can be placed in different positions within the energy transfer mechanism. Thus, it can be included in the input module (A) or between said module and intermediate module (B), or even between the intermediate module (B) and the output module (C). This irreversibility module transmits the torque of the input shaft to the output shaft of said mechanism, and during the transmission of said torque it blocks any movement of the output shaft in the direction of rotation contrary to that of torque transmission. And once the transmission of said torque has ended, it blocks any movement of the output shaft in any of the two directions of rotation. Said irreversibility mechanism, combined with the centrifugal clutch, makes it possible to obtain higher stresses due to successive accumulations of kinetic energy in the motor, being higher than that produced by the maximum torque. OUTPUT MODULE C The output of this mechanical power transfer mechanism, that the invention proposes, is comprised of a single basic group, though and in terms of the characeristics thereof, it can come in four different output variants, alternative between them and combinable with the rest of the modules and above groups, as well as with the additional devices. These variants are: C1 = rotating output module - (figure 3.1) C2 = threaded output module - (figure 3.2) C3 = output module with multiplier I (figure 3.3) C4 = output module with multiplier II (figure 3.4) (C1): Module C1 is comprised of the group with the bushing (f) in which this bushing (29) carries out the function of a charging cell with the particularity that the key (30) is helicoidal (with reversible thread), whereby the axial movement of the bushing (29) produces a sag in the elastic element (31), generating a signal. These signals generated by the displacement of the bushing (29) are collected mechanically, acustically, optically, electrically, electronically, etc. (in figure 3.1 a microswitch pack), being used for the maximum torque checking device ( ) as well as for the packing retightening signal device (ε). ( ): Maximum torque checking: additional device that takes advantage of the checking signal given off by the group (f). In the figure it is comprised of a sliding ring (32), an intermediate ball (33) and a microswitch pack (34), which do not require further description. This microswitch pack (34) can be replaced by any mechanical, optical, electronic element, etc., that carries out an equivalent function, of generating a signal that can be picked up directly in any amplifier or indirectly registered by microprocessor and printer or any other registering means. (ε): packing retightening signal. Device that by the above cited charging cell (29) and, at times, even, by means of the same signal elements, or else independently, notifies us of the wear of the packing of the actuated element. In the event that the output module is of a type of the group threaded inside (C2) or group with multiplier (C3) and (C4), the floating output nut, installed between the elastic elements, moves without turning and proportionally to the force exerted on the packing, and, upon this varying, the signal is produced which gives the order to retighten to another auxiliary actuator that is the one that carries out the retightening, by means of an electroclutch or actuator existing for this purpose. In the event that the output module is of the rotating type (C1) the action of the nut is replaced by a bushing threaded outside, also floating between two elastic elements, in which the reversible outside thread acts as a helicoidal cotterway. (C2): Module C2 (figure (3.2) is comprised by the floating nut group (g), which aside from absorbing the dilations of the output rod, due to thermal dilation, it also serves as a charging cell that warns of variations of the passive resistance conditions (for example, frictions, lack of lubricant, etc.), due to axial movement. This group is comprised, in figure 3.2., of a floating nut (38), a key (39) and the elastic elements (40) that do not require further description. The threaded output module C2 can have up to two additional devices: the device for checking stresses on the rod (ϕ) and the packing retightening signal device (ε) (the latter already described), which can also constitute independent units so as to adapt to the integral actuator like the existing conventional ones. (ϕ): Checking of stresses on the rod: It is an additional device built and included expressly for this checking function, from the signal given off by the floating nut group (g) in figure (3.2) it is comprised of:a sliding ring (35), an intermediate ball (36) and a microswitch pack (37), that are not going to be described due to their simplicity. In the case of the output module of the group (g) type as well as in those of types (h) and (i), the variations of load in the axial displacement of the group converts into sagging of the elastic elements, which are picked up by the additonal devices (ϕ) and (ε). (C3): Module C3 is comprised of an output group with multiplier I (h), which takes advantage of the principle that, for a single torque, at a smaller pitch and thread diameter, the greater the resulting stress. Upon linking a big diameter thread with another