WO2010028609A2

WO2010028609A2 - Control method for transmissions and time limited processes

Info

Publication number: WO2010028609A2
Application number: PCT/CY2008/000001
Authority: WO
Inventors: Panayiotis Economou
Original assignee: Panayiotis Economou
Priority date: 2008-09-12
Filing date: 2008-09-12
Publication date: 2010-03-18
Also published as: WO2010028609A3

Abstract

The invention comprises a method and devices used to control the change in the relative position of various components, referred to as 'critical movement', in mechanical and electromechanical assemblies or collection of assemblies, while a primary movement is in progress, where the critical movement has to be performed and completed within a specific time limit to avoid unwanted consequences. Examples include gear-change in variable transmissions and railroad switches. The invention is characterized by the use of each of the following steps at least once: an operator dependent step, referred to as the 'intension' step which in itself does not directly bring about the critical movement; a step referred to as 'interaction' step, which is brought about by interaction of a component with the intension step or another interaction step, where the component, referred to as 'client servant', is associated directly or indirectly with the primary movement and a step utilizing an all-or-nothing process, such as release of a pre-tensioned spring, which makes the whole process all-or-nothing. The invention can also include the following optional steps: a step referred to as 'enforcer step', which ensures the timely completion of one or more of the other steps by interaction of components with a client servant; a step involving modifications to the assembly to ensure correct function and readiness for a critical movement and an interaction step that returns the relevant components to their original positions after the process is completed.

Description

CONTROL METHOD FOR TRANSMISSIONS AND TIME LIMITED PROCESSES

Technical Field

[1] The invention relates to methods and devices used to control the change in the relative position of various components, in any mechanical and electromechanical assembly or collection of assemblies while a primary movement is in progress, where this change in the relative position of various components has to be performed and completed within a specific time limit to avoid damage, clash or any other unwanted result. Examples include the control method and mechanism needed to control gear-change in some variable transmissions such as that described in patent application PCT/CY2007/000005 and the control method and mechanism needed in a railroad switch to enable a railway train to be guided from one track to another.

Background Art

[2] Very often in mechanical and electromechanical assemblies or collection of assemblies, while a primary movement is in progress, a change in the relative position of various components is required. On many occasions this has to occur within a specific time limit, in relation to the primary movement, to avoid damage or clash.

One example is the case of some transmissions such as the GCEVT as described in patent application PCT/CY2007/000005. When change of gear is sought, the elevators must move to one position within a specific time limit and then again to their original positions within another time limit. If this process is not done within specific time limits then some components of the transmission may collide. For this reason the control mechanism is specially designed to ensure that the movement is commenced and completed on time and in association with the rotational movement of the central gear. Another example is the case of a train traveling on a rail track when the track divides into two possible directions. If the switch rails are in the first position then the train travels in the first direction, if they are in the second position then the train travels in the second direction. If at the crucial time the switch rails are in an intermediate position then the train could derail. [3] The GCEVT, as described in patent application PCT/CY2007/000005, employs a two step approach. The first step is displacement of the gear selector lever by the operator, the operator being either human or an automated device. This causes the displacement of a tilted disc or other component in such a way as to enter the path of an extension attached to one of the elevators. The second step begins when the extension intercepts the tilted disc, in which case it and the elevators are displaced in pace with the rotational motion of the central gear and moved to a predetermined position. Other components ensure the return of the elevators to their neutral positions on time and in relation to the rotational movement of the central gear. [4] Interlocking has been used in railways. Mechanical, electromechanical, relay based and electronic interlocking has been used. In mechanical interlocking, a locking bed is used consisting of steel bars forming a grid. The levers that operate switches, signals or other appliances are connected to the bars running in one direction. The bars are constructed so that, if the function controlled by a given lever conflicts with that controlled by another, then mechanical interference is set up in the cross locking between the two bars, in turn preventing the conflicting lever movement from being made. In electromechanical interlocking systems the levers instead of operating the switches and signals directly, they do so electrically or electro-pneumatically. The same concept is used in relay interlocking but relays are used instead of mechanical methods to prevent clashes. In electronic interlocking, computers and software are used. Interlocking, however, is primarily intended to ensure that a correct set of steps is performed together as a group to avoid conflict and not to ensure that the steps are performed on time in relation to the traveling speed of the train. [5] A usual way of solving this problem is by the use of intelligence, either human or electronic to estimate the time constraints and follow them to avoid a clash, hi trains for example, these changes are done in good time before the train approaches a junction.

