Patent Application
20160017974
The invention relates to a valve closing device having a driven shaft and having an input shaft which is coupled to the driven shaft and by means of which the driven shaft is drivable in normal operation, and having an emergency drive, wherein the driven shaft is transferrable additionally by the emergency drive from a position of use into an end position.
The invention further relates to a valve actuating assembly having an actuating drive for actuating, in the event of mains operation, a driven shaft which is operatively connectable or operatively connected to a valve and having a valve closing device for actuating the driven shaft in the event of mains failure.
These types of valve closing devices are known, for example, from technical systems in which a mass flow is controlled or regulated by means of valves. In this connection, the valves are actuated in normal operation by way of corresponding actuating drives. In the event of a mains failure, for example in the event of an electric power failure or in the event of a failure of a hydraulic or pneumatic supply to the actuating drives, the valve closing devices serve for the purpose of transferring the driven shaft into a pre-defined end position in order to transfer the valve connected in each case into a defined end state, for example into an open state or a closed state.
In order to be independent of the power supply via the already mentioned mains system, it is known in the event of mains failure to store the energy that is necessary for transferring the driven shaft into the desired end position in a mechanical manner in a spiral spring or a coil spring.
The known valve closing devices are used as an assembly part or are integrated into valve actuating assemblies of the type described in the introduction.
A defined torque is necessary, as a rule, to actuate the valve. In the case of the known emergency drives with mechanical energy storage in a spiral or coiled spring, the torque that can be developed by the emergency drive to actuate the driven shaft reduces during the energy releasing operation. The spiral or coiled spring consequently has to be sized such that there is still enough torque developed even at the end of the actuation movement. Conversely, this means that a tensioning device for tensioning the emergency drive has to be sized large enough such that even the spring force close to the tensioned state of the emergency drive is overcome. This tensioning device consequently has to be sized large enough, as a rule, such that a multiple of the torque that is actually necessary for actuating the driven shaft is able to be developed. The emergency drive is frequently tensioned by means of the already mentioned actuating drive for normal operation, the result of which is that the actuating drive is oversized for its usual tasks.
The object underlying the invention is to reduce the sizing requirements for a valve actuating assembly.
To achieve said object one or more features according to the invention are provided. In particular, consequently, it is provided according to the invention in the case of a valve closing device of the type described in the introduction that the emergency drive is realized as at least one constant force spring motor. Constant force spring motors are known per se and are used, for example, in toys or in cable rewind drums, blinds and many more things. They are distinguished from other storage means for mechanical energy as a result of the developed torque being almost constant or even precisely constant over the energy releasing operation. They are consequently also designated as constant force springs. The advantage of using at least one constant force spring motor in the case of an emergency drive of the valve closing device of the type described in the introduction is that a lower maximum torque is necessary during the tensioning of the emergency drive. This is due to the fact that the necessary torque at the start of the tensioning operation only has to be slightly above the torque that is necessary to actuate the driven shaft. During the course of the tensioning operation, this necessary torque is substantially constant such that it is not necessary during tensioning to develop a multiple of the required torque of the emergency drive. As a result, the sizing of the emergency drive and of a tensioning device of the emergency drive can be clearly smaller than has been usual up to now.
The valves addressed here where the invention can be used in an advantageous manner can be, for example, a valve or a ball tap. The valve is consequently adjustable by way of the emergency drive and by means of an actuating drive which is connectable or connected to the input shaft as an alternative or at the same time.
In the case of a development of the invention, it can be provided that the at least one constant force spring motor is tensionable by way of the input shaft. The advantage in this case is that an additional tensioning device can be omitted. Rather, the at least one constant force spring motor is tensionable in normal operation by way of an actuating drive that is connected to the input shaft.
As an alternative to this or in addition to it, it can be provided that the at least one constant force spring motor is tensionable by way of a device. The tensioning device is preferably electrically operated, however hydraulic or pneumatic tensioning devices can also be used in an advantageous manner. The advantage of the development with a tensioning device is that the sizing of a connected actuating drive can be chosen independently of the emergency drive and can be matched to the respective requirement of the connected valve.
In the case of a development of the invention, it can be provided that the at least one constant force spring motor comprises at least one band-shaped spring element. The advantage here is that the at least one band-shaped spring element can be tensioned or untensioned in a simple manner for developing the desired torque and for tensioning.