one of a small diameter we obtain, with the first one rapid movements and low stress to overcome the passive forces and, then, slow movements and high stress with the small diameter and pitch thread. For this it suffices that the first one stops against the second one, thus converting into a helicoidal cotterway. In this mechanism, upon starting of a movement, the small diameter thread always does so. The greater thrust effect has already been produced in figure 3.3a, the actuator has stopped and is ready to start, when ordered to do so, the backward movement. Upon the main nut (41) initiating circular movement, its thread acts as a helicoidal cotterway, dragging in its rotation the nut (42) as its diameter and pitch are smaller and since longitudinal movement thereof is prevented during the housing of the rigid element in the canal of the coupling (47) and causing the spindle (48) to move (this latter immobilized to turn by a key placed in its opposite end, outside of the figure)until reaching its stop, in which an axis of a throat made in it faces the axis of the rigid element (46) and that of the circular canal of the coupling (47) (figure 3.3b) and as of this moment the smaller diameter thread becoming a helicoidal cotterway, thus forcing the sleeve or the double thread nut (42) to turn, as the rigid element (46) no longer prevents it, the rigid element (46) has become housed in the throat of the spindle (48), following the path of the latter until the floating bushing (45) prevents the escape outside of the rigid element, remaining at the end of its path waiting for the order to return in the reverse direction (figure 3.3c). Upon the nut turning in the opposite direction and for following the rigid element (46) housed in the circular canal of the spindle (48) forced by the floating bushing (45), the smaller thread of the nut (42) becomes a helicoidal cotterway, thus this nut moving until reaching its stop, in which the axis of the rigid element again faces the circular canal of the coupling (47) and the canal of the spindle (48) (figure 3.3b) converting in this instant the thread of the main nut (41) into a helicoidal cotterway, while the thread of the small nut is no longer a cotterway and its rotation moves the spindle longitudinally, transmitting in this phase the greater stress until the starting point thereof is reached, repeating the cycle again. (Figure 3.3a.) This group (h) is comprised of the following elements in figure 3: 41 - Main nut. It is the nut that may or may not float, that converts the circular movement (stress) into linear movement. 42- Double thread nut - It is a bushing with an outside thread with a larger diameter than the inside one, with the double function in both as thread and helicoidal cotterway. One or several rigid thrust element(s) is/are housed in this nut (in the figure two balls.) Due to mechanical needs these threads can be bushings inserted in a sleeve, both of them as well as one of them (in the figure only the one with the smaller thread is inserted). 43 - Key. In the drawing the bushing threaded with a smaller diameter is linked with the double thread nut (42). 44 - Stop bushing. It regulates the run length limit of the spindle (48) through the smaller diameter thread. 45 - Floating bushing. It releases or fastens in its movement the rigid element (46). It can be replaced by continuity in the adjustment area of the double thread nut (42), in the cases of a short run. 46 - Rigid element. It may be one (or more) ball(s), a cylindric pin with the tips formed and, in general, any auxiliary element that can comply with the above cited operating conditions. 47 - Coupling - Bushing with inside circular canal for circumstantial housing of the rigid element and simultaneous immobilization of movement by means of the nut. 48 - Threaded spindle. Final element that carries out the sum of movements caused by the main nut (41) and the one with a smaller diameter and, partially, in each instant, the stresses corresponding to each one of the movements. (C4): Module C4 is comprised of an outlet group with multiplier II (i), which carries out the same functions and in the same sequence with the difference that, instead of having a rigid element and a floating bushing, it is provided with a coupling (53) and an elastic element (52) that regulates the pressure of the above so that the friction torque of the coupling is always greater than the difference of torques between the larger diameter thread and the smaller diameter one, for the same thrust (figure 3.4). It is comprised of the following elements: main nut (49), double thread nut (50), key and threaded spindle (54), already described in group (h), as well as: 52 - Elastic element: Spring, Belleville washers or any other element that provides pre-set pressure to the coupling cone (53). 53 - Coupling. Conical, flat, toothed etc. (Conical in the figure) that makes it possible to transmit the torque that forces into action the main nut instead of the small one; in module (C3) as well as in module (C4) the conventional threads can be replaced by low friction ball bearings and, therefore, with high efficiency, that makes it possible to improve the overall operation of said output modules (C3) and (C4).