Disclosure of Invention

Technical Problem

[6] As mentioned above, the usual way of solving the problem of timing is by the use of intelligence, either human or electronic. The time constraints are calculated either manually or by the use of sensors and computers and the process is initiated and completed on time to avoid any clash. The use of multiple modalities and estimations is, however, prone to error. Any process involving a large number of steps is exposed to a large number of possible errors, like for example, failure of one of the sensors or failure of one of the computers, power failure or human error.

What compounds the problem is the fact that the time constraints are not fixed. They depend on the rate of movement of other components of the assembly or collection of assemblies and this rate of movement could vary even during the time the calculations are made. [7] Another technical problem arises if the operator does not fully complete the action necessary to initiate the change or if the operator changes his mind in the middle of a change and either withdraws the action or makes a new action towards a new change. Such actions by the operator are likely to result in a clash. For example if during the time a train is diverted towards one direction at a railroad switch, the switch rails are moved to a different position then part of the train will derail. A simple reliable method is needed to make the initiation of change irrevocable and also prevent any more changes from being made while the first change is in progress.

Technical Solution [8] For simplicity in this text we will refer to the usual main movement of the relevant parts of the assembly as the "primary" movement. One example of primary movement is the ordinary rotation of the central gear of the transmission in patent application PCT/CY2007/000Q05, while transferring rotational movement from the engine to the wheels. Another example is the ordinary travel of a train along its track. We will refer to the movement that needs critical timing as the "critical" movement.

Examples are the displacement of the elevators during gear change in the transmission described in patent application PCT/CY2007/000005 and the travel of a train along the switch rails in order to change course. The part or parts of the assembly that are displaced during the critical movement will be referred to collectively as the "client". In the case of the variable transmission of patent application PCT/CY2007/000005 the client comprises the two elevators and structures attached to them, hi the case of the train the client is the whole train at the time of change of direction, hi this text the term "operator" refers to either a biological being, for example a human being, or any other device or source of motion that could initiate the changes that would lead to a critical movement like for example an automated mechanism or a computer. [9] The method disclosed in this invention is intended to provide an alternative that overcomes most of the disadvantages of the prior art. It utilizes processes already in use in the prior art and puts them together for use as a series of steps in a distinct method. The aim is to make the control process, simple, totally predictable and totally related to and controlled by the primary movement. The method consists of a series of steps which must include the following steps: The initial step is an action in which the operator sets the process in motion. This first action stems from the operator's intension to start the process that will lead to a critical movement and will be referred to as the "intension" step. For example, the operator displaces the handle of the gear-change mechanism in a transmission. It is important for the disclosed method that this action should not lead directly to the critical movement. The exact timing of the intension step, with regard to the control method disclosed, is therefore not crucial and no calculations are needed. The next step begins when this action interacts with a component associated directly or indirectly with a component involved in the primary movement. Such components involved in interactions will be referred to from now on as "client servants" and the steps "interaction steps". In fact all other important steps in the disclosed method are initiated by client servants and are interaction steps. This way the onset of each step is in direct association with the primary movement. Its onset can therefore be predicted exactly in relation to the primary movement. In addition the time available for completion of each step before the critical movement, is directly related to the rate of the primary movement and thus if the maximum rate of primary movement is known it is totally predictable.