In this connection, it can be provided that the at least one band-shaped spring element is coiled in a spiral manner in an energy-released state. It is particularly expedient when, for tensioning the at least one constant force spring motor, the at least one band-shaped spring element can be wrapped and is wrapped around at least one further roller from the spiral-shaped coiling of the energy-released state. To achieve a higher torque, at least two, in particular at least three or more than three, band-shaped spring elements can be wrapped and are wrapped around one common roller for the tensioning in each case of one associated roller. In this connection, the at least two band-shaped spring elements can cooperate with the commonly utilized roller at target points which are offset with respect to one another in the circumferential direction of the commonly utilized roller. It can be achieved as a result that the at least two band-shaped spring elements, in the wrapped around state or the tensioned state, are tensioned on top of one another in such a manner in a common axial portion of the commonly utilized roller that an at least double-flight winding is formed. It can also be provided conversely that, for tensioning, at least two, in particular at least three or more than three, band-shaped spring elements can be tensioned and are tensioned from one common roller onto in each case a roller that is associated with the individual spring elements. In this connection, the at least two band-shaped spring elements can form an at least double-flight winding in the energy-released state. The terms “axial”, “radial” and “in the circumferential direction” refer to the respective roller in this description. It can also be provided that the at least two band-shaped spring elements can be tensioned and are tensioned around pairs of rollers that are separated from one another, one roller of a pair of rollers being coupled with a roller of at least one other pair of rollers, for example as a result of an arrangement on a common shaft.
It is particularly expedient when the roller is operatively connected to or coupled with a drive shaft of the emergency drive, from which the at least one spring element is untensioned when the energy is being released. The advantage in this case is that said roller is consequently subject to tensile stress for driving.
It can consequently be provided that the at least one constant force spring motor is tensionable as a result of untensioning at least one spring element, for example the already mentioned at least one band-shaped spring element. In a preferred manner, in this connection, the at least one spring element can be untensioned from a first roller. The torque that the emergency drive develops in its operation depends consequently on the diameter of said first roller. In the case of a correspondingly thin at least one spring element, the roller diameter is only changed insignificantly during tensioning or untensioning. This is particularly beneficial for constant torque generation.
For storing the mechanical energy, it can be provided that in a tensioned state at least one spring element, for example the already mentioned at least one spring element, of the at least one constant force spring motor is tensioned in opposition to a preferred tensioning direction. To this end, it is possible to provide a second roller, around which the at least one spring element can be tensioned and is tensioned for tensioning the at least one constant force spring motor.
In the case of a development of the invention, it can be provided that the emergency drive comprises at least two constant force spring motors connected in parallel. The advantage in this case is that the torque to be developed can be applied by several individual drives. Consequently, it is achievable for the individual constant force spring motors to have to apply a smaller torque in each case and to be able to be designed consequently for a smaller torque. Motors connected in parallel is to be understood in this connection as an arrangement in which the torque developed by the individual motors is added up. In this connection, the motors can drive, for example, one common toothed part or several toothed parts which are coupled together in a rigid manner and are associated in each case with one motor.
In this connection or in the case of a further development of the invention, it can be provided that the at least one constant force spring motor drives the driven shaft by means of a gearing arrangement. The advantage in this case is that a torque developed by the individual constant force spring motor is adaptable to a necessary torque for actuating the output. It is expedient in this connection when the gearing arrangement is realized as a reduction gearing arrangement. It is advantageous in this connection for a large torque to be able to be developed and applied onto the driven shaft. In a preferred manner, the gearing arrangement is a multi-stage reduction gearing arrangement. Consequently, large gear ratios can be realized in a small space.
The described arrangement of at least two constant force spring motors connected in parallel and/or of at least one constant force spring motor coupled by means of a reduction gearing arrangement results in the individual constant force spring motors only having to apply a small torque. The advantage of this is that the rollers onto which the spring elements are tensioned or from which the spring elements are untensioned, can be realized with a larger diameter. This extends the service life of the constant force spring motor or of the constant force spring motors in a considerable manner as the spring elements are subject to less load. For many applications the service life achievable with smaller diameters is, however, sufficient such that the advantage of a smaller installation space that is present in the case of these variants prevails.