Claims: Mechanical-kinetic servomechanism for instant limitation and retention of torque or stress transmitted from an input shaft or mechanism (1, 71) to an output shaft or mechanism (3, 73), comprising: an input (1, 71) of torque or stress; an output (3, 73) of torque or stress; transfer means (2,2',2'',2''',3,4,70,75) for transferring torque or stress from said input to said output; control means (2,2',2'',2''',5,6,7,59,60,61) for controlling the transfer means in such a way that the torque or stress transferred to the output does not exceed a predetermined level; whereby the control means comprise: a circumstantially movable part (2,2',2'',2'''), capable of responding to the transmitted torque or stress and through which said torque or stress is transmitted, that is arranged so that when the circumstantially movable part moves, the torque or stress at the input is not fully transferred to the output, and when the circumstantially movable part is held immobile, the torque or stress at the input is transferred to the output; a torque and/or stress limiting group (b) arranged to act in close contact with the circumstantially movable part (2,2',2'',2'''), said torque and/or stress limiting group (b) including: at least one mechanical contact element (5); at least one elastic element (6); whereby by means of said circumstantially movable part the servomechanism is arranged to divide the torque or stress applied to its input into two well defined stresses or torques, comprising: a torque or stress applied to the output; and an excess torque or stress; the circumstantially movable part (2, 2', 2', 2''') being arranged in such a way that said circumstantially movable part, in its movement and due to its configuration, gives rise to: at least one signal for subsequent use; and total or partial damping of the excess torque or stress, in order that said excess torque or stress will not reach the output; characterized in that the circumstantially movable part is arranged to start to move when the transmitted torque or stress reaches a predetermined threshold; the torque and/or stress limiting group (b) is arranged to prevent movement of said circumstantially movable part when the torque or stress is below said predetermined threshold and to permit suddenly free relative movement of the circumstantially movable part when said torque or stress is above said predetermined threshold; the torque and/or stress limiting group (b) includes threshold regulation means for regulating said predetermined threshold, whereby said threshold regulation means include the at least one elastic element (6) and means for regulating the pressure that the at least one mechanical contact element (5) exerts on the circumstantially movable part (2,2',2'',2'''). Servomechanism according to claim 1, characterized in that the torque limiting group (b) includes an adjustment and regulation element (7) arranged to adjust the torque or stress threshold at which said torque limiting group (b) allows relative movement of the circumstantially movable part (2,2',2'',2''') whereby said adjustment and regulation element (7) is arranged to act on the at least one elastic element (6) in order to regulate the force that the at least one mechanical contact element (5) exerts on the circumstantially movable part (2,2',2'',2'''). Servomechanism according to any of claims 1 or 2, characterized in that the circumstantially movable part is the outside idle wheel (2) of a planetary gear mechanism, said idle wheel being capable of moving around its own shaft; said mechanism comprising at least: a frame (O); an input shaft (71); a center pinion or wheel (1) fastened to said input shaft and arranged to gear directly with the planetary pinions or wheels (4) of the planetary gear mechanism; a planetary element holder (3) supporting one or several planetary pinions or wheels (4), said planetary element holder (3) constituting an output for torque from the planetary gear mechanism, said planetary element holder (3) being able to include one or several arms; one or several, preferably three planetary wheels (4) mounted on said planetary element holder (3), said planetary wheels (4) being arranged to gear with the center wheel (1) and with the outside idle wheel (2); whereby the idle wheel (2) is arranged to gear by its inside with the planetary wheels (4), and wherein the idle wheel (2) is normally braked by at least one mechanical contact element (5) of the torque limiting group (b), said at least one mechanical contact element (5) being housed in a groove or configuration arranged for this purpose in said idle wheel (2), thus controlling and limiting rotation of said idle wheel; in such a way that, when the torque exceeds a pre-set torque threshold, said idle wheel (2) is released and starts to turn, whereby its configuration is arranged to cause, as a result of the turning movement of the idle wheel, cutoff of the driving power of a motor at the input, and whereby due to the movement of the idle wheel (2), only a limited