This principle will become clearer with the description of the example embodiment that will follow. The next concern is to eliminate the possibility of incomplete actions. To achieve this, the disclosed method utilizes at least one interaction step involving a known all-or-nothing process. It is preferable that this step is the first interaction step. Examples of such processes include the release of a pre-tensioned

"loaded" spring, the release of atensioned elastic material, the release of fluid or gas from a pressurized container in an irrevocable way, the discharge of a capacitor and in general any process that releases potential energy in an irrevocable way. For simplicity in this text the release of a loaded spring will be used in most of the examples and will represent all these processes. The response time of these all-or-nothing events can be modified and predicted to a high degree of accuracy. Thus it can be arranged and accurately predicted that the first interaction step will be completed on time as long as the primary movement is within a specific known range. This will ensure that all other interaction steps are completed on time, m other words the involvement of an all-or-nothing process converts the whole process of the disclosed method into an all-or-nothing process. [10] The process described in this method can be made even more efficient if an optional further step is added. This consists of a mechanism which, through the action of a client servant, enforces timely completion of a crucial interaction step. Such steps will be referred to as "enforcer" steps. The principle of enforcer steps will become clearer with the description of the example embodiment that will follow. An enforcer step in general widens the margin of safety for timely completion of the interaction step in enforces.

[11] The next concern is to make sure that once the process described in this method is initiated it can not be reversed or stopped mid-way before all steps are completed. Therefore, if the components that brought about the crucial movement have to be restored to their original positions, this is brought about by a client servant as an optional final step at the end and not by the operator. Another optional step in this method is any other step taken to ensure correct function of the assembly or collection of assemblies before, in preparation for and during a critical movement. [12] The above description is not intended to be limiting. Many combinations can be used. The principles of this invention will become clearer once one goes through the examples below.

Advantageous Effects

[13] This invention deals with critical movements which can be an important part of a multiplicity of mechanical and electromechanical assemblies. It makes the timing of such events scientifically predictable and controllable thus avoiding catastrophic clashes or collisions of components or other unwanted effects. It achieves this by utilizing a method that makes the timing of critical events non operator dependent. The method consists of a small number of simple steps which should be easy and inexpensive to implement. The method disclosed in this invention can prevent costly damage to expensive equipment as well as human injury.

Description of Drawings

[14] Fig. 1 is a perspective view of one embodiment of the transmission disclosed in patent application PCT/CY2007/000005 with a central gear, two elevators, two complementary gears, most of the components of the control mechanism and a differential assembly. [15] Fig. 2 is a perspective view of the embodiment demonstrated in Fig. 1 but with a different control mechanism and modified elevators.

[16] Fig. 3 is a perspective view of the elevators of the embodiment demonstrated in Fig. 2, isolated in order to demonstrate their structure.

[17] Fig.4 is aperspective view of the central gear of the embodiment shown in Fig.2 demonstrating the position of the guide pin.

[18] Fig. 5 is a perspective view of the guide pin demonstrating its structure. [19] Fig. 6 is a perspective view of the specially shaped axle of the guide pin demon- strating its structure.

[20] Fig. 7 is a perspective view of the guide pin in a channel.

[21] Fig. 8 is a perspective view of the guide pin in a straight channel hi the control body of the embodiment used as an example in this application.

[22] Fig. 9 is a perspective view of the control body shown in Fig. 8 but with a curved channel.

[23] Fig. 10 is a perspective view of the embodiment used as an example in this application with the control body absent, to demonstrate the deviators with the channel straight.

[24] Fig, 11 is a perspective view of the embodiment used as an example hi this ap- plication with the control body absent, to demonstrate the deviators with the channel curved. [25] Fig. 12 is a perspective view of the deviators and some of the components used to control their position.

[26] Fig. 13 is a perspective view of the embodiment demonstrated in Fig. 2 and demonstrates the gear-change component.

[27] Fig. 14 is a perspective view of the embodiment demonstrated in Fig.2 and demonstrates the enforcing levers. [28] Fig. 15 is a perspective view of the enforcing levers with the control body absent. [29] Fig. 16 demonstrates another embodiment of the transmission shown in Fig. 1 and illustrates modifications that can be made to the line joining the secondary sites to improve the control method for gear-change.

Best Modes [30] In the folio wing description and the accompanying drawings, the present invention will be described in more detail in terms of exemplary embodiments. It is to be understood that the invention is not to be limited in any way to these exemplary embodiments. Words used here are words of description rather than of limitation. The invention is intended to cover various modifications and equivalent arrangements. Multiple changes in the form of the invention may be made without departing from the principles and scope of the invention as disclosed.