The parallel arrangement of several constant force spring motors, for example two, three, four or more than four, for example ten or more than ten, constant force spring motors, can be set up such that the torque developed by one constant force spring motor is not sufficient to actuate the driven shaft. This results in contrast in a redundant design, where each constant force spring motor could actuate the driven shaft on its own, with the purpose of the constant force spring motors together not being able to exceed a maximum required or admissible torque. In other words, the design takes into consideration the fact that the individual constant force spring motors are not separately disconnectable.
The advantage of using the constant force spring motors connected in parallel is that it is possible to realize a modular system where, depending on the requirement, individual or several constant force spring motors can be used. In this way, it is possible to cover or reproduce a step range of torques for actuating drives. For example, a step range of 60 Nm, 120 Nm and 240 Nm can be realized.
A solution according to the invention of independent inventive significance provides in the case of a valve closing device of the type described in the introduction that the emergency drive is coupled with the driven shaft by means of an overriding gear arrangement. The advantage in this case is that the tensioning of the emergency drive and the connecting of the emergency drive in the event of mains failure are realizable in a simple manner. In this connection, an overriding gear arrangement is to be understood as a gearing arrangement with two input points and one driven shaft, the torques admitted by means of the input points in each case—where applicable by means of a gear ratio—being provided totaled up at the driven shaft. It is possible to dispense with couplings in the power train of the emergency drive by using an overriding gear arrangement. It is particularly expedient when the overriding gear arrangement is realized as a differential gearing arrangement or as an epicyclic gearing arrangement, in particular as a four-wheel planetary gearing arrangement in a basic design or with a method of operation describing a power train, it being possible to have additional planetary wheels for reinforcement. In this case, the mentioned input points are provided by an input shaft and a planet gear carrier. It is particularly expedient when the emergency drive, in the case of a valve closing device of the type described initially according to the invention is provided. The advantage in this case is that the described preferences of the constant force spring motor are able to be combined with the described coupling of the torque from the emergency drive in the event of mains failure. A usable epicyclic gearing arrangement can be characterized, for example, in that there are two sun wheels which are preferably coaxially arranged, a first of the sun wheels being connected to an input shaft and a second of the sun wheels being connected to an output shaft of the overriding gear arrangement and the sun wheels being coupled together by means of at least one planetary wheel block. The at least one planetary wheel block, in this connection, can comprise a single planetary wheel which meshes with the two sun wheels or two planetary wheels which are coupled rigidly with one another on one shaft and in each case mesh with only one of the two sun wheels. In a preferred manner, the number of planetary wheel blocks arranged along the circumferences of the sun wheels corresponds precisely to a difference in the number of teeth between the individual sun wheels with respect to one another. It is particularly expedient when each planetary wheel block comprises a standard number of teeth. It is advantageous when using epicyclic gearing arrangements that between the input shaft and the output shaft of the overriding gear arrangement a gear ratio of almost one can be set up. It is further advantageous in the case of the described type of overriding gear arrangement that a direction of rotation between the input shaft and the output shaft is maintained and, in particular, a reversal of direction of rotation is avoidable. A gear ratio that lies between 0.8 and 1.2, in a preferred manner between 0.9 and 0.95 or between 1.05 and 1.1 is favorable. It is further advantageous that the emergency drive, for example a constant force spring motor of the described type, is couplable to the output shaft by means of a planetary carrier which carries the at least one planetary wheel block. Here, speed reducing gear ratios of more than 8, in a preferred manner 10 or more than 10, for example 15, from the emergency drive to the output shaft are achievable. Consequently, the emergency drive can develop a necessary, comparatively high torque by means of the output shaft in order to close or to open a valve or to set it in general.
In the case of a development of the invention, it can be provided that the input shaft and the driven shaft are coupled by an overriding gear arrangement, for example the overriding gear arrangement already mentioned. It is advantageous in this case that a simple option is created to couple an emergency drive into the power train between the input shaft and the driven shaft.
In the case of a development of the invention, it can be provided that the emergency drive drives a planet gear carrier of a, in particular of the already mentioned overriding gear arrangement. The advantage is this case is that a gear ratio of almost or precisely 1:1 can be set up between the input shaft and the driven shaft. This is particularly favorable in order to be able to achieve the same sizing (nominal torque, nominal speed etc.) of the connectable actuating drive as would be necessary without the described valve closing device (i.e. without the additional emergency drive). As a result, simple in-retro-fitting is possible, for example in the case of an existing actuating drive-fitting combination.