portion of the torque at the input can be transmitted through the planetary element holder (3) to the output. Servomechanism according to any of claims 1 or 2, characterized in that the circumstantially movable part is the planetary element holder of a planetary gear mechanism, said planetary element holder being arranged so that it can rotate around its own shaft; said mechanism comprising, at least: a frame (O); an input shaft (71); a center pinion or wheel (1) fastened to said input shaft, and arranged to gear directly with planetary pinions or wheels (4); one or several, preferably three planetary wheels (4) mounted on said planetary element holder (2'), said planetary wheels (4) being arranged to gear with the center wheel (1) and with an outside idle wheel (3); the outside idle wheel (3), that is arranged to be free or stationary; the planetary element holder (2') where the planetary wheels (4) are mounted and that can only have rotational movement which is limited and regulated by at least one mechanical contact element (5) of the torque limiting group (b), said at least one mechanical contact element (5) being housed in at least one corresponding configuration or groove arranged for this purpose in said planetary element holder (2'). Servomechanism, according to claim 4, characterized in that the outside idle wheel (3) is arranged to gear externally with a transmission gear that either transmits movement and torque to said idle wheel (3), or else keeps said idle wheel (3) stationary and braked. Servomechanism according to any of claims 4 or 5, characterized in that it includes two planetary gear mechanisms, a first one preferably being conical and a second one preferably being straight, and in that the input shaft (1) of the second planetary gear mechanism is integral with the idle wheel (90) of the first planetary gear mechanism, comprising at least: an input shaft (71); a preferably conical input pinion (92) fastened to said input shaft (71) and that gears directly with preferably conical planetary pinions or wheels (91); a planetary element holder (93) where the preferably conical planetary wheels (91) are mounted and through which, in the event that the preferably conical idle wheel (90) is stationary, the movement and torque resulting from the first planetary mechanism come out; one or several preferably conical planetary wheels (91) mounted on the planetary element holder (93), whereby said planetary wheels (91) are arranged to gear with the preferably conical input pinion (92) and with the preferably conical idle wheel (90); whereby, while the outside idle wheel (3) of the second planetary mechanism is in a stationary position, there are two possibilities of movement: 1) when the torque transmitted by the first planetary gear mechanism is below the pre-set torque threshold, the movement and torque will come out through the planetary element holder (93) of said first planetary gear mechanism; 2) when said torque is above said threshold, the torque will come out partly through the planetary element holder (93) of the first planetary gear mechanism and partly through the planetary element holder (2') of said second planetary gear mechanism, thus releasing said planetary element holder (2') of said second planetary gear mechanism. Servomechanism according to any of claims 1 or 2, characterized in that the circumstantially movable part (2'') is arranged so that it can only move longitudinally and never rotationally, and in that it comprises: a frame (O); an input shaft (71) threaded on its end with a reversible function thread (70); a hollow shaft (72), threaded internally and arranged to house the input shaft (71); an output shaft (74) arranged inside said hollow shaft (72) and fastened to it by a sliding key or the like (75) arranged to make both shafts turn, but allowing longitudinal movement of the output shaft (74); at least one elastic element (69) that is arranged to push the circumstantially moveable part (2'') towards an initial position in order to return the circumstantially movable part (2'') to said initial position at the end of an operation cycle; the circumstantially movable part (2'') that, mounted outside said hollow shaft (72), can only move longitudinally along said hollow shaft (72), whereby said circumstantially movable part (2'') has a geometry such that its longitudinal movement is limited and controlled by the mechanical contact element (5) of the torque limiting group (b) whereby it limits at the same time, the longitudinal movement of said hollow shaft (72) in such a way that upon exceeding the pre-set torque threshold defined by the elastic element (6) of the torque limiting group, said circumstantially movable part (2'') can move longitudinally cutting off the supply of input power and absorbing or taking advantage of the excess power by the profile (59) of said circumstantially movable part (2''). Servomechanism according to any of claims 1 or 2, characterized in that the circumstantially movable part (2'') is arranged