[31] Nuts and bolts as well as most of the support structures have been omitted for the sake of clarity. Ball bearings have also been omitted as well as other details of construction, all in an effort to make the description easier and the drawings simpler and clearer.

[32] Fig. 1 demonstrates the variable transmission used as an example in patent application PCT/CY2007/000005. That example is described in detail in patent application PCT/CY2007/000005 and a detailed description of that transmission is not intended in this divisional application. The transmission as shown in Fig. 1 is comprised of the following major elements: a central gear 10, two complementary gears 11 and 12 with their corresponding shafts 13 and 14, the support structures (of which only a small part of the base 15 is shown), the control mechanism 16 and a differential assembly 17. Fig. 2 demonstrates another embodiment of the transmission of patent application PCT/CY2007/000005. This embodiment will be used as an example in this text. The transmission as shown in Fig. 2 is similar to that shown in

Fig. 1 but the elevators are supported in a different way and also a different embodiment of the control mechanism is being used. It is comprised of the following major elements: a central gear 10, two complementary gears 11 and 12 with their corresponding shafts 13 and 14, the support structures (of which only a small part of the base 15 is shown), the new control mechanism 18 and a differential gear 17.

[33] Fig. 3 shows the elevators 19 and 20 separated from the central gear. In this embodiment the elevators are not supported by axles. Instead they are supported by longitudinal protruding elements 21 which fit in channels in the central gear. Control rod 22 forces the elevators to slide in opposite directions as in the embodiment used as an example in patent application PCT/CY2007/000005. To bring about gear-ratio change the active elevator 19 is pushed towards the narrower side of the central gear. Through control rod 22 the passive elevator 20 is pulled towards the wider part of the central gear. As rotation of the central gear continues the complementary gears 11,

12 rotate from the elevators to the body of the central gear or vice versa and in the process find themselves on a different composite gear. The elevators are then displaced back to their normal positions and thus gear-change is brought about. [34] Fig. 4 demonstrates the elevators in their normal positions in the central gear. In this example embodiment, guide pin 23 represents the client servant which will bring about the displacement of the active elevator when gear-ratio change is sought. Fig. 5 demonstrates the guide pin 23 isolated to show that it comprises a specially shaped axle 24 and two guide rings 25. Fig. 6 demonstrates the structure of the specially shaped axle 24 of the guide pin. Fig. 7 demonstrates an embodiment in which the guide pin, comprising the specially shaped axle 24 and the two guide rings 25, rotates on the periphery of a cone within the associated channel. In this example embodiment, during normal function the guide pin travels in a channel which is part of the control mechanism. This ensures that the elevators are constantly aligned within the central gear and also makes sure that the guide pin, which serves as a client servant, is always ready for gear-ratio change. As shown in Fig. 7 during normal function the inner guide ring rolls on the inner part of the channel while the outer guide ring rolls on the outer part of the channel, ensuring absolute stability. Ball bearings between the specially shaped axle and the guide rings minimize friction. They are not shown in the diagrams. The use of the guide pin and a channel is one of the optional steps of the disclosed method that ensure correct function of the assembly before, in preparation for and during a critical movement Another embodiment is demonstrated in Fig. 8. In this embodiment the channel 26 is in the periphery instead of the guide pin 23, as demonstrated. This embodiment will be used to demonstrate the method. Fig. 8 demonstrates the main body of the control mechanism which will be referred to as the control body 27. The control body 27 contains the main channel 26 in which the guide pin 23 travels. During primary movement, of the transmission the guide pin travels in a circular fashion within the channel without deviation. This will be referred to as "straight" movement of the guide pin indicating that there is no deviation. When gear-ratio change is needed, modifications are brought about to produce a deviation in the channel as shown in Fig. 9. This forces the guide pinto deviate causing displacement of the active elevator. In this example embodiment the deviation is brought about by utilizing suitably shaped components. These components are the internal deviator 28 and the external deviator 29 seen in Fig. 8 and in Fig. 9. In Fig. 8 the internal deviator 28 is down and the external deviator 29 is up making the channel straight. In Fig.9 the internal deviator 28 is up and the external deviator 29 is down creating a deviation in a portion of the channel. [35] There are two control mechanisms on control body 27. When gear-change in one direction is required, one of the two is activated. When gear-change in the opposite direction is required the other mechanism is activated. In Fig. 10 the control body has been removed to better demonstrate the two mechanisms as well as the deviators and associated components. The internal deviator 28 is in the down position and deviator springs 30 are armed (compressed). External deviator 29 is in the up position held there by swivel rod 31 which itself is controlled by the internal deviator 28. The channel is therefore straight and guide pin 23 on active elevator 19 travels with no deviation. Despite the fact that deviator springs 30 are armed the internal deviator 28 is held in the down position by locking pin 32 inserted in a hole in the internal deviator and supported by the control body. The locking pin is held in the hole in the internal deviator by a spring not shown in the diagram. [36] In Fig. 11 , locking pin 32 has been pulled out of the hole in the internal deviator 28, which due to the action of the deviator springs 30 has moved to the "up" position. This forced the attached swivel rod 31 to swivel forcing the external deviator 29 down. Due to the shape of the deviators a deviation is thus created in the channel.