In the case of a development of the invention, it can be provided that a regulating device is present and is set up for regulating a tensioning device of the emergency drive in such a manner that a rotational movement of the input shaft is compensatable such that a desired rotational movement, in particular a standstill, of the driven shaft is stopped when the emergency drive is tensioned. For example, the desired rotational movement can be a rotational movement at a speed of zero, this means a standstill, or a rotational movement at a constant speed. The advantage in this case is that it is possible to tension the emergency drive without adjusting the valve. This is particularly advantageous when tensioning the emergency drive forcibly involves a rotational movement or pivoting movement or linear movement of the associated input point on the overriding gear arrangement, as is the case, for example, with a constant force spring motor.
Associated herewith consequently is a regulating method of possibly independent inventive quality where a speed and/or a torque of a tensioning device is adjusted such that a rotational movement (here introduced by an actuating drive) on an input shaft of an overriding gear arrangement is compensated for such that a driven shaft of the overriding gear arrangement, which is monitored preferably by way of a sensor, carries out a desired rotational movement, for example a constant rotational movement or a standstill. Instead of or in addition to the rotational movement of the driven shaft, the movements at the input points of the overriding gear arrangement can also be monitored and are monitored by way of respective sensors. By way of the known or filed gear ratios of the overriding gear arrangement, it is possible, as a result, to determine the rotational movement of the driven shaft for monitoring purposes.
In this connection it can be provided that there is present a sensor which is set up for detecting a rotational movement of the driven shaft. In a preferred manner, the sensor is operatively connected to the regulating device. Consequently, a regulating circuit is formable and is formed in the case of a development.
In the case of a development of the invention of independent inventive significance, it is provided in the case of a valve closing device of the type described in the introduction that a locking device is set up for locking the emergency drive in the event of mains operation and/or for releasing the emergency drive in the event of mains failure. The advantage in this case is that the emergency drive is deactivatable in a simple manner in normal operation. For example, it can be provided in this connection that the locking device automatically releases the emergency drive when a mains failure is ascertained. The locking device, in this connection, can be set up to interrupt the power train in one sense of direction or in both senses of direction.
In the case of a development of the invention, it can be provided that the locking device is realized as a self-locking gearing arrangement which is drivable by the emergency drive. The advantage in this case is that it is achievable in a simple manner for the emergency drive to be uncoupled from the main train between the input shaft and the driven shaft. A separate tensioning device can be provided for tensioning the emergency drive, insofar as it is mechanically driven. However, it can also be provided that the emergency drive is driven in a pneumatic, electric or hydraulic manner.
In the case of a development of the invention, it can be provided that the locking device comprises a pawl which is movable between a locking position and a releasing position, wherein the pawl interacts in a locking manner in the locking position with a gearing part which is drivable by the emergency drive. Consequently, it is achievable for the locking device to block the emergency drive or the already mentioned overriding gear arrangement or a further gearing part in the power train between the emergency drive and the driven shaft in a locking manner.
In the case of a development of the invention, it can be provided that the gearing part is a planet gear carrier, for example the already mentioned planet gear carrier of an overriding gear arrangement. The advantage in this case is that in a simple manner it is possible to control whether a torque developed by the emergency drive strikes the power train between the input shaft and the driven shaft or not.
In the case of a development of the invention, it can be provided that a disengaging device is set up for transferring a pawl, for example the already mentioned pawl, into the releasing position. The advantage in this case is that the locking of the locking device is releasable in a simple manner. It is particularly favorable when the disengaging device is motor-operated. This can be set up so as to be motor-operated in an electrical, pneumatic, hydraulic or other manner.
In the case of a development of the invention, it can be provided that a, in particular the previously mentioned, disengaging device, of a, in particular the previously mentioned, pawl of the locking device is realized as a lifting magnet. The advantage in this case is that the disengaging device is holdable in the locking position in an electromagnetic manner such that in the event of a mains failure the locking device automatically actuates the power train from the emergency drive. The lifting magnet, in this connection, can be coupled with a return spring.
In the case of a development of the invention, it can be provided that the pawl is realized on the free end of a toggle lever. The advantage in this case is that with a toggle lever in the extended state a high level of holding force can be developed. Conversely, when a toggle lever is used, there is the advantage that an initial force to disengage the pawl out of the extended state of the toggle lever has to be low. A toggle lever is to be understood in general as two legs which are pivotably interconnected and are pivotably mounted on an end remote from the connected joint, the other end remote from the connecting joint being realized as a free end.