so that it can only move longitudinally, never rotationally, and in that it comprises: a frame (O); an electric, pneumatic or hydraulic motor that acts as an input mechanism (100); an output shaft (73) with a reversible function thread; a hollow shaft (71) threaded inside to house the output shaft, the outside of said hollow shaft being integral to the motor; an output bushing included in one end of the hollow shaft and between said hollow shaft and the output shaft; said output bushing being joined to said output shaft by means of a sliding key (75) or similar element that makes them turn together, but allowing longitudinal movement of the output shaft; a circumstantially movable part (2''), that is mounted outside to said output shaft (73) and that can only move longitudinally along said output shaft, whereby said circumstantially movable part (2'') has a geometry so that its longitudinal movement is limited and controlled by the mechanical contact element (5) of the torque limiting group (b) and limits, at the same time, the longitudinal movement of said output shaft (73), so that upon exceeding the pre-set torque threshold defined by the elastic element (6) of the torque limiting group (b), said circumstantially movable part (2'') can move longitudinally cutting off the input energy supply and absorbing or taking advantage of the excess energy by the profile of the circumstantially movable part (2''); at least one elastic element (69) that is arranged to push the circumstantially moveable part (2'') towards an initial position in order to return said circumstantially movable part (2'') to its initial position at the end of an operation cycle, whereby said elastic element is big enough to allow friction to be overcome and to return the mechanism to its initial position, but small enough not to prevent or interfere with the operation of the mechanism. Servomechanism according to any of claims 7 or 8, characterized in that it includes a locking adjustment device that comprises: an elastic element (61); contact elements (60) resting on said elastic element (61); a groove placed in the outside of the shaft just inside the circumstantially movable part (2''); whereby due to the elastic element (61) a contact element (60) is kept constantly in contact with the mechanical contact element (5) and another contact element (60) is kept in constant contact with said groove in said shaft, whereby it is achieved that during starting up the force that the mechanical contact element (5) exerts on the circumstantially movable part (2'') is greater and thus, the adjusted maximum torque is greater too. Servomechanism according to any of claims 1 or 2, characterized in that the circumstantially movable part (2''') is arranged so that it can move longitudinally as well as rotate with regard to its own shaft and in that it comprises: a frame (O); an input mechanism or shaft (71); an output shaft (73) having a threaded part (70); a hollow outside part (88), fastened to the input shaft or mechanism (71); a hollow intermediate part (89) integral in its rotation movement to said hollow outside part (88) but that can move longitudinally with regard to the latter, thanks to a sliding key or other similar element that joins them; a hollow element (98) threaded inside, integral in its rotation movement to said hollow intermediate part (89) and whose inside thread is coupled to the thread of said output shaft; a circumstantially movable part (2''') arranged to turn integrally with said hollow outside part (88) but arranged so that it can move longitudinally with regard to said hollow outside part, thanks to a sliding key or similar element that joins them, said circumstantially movable part (2''') being mounted outside to said output shaft (73) and to said hollow intermediate part (89) and being able to move longitudinally with regard to said hollow intermediate part (89); said circumstantially movable part (2''') having a shape or configuration so that said longitudinal movement is limited and controlled by the mechanical contact element (5) of the torque limiting group (b), though without limiting the longitudinal movement of said hollow intermediate part (89); at least one elastic element (69) arranged to return, once the operation of the input mechanism or shaft (71) has ended, said circumstantially movable part (2''') to an initial position; further characterized in that the torque limiting group (b) is arranged to effect circular movement around its own main shaft, integral to the cited hollow outside part and in that it includes: at least one mechanical contact element (5); at least one elastic element (6); one adjustment and regulation element (7) arranged to act on of said elastic element (6), the elastic element (6) being regulated by the adjustment and regulation element (7) in order to adjust the force that the mechanical contact element (5), depending on the speed of rotation of the input mechanism or shaft (71) and on the centrifugal force generated by the mechanical contact