The critical movement occurs when guide pin 23 reaches this point. It follows this deviation, the active elevator is displaced accordingly and gear-ratio change is brought about. [37] Fig. 12 demonstrates the deviators from a different angle, when the channel is straight. The internal deviator 28 is down and the external deviator 29 is up. The inner end of locking pin 32 is in the hole in the internal deviator holding it in place. The locking pin itself is held in position by a spring not shown. The outer end of locking pin 32 is attached to an axle 33 which itself is supported in a pivoted fashion by the locking arm 34 of the angular lever 35. The angular lever is supported on the control body in a pivoted fashion so that when the control arm 36 of the angular lever 35 is pushed "down" to approach the locking pin, the locking arm 34 is pushed away from the internal deviator 28 thus pulling the locking pin 32 out of the hole in the internal deviator thus releasing the deviator springs and forcing the deviators to change their positions.

[38] Fig. 10 demonstrates the rectifier roller 37. This is a component which rolls in the inner part of the control body parallel to the channel and a small distance from it. The rectifier roller is attached to the body of the central gear and is thus indirectly as- sociated to the active elevator and is another client servant. During normal function of the transmission when there is no deviation in the channel, the rectifier roller rolls just above the rectifier plate 38 of the internal deviator, without depressing it. It also rolls just above the control arm 36 of the angular lever 35 without depressing it. An interceptor component 39 is pivotably attached to the angular lever as shown in Fig. 12. When gear-change is needed, the handle 40 of the interceptor is displaced and this causes a displacement of the control arm 41 of the interceptor. Normally the control arm of the interceptor is outside the path of the rectifier roller. During displacement of the handle 40, the control arm 41 of the interceptor component 39 either moves away from the path of the rectifier roller 37 or it moves into the path. If the displacement is such that it enters the path of the rectifier roller, the roller rolls over it and the first interaction step takes place. The control arm 41 of the interceptor together with the control arm 36 of the angular lever are displaced down towards the locking pin. The spring is released and this sets off the process for gear-ratio change as described above. [39] Fig. 13 demonstrates the control mechanism as well as some of the support structures including support rod 42 which is on the axis of rotation and pivotably supports the central gear 10. Support rod 42 also pivotably supports the gear change component 43. Gear-ratio change is initiated by movement of the gear-change component handle 44 in either direction depending on the direction of the gear-change required.

[40] The sequence of events leading to a change in gear-ratio demonstrates the main steps of the disclosed method. The first step, the "intention" step is displacement of the gear-change component handle 44 as shown in Fig. 13. Displacement of the handle causes displacement of both gear-change arms 45 which are associated with and cause displacement of both interceptor handles 40. One interceptor handle will cause its corresponding interceptor control arm to move away from the path of the rectifier roller and the other will cause its corresponding interceptor control arm to move into the path of the rectifier roller. Which one of the two arms moves into the path of the rectifier roller depends on the direction of displacement of the gear-change component handle 44 and this also determines whether we get up-gear shift or down-gear shift. The intension step results in one of the interceptor control arms entering the path of the rectifier roller but does not cause any other movement or change. Its timing is therefore flexible in accordance with the disclosed method.