element (5), exerts on said circumstantially movable part (2'''), taking advantage of the centrifugal force as a self-adjustment element. Servomechanism, according to any of the preceding claims, characterized in that it includes a device that defines a biunivocal correspondence between the excess energy and the angular or longitudinal movement of the circumstantially movable part (2,2',2'',2'''') upon being released and in which, when the applied energy is pre-set, one can observe or measure the variation of passive energies by variation of the angular or longitudinal movement of the circumstantially movable part (2,2',2'',2'''). Servomechanism, according to any of the preceding claims, characterized in that it comprises means to effect a general check of the mechanism and of the equipment actuated by it, upon including any sensor device that gives a signal or continuously or discretely measures the angular or longitudinal movement of the circumstantially movable part (2,2',2'',2'''), which, when it is less than the established one, implies an increase of the passive forces and therefore malfunctioning of the mechanism or actuated equipment, and on the contrary, the increase of angular or longitudinal displacement of the circumstantially movable part (2,2',2'',2''') implies a drop of the passive forces, this signal being able to be picked up and taken advantage of in certain cases, such as for ordering retightening of a packing by means of an electroclutch or an auxiliary actuator mechanism. Servomechanism, according to any of claims 1-3 and 11-12, characterized in that the circumstantially movable part (2) has an outside periphery that is not concentric with its inside toothed periphery, and in that the elastic element (6) acts on a notch made in the point of the outside periphery that is radially closest to said inside periphery. Servomechanism, according to any of the preceding claims, characterized in that it includes a device that allows circumstantial locking of the circumstantially movable part (2,2',2'',2'''), either by immobilization of the torque limiting group (b) or by insertion of a rigid element into said circumstantially movable part. Servomechanism, according to any of the preceding claims, characterized in that it includes one or more auxiliary damping devices (χ) applied to the circumstantially movable part (2,2',2'',2''') to absorb in the relative movement of said part more excess energy than that maximum that can be absorbed by the torque limiting group (b); said absorption depending on the outside geometric configuration of said circumstantially movable part (2,2',2'',2''') and on the adjustment of said auxiliary damping device (χ). Servomechanism, according to any of the preceding claims, characterized in that it includes an inertial flywheel, in order to allow for an increase of the kinetic energy in sporadic cases. Servomechanism, according to any of the preceding claims, characterized in that it includes an automatic centrifugal clutch (d) connected to the motor, carrying out the connection of the motor to the servomechanism upon attaining a preset rate of revolutions. Servomechanism, according to claim 17, characterized in that there is a flywheel (26) that can be actuated manually to apply manual power to the output, connected to the centrifugal clutch (d), being disengaged upon the motor exceeding a predetermined speed. Servomechanism, according to any of claims 17 and 18, characterized in that the centrifugal clutch (d) is arranged so that when the revolution velocity of the motor is reduced, the motor becomes disengaged and, without stopping, can increase its velocity and become re-engaged, in order to be able to accumulate successive pressure surges until the motor stops due to heating, whereby an irreversible element is inserted at an output of the mechanism. Servomechanism, according to any of the preceding claims, characterized in that it has a high efficiency irreversible element arranged to transmit the torque from the input shaft to the output shaft of said mechanism, whereby said irreversible element is arranged so that during said torque transmission it blocks any movement of the output shaft in the direction contrary to that of the torque transmission and once the transmission of said torque has ended, it blocks any movement of the output shaft in any of the two directions of rotation. Servomechanism according to any of the preceding claims, characterized in that it has an adjustment device for adjusting locking the mechanical contact element (5) that comprises: a centrifugal mechanism (19, 20, 23, 24, 25); at least one intermediate elastic element (61); optional contact elements (60) resting on the intermediate elastic element 61; wherein an outside surface of the centrifugal mechanism (23) is kept pressed against the contact elements and these in turn against the adjustment device (b), whereby the force needed to release the circumstantially movable part (2,2',2'',2''') will depend on the outside geometry and on the elasticity of the centrifugal mechanism (23). Servomechanism according to any of the preceding claims, characterized in having one or several current cutoff elements (c) each one of which comprises: at least one electric microswitch or any other element for direct or indirect interruption of electric current (9); at least one elastic element; a sliding element (10) contacting with the circumstantially movable part (2,2',2'',2'''), said sliding element having at least one groove arranged in correspondence with at least one corresponding contact element arranged to activate the corresponding microswitch in response to a sliding movement of said sliding element (10); whereby the outside surface of said circumstantially movable part (2,2',2'',2''') has a geometric shape arranged so that determined angles of angular movement will move said sliding element in one direction or the other. Servomechanism, according to any of the preceding claims, characterized in that it includes a group with a bushing (f) that allows checking the output torque and capturing a signal by means of two concentric bushings with reversible thread, acting as helicoidal cotterway, the inside of the bushings resting on one or two elastic elements that allow movement thereof, whereby said movement is arranged to generate a signal that indicates the variation of passive forces, an increase of forces corresponding to a smaller run, indicating an anomaly in the transfer mechanism or in the equipment actuated by it, while a longer run corresponds to a drop of passive force, it being possible to take advantage of this signal in order to order retightening of a packing by means of an electroclutch or auxiliary actuator. Servomechanism, according to any of the preceding claims, characterized in that it includes a floating nut group (g) that allows checking of the thrust of the pressure exerted longitudinally by a spindle on the nut that orders it, the nut being floating, in one or both ends, on one or two elastic elements that allow it to move, the mechanism being arranged to take advantage of this movement to generate a signal that indicates the variation of the passive forces, a rise of forces corresponding to a smaller run, which indicates an anomaly in the energy transfer mechanism or in the equipment actuated by it, while a greater run corresponds to a drop of passive forces; whereby it is possible to take advantage of this signal in order to order retightening of a packing by an electroclutch or auxiliary actuator. Servomechanism, according to any of the preceding claims, characterized in that it includes a multiplier group (h) that with the same output torque and revolutions allows conversion of circular movement of a main nut (41) into linear movement, by means of a doubly threaded sleeve (42) having a large diameter outside thread and an inside thread with smaller diameter than the outside thread, a male portion of which engages with the main nut and a female portion of which engages with the end of a spindle (48), which cannot turn but can move longitudinally, in such a way that the threads can alternately actuate as threads and helicoidal cotterways depending on a rigid or flexible element (46), as well as on some stops, there being greater speed and less force in the linear movement of the spindle (48) when the smaller diameter thread acts as a helicoidal cotterway and the larger diameter thread acts as thread and less speed and greater force when the larger diameter thread acts as a helicoidal cotterway and the smaller diameter thread acts as thread, with the additional particularity that upon reversing the rotation of the main nut (41) the spindle is withdrawn through the smaller thread and, upon said smaller thread abutting the speed of movement of the spindle increases by means of the larger diameter thread, until reaching its pre-set position, remaining ready to repeat the cycle completely or partially. Servomechanism according to claim 25, characterized in that the threads forming part of the mechanism are ball threads and are therefore reversible with low friction and high efficiency. Servomechanism according to any of claims 7-10, characterized in that it includes a worm-wheel reduction mechanism arranged to provide the possibility of reversible longitudinal movement. Servomechanism according to any of the preceding claims, characterized in that it includes in the output any known reduction or multiplication element that makes it possible to achieve different velocities and stresses or torques. Servomechanism according to any of claims 4-28, characterized in that it includes a mechanism (60, 61) for varying automatically, in dependence upon the speed, the torque threshold at which the torque limiting group (b) allows relative movement of the circumstantially movable part.

Inventors: SASTRE DEL RIO SALVADOR, SASTRE DEL RIO, SALVADOR
Applicants: CENTRALAIR SA, CENTRALAIR, S.A.
Application year: 1995
Main classification: F16K31
IPC codes: F16D21, F16H35, F16D11, F16K31, H02K7, F16D43