The next step is an interaction step and begins after the rectifier roller has traveled beyond the mid position of the rectifier plate of the internal deviator, when it rolls over the control arm 41 of the interceptor component. This depresses it as well as the control arm of the angular lever 36 just below it. The results is outward displacement of the locking arm 34 of the angular lever which pulls on the locking pin 32; This in turn releases the internal deviator which is pushed up by the deviator springs. This way an all-or-nothing process is involved hi the first interaction step. [41] The rectifier roller rotates a few degrees behind the guide pin. The deviators have to reach their final positions fully by the lime the guide pin completes the circle and is intercepted by them. This tune can be calculated scientifically and exactly and depends directly on the speed of rotation of the central gear. The response time of the springs can also be calculated and predicted exactly. It can also be altered and modulated by altering the strength of the springs. In any case it can be exactly predicted that for a specific spring strength there will be a definitive range of rates of rotation of the central gear which will give enough time for the deviators to complete their displacement, thus avoiding any clashes. Consequently, once the transmission is manufactured, it works mechanically like clockwork and no more calculations are needed during operation.

[42] Once the guide pin reaches the displaced deviators the second interaction step takes place and brings about the critical movement. It is displaced by the deviators thus displacing the active elevator and bringing about gear-ratio change in an exact and absolutely controlled and predictable manner. During and after gear change the central gear and the control mechanism shift towards one or the other complementary gear as described in patent application PCT/CY2007/000005. It can be arranged so that the shift of the central gear at gear-change is in the same direction and equal to the original displacement of the handle of the gear-change component that caused the gear-change. This way, once gear change has occurred, the handle of the gear-change component, even though it stays in the same special position, in relation to the control mechanism it is displaced to its neutral position thus pulling the control arm of the interceptor out of the path of the rectifier roller. [43] In the case of this example it is necessary for the components that brought about the critical movement to return to their original positions. This is an optional step of the disclosed method but when it is needed it is brought about by a client servant which in this case is the rectifier roller. Once the control pin rotates past the deviators the rectifier roller rolls onto the rectifier plate 38 of the internal deviator 28 and pushes the internal deviator down thus compressing, "loading", the rectifier springs 30 and forcing the external deviator 29 up through the action of the swivel rod 31. The locking pin 32 then locks in the hole in the internal deviator. The channel becomes straight and remains straight and stable until the next intention step. Component 59 as shown in Fig. 14 is a balance component to ensure centrifugal stability. [44] Another step can be added to the method to increase greatly the maximum range of rate of rotation of the central gear for a given rectifier spring strength. This is the enforcer step. Fig. 14 demonstrates the control mechanism with the addition of enforcing levers 46. There is one enforcing lever for each internal deviator. As shown in Fig. 14, the enforcing lever for each internal deviator is outside the path of the rectifier roller and "up", which means it is protruding internally from the central body, when the internal deviator is depressed and the channel is straight. During normal function the rectifier roller does not intercept any enforcing lever. In Fig. 15 the central body has been removed to demonstrate the enforcing levers 46 and their relation to the internal deviators. Each enforcing lever is pivoted on a helical gear 47, or any other helical component. As a result when the internal deviator is released and starts to travel upwards, the enforcing lever not only starts to travel away from the centre of the central body but it also travels forwards and into the path of the rectifier roller. Therefore, once the internal deviator is released, the enforcing lever enters the path of the rectifier roller. Ideally by the time the rectifier roller would roll over the enforcing lever, the lever should have moved outwards and be hidden inside the control body. If, however, for any reason there is a delay, then just before the guide pin would enter the region of the deviators, the rectifier roller rolls over the enforcing lever forcing it outwards and thus forcing the internal deviator fully up and consequently the external fully down thus forcefully completing the specific interaction step.

[45] Fig. 16 demonstrates one embodiment of the transmission described in patent application PCT/CY2007/000005. In this embodiment the structures with rotational symmetry that keep the complementary gears 48, 49 aligned with the complementary gears comprise channels 51, 52, 53, 54 within the central gear 50 and the complementary such structures comprise discs 55, 56 fixed to the complementary gears. This arrangement allows space for the cutting tool to create the gear teeth in the central gear with greater ease. The line joining the secondary sites of the composite gears could be a relatively straight line 55. It could, however, be a line 56 that is not straight 57, 58 as long as it does not hinder the movement of the elevator during gear change. The direction of movement of the elevator hi Fig. 16 is indicated by the arrow. This is an option that the manufacturer may use hi some instances to ensure that the line joining the secondary sites does not cut through the contact surfaces of the gears. The need to do this may also depend on whether spur gears, helical gears or other gears are used. On such occasions there could be portions of the line for example between points 57 and 58 where surface tension of the oil may hinder the onset of the critical movement for gear change. An optional step in the disclosed method is to ensure that such portions are situated in the spaces between the composite gears and make sure that there is a gap thus avoiding oil surface tension. [46] The method can be used in trams as well as other mechanical and electromechanical assemblies. In the case of a train, examples of the intension step could include the utilization of components which are moved into the path of the train or the energizing of a sensor which will react when it is triggered by the train. The first interaction step could involve the mechanical release of a loaded spring or if a sensor is used, the release of the spring by the use of an electromagnet. The released spring then, pulls the switch rails to the new position. The enforcer step could involve mechanical components, situated at safe distance before the railroad switch, which are intercepted by the train only if the switch rails are in an intermediate position when the train reaches these components. The next interaction step is the train going through the railway switch and changing direction. For the next interaction step, suitable mechanical components can be placed ahead of the railway switch at a distance longer than the length of the train. When the train intercepts these components the switch rails are pushed to their original positions and the springs are tensioned again. This method does not compete with or abolish interlocking which can also be used at the same time.

Modes for Invention [47] The embodiments described above were described just to demonstrate the main features of the invention. The invention is very versatile and the ideas and methods described can be embodied in a multiplicity of ways. For example, in the embodiment described to control gear change in a variable transmission, the internal deviator could be in two parts a first and a second part. The same could be true for the external deviator. The first and second parts could be separated by a specific distance. This would allow for the presence of two channels between the first and the second parts and the channels could be apart at any distance. When both internal deviators are down and both external are up the guide pin travels through the straight channel. When the positions of the deviators is reversed the guide pin is guided to the second channel, it travels for a specific distance in that channel and then encounters the second parts of the deviators and is guided back to the original channel. This embodiment is more complicated but has the advantage that there is no limit to the distance the two channels can be apart.

[48] Mainly mechanical components were used in the examples above. However, the disclosed method is not restricted to mechanical components. For example, electrical and electronic components like sensors, electromagnets, relays and electric motors can also be used in most of the steps. As mentioned above ball bearings can be used to ensure stability and diminish friction. Also damping mechanisms can be used to make movement of various components smoother.

Industrial Applicability [49] Examples of industrial applicability of this invention have been given above. In general the method disclosed in this invention can be used in all circumstances where there could be a clash of mechanical components as described above. It can also be used to eliminate indecisive steps. For example, in transmissions, it can stop the operator, whether the operator is human or an automated system from hovering between one gear and the next. It ensures that the process is all-all-nothing. It also can stop the operator from initiating a new process while the previous one is still being executed thus avoiding possibly catastrophic clashes and accidents. This invention can be used in a wide range of mechanical and electromechanical assemblies to ensure that critical movements of components are commenced and completed in good time to avoid any collisions or clashes. It does so using simple steps which can be just mechanical making the process cheaper to manufacture and more reliable. Used appropriately, this method can save time, money and injury. Sequence List Text

[50]

Claims

[1] A method to be used to control the change in the relative position of various components in any mechanical and electromechanical assembly or collection of assemblies while a primary movement is in progress, where this change in the relative position of various components, referred to as "critical movement", has to be performed and completed within a specific time limit to avoid damage, clash or any other unwanted result, characterized by the use of each of the following steps at least once: a step which is operator dependent and represents the intension of the operator to set the change sequence in motion, referred to as the "intension" step which in itself does not directly bring about the critical movement; a step, referred to as "interaction" step, which is brought about by interaction of a component with the intension step or another interaction step, where the component, referred to as "client servant", is associated directly of indirectly with components involved in the primary movement; and a step utilizing an all-or-nothing process such as release of apre-tensioned "loaded" spring or any other process in which potential energy is released in an irrevocable way.

[2] The method according to claim 1 further characterized by the addition of at least one or more of the following steps: a step, referred to as "enforcer step", which ensures the timely completion of one or more of the other steps by interaction of a component or of components with a client servant; a step involving modifications to the mechanical or electromechanical assembly to ensure correct function of the assembly before, hi preparation for and during a critical movement; and an interaction step that returns the relevant components to their original positions.

[3] The method according to claim 2, used to control the change of gear in a variable transmission as described in international patent application PCT/ CY2007/000005 characterized by the use of the following steps: an intension step to initiate the process; an interaction step in which specially designed components, associated with pre-tensioned springs, are released; and an interaction step where a client servant interacts with the released components to bring about the critical movement that leads to gear-change.

[4] The method according to claim 3 characterized by the addition of at least one or more of the following steps: an enforcer step where through interaction of a client servant with specially designed components, the completion of other interaction steps is speeded up and completed on time; and an interaction step where through the interaction of a client servant on a component, the various components used to bring about the critical movement are shifted to their original positions and the springs are tensioned "armed" again.

[5] The method according to claim 4 further characterized by involving one or more of the following modifications to the transmission to ensure correct function before, in preparation for and during gear-change: the use of a channel and a guide pin (23) that engages both sides of the channel, as a method to enforce alignment of the relevant components; the creation of spaces in the line that separates the elevator or elevators from the body of the central gear to decrease resistance during the onset of gear-change; and the use of a balance component (59) to ensure centrifugal stability. [6] A device to be used to control gear-change in transmissions such as the variable transmission of international patent application PCT/CY2007/000005, comprising a control body (27) attached to the support structures and components (23) attached to the elevator and the central gear, characterized by comprising: a channel (26); a guide pin comprising a specially shaped axis (24) and at least two guide rings (25) thus engaging and rolling on both walls of the channel; at least one internal (28) and one external (29) deviator for each mechanism used on the control body(27); and a swivel rod pivotably attached to each internal deviator and each external deviator ensuring that when one is up the other is down and vice versa. [7] The device according to claim 6 further characterized by comprising: a set of springs associated with each internal deviator; a locking pin (32) which holds the corresponding internal deviator in position during ordinary function of the transmission; and an angular lever (35) comprising a control arm (36) which when depressed moves a locking arm (34) which pulls on the locking pin (32) which is pivotably attached to it, which as a result moves and releases the internal deviator (28). [8] The device according to claim 7 further characterized by comprising: a rectifier roller (37) associated with the central gear; and a rectifier plate (38) on the internal deviator on which the rectifier roller rolls to push the internal deviator to its original position after gear-change. [9] The device according to claim 8 further characterized by comprising: an interceptor component (39) pivotably attached to each angular lever (35), each interceptor component comprising a handle (40) which when moved in one direction pushes the control arm (41) of the angular lever into the path of the rectifier roller, which can then roll over it thus displacing it and the underlying control arm (36) of the angular lever (35); and a gear-change component (43), pivotably attached to one of the support structures of the transmission (42), comprising a handle (44) which when moved causes movement of the gear-change arms (45) which in turn cause displacement of the handles of the interceptor components. [10] The device according to any of the claims 6 to 9 further comprising at least one or more of the following: a balance component (59) which ensured centrifugal balance of the transmission during normal function; the use of gaps along the interface of moving parts of the transmission to decrease resistance to gear-change; the use of ball bearings between moving parts to reduce friction; and the use of components which ensure oiling of the moving parts.