In the case of a development of the invention, it can be provided that a, for example the previously mentioned, disengaging device of a, for example the previously mentioned, locking device cooperates with a joint of the toggle lever. In a preferred manner, the disengaging device cooperates in a transverse manner with respect to the extended toggle lever. The advantage in this case is that the force developed by the disengaging at the start of the disengaging movement is transferrable to the pawl at a high gear ratio, the gear ration decreasing during the course of the disengaging movement. Consequently, the pawl can also be disengaged when the locked gearing part acts on the pawl with a force or a torque and thus prevents a movement of the pawl.
One or more features are provided according to the invention to achieve the named object in the case of a valve actuating assembly. The advantage in this case is that an actuating drive of the valve actuating assembly can be sized as small as possible and that the emergency drive is connectable and separable from the power train between the input shaft and the driven shaft in a simple manner.
In the case of an advantageous development, it can be provided that the valve closing device is integrated into the actuating drive. The advantage in this case is that a compact valve actuating assembly is provided.
As an alternative to this or in addition to it, it can be provided that the valve closing device is connected releasably to the actuating drive as a separate unit. The advantage in this case is that the valve closing device can be fitted in retro and in that a valve closing device is combinable with a plurality of actuating drives in order to form a valve actuating assembly according to the invention.
In the case of a development of the invention, it can be provided that a valve for producing an operative connection is connected to the driven shaft. The advantage in this case is that the valve actuating assembly is usable for use in a technical system with a valve that regulates mass flow.
The invention is now described in more detail by way of exemplary embodiments, but is not limited to these exemplary embodiments. Further exemplary embodiments are produced as a result of the combination of the features of individual or several claims together and/or with individual or several features of the exemplary embodiments, in which:
The valve actuating assembly 1 has an actuating drive 2 by way of which a connectable or connected valve 3 can be operated.
The actuating drive 2, in this connection, comprises in a manner known per se a motor 4 by way of which an output 5 is drivable.
The motor 4, in this connection, can be drivable in an electric, pneumatic, hydraulic or other manner.
A brake 6 and a gearing arrangement 7 are also arranged in a known manner per se between the motor 4 and the output 5. The power train between the motor 4 and the output 5 can be interrupted by way of the brake 6. The brake 6 can be omitted, where applicable, when the gearing arrangement 7 is self-locking.
A valve closing device 8 according to the invention, which is described in more detail below, is arranged between the actuating drive 2 and the valve 3.
The valve closing device 8 comprises a driven shaft 9 to which the already mentioned valve 3 is connectable for producing an operative connection.
The valve closing device 8 also has an input shaft 10,
The already mentioned actuating drive 2 is couplable to the input shaft 10.
The input shaft 10 is coupled with the driven shaft 9 such that the driven shaft 9 is drivable by way of the actuating drive 2 in normal operation in order to actuate the valve 3 or another connected valve.
The valve closing device 8 further comprises an emergency drive 11. In the event of mains failure, that is if the actuating drive 2 is inoperative, the driven shaft 9 is drivable by way of the emergency drive 11 which is driven by way of the electric motor or mechanically, pneumatically or hydraulically at least until the driven shaft 9 is transferred into a defined end position.
This end position can be defined such that a connected valve assumes a defined end state, for example a completely closed state or a completely open state.
The symbol “x” indicates that the power train between the motor 4 and the input shaft 10 is blocked. This can be achieved, for example, as a result of the brake 6 automatically coming in in the event of a mains failure.
In this case, it is provided that the emergency drive 11 drives the driven shaft 9 in the described manner.
In the case of the exemplary embodiment shown, the emergency drive 11 is realized for mechanical operation as a constant force spring motor.
Such a constant force spring motor 28 as an emergency drive 11 is shown in
The emergency drive 11 has a first roller 12 onto which a band-shaped spring element 13 is coiled.
It is obvious that the spring element 13 is coiled in a spiral manner on the first roller 12.
The emergency drive 11 has a second roller 14 which does not have anything wrapped around it in the tensioned state according to
To tension the emergency drive 11, the band-shaped spring element 13 is consequently coiled onto the first roller 12.
In this connection, the spring element 13 is unrolled by the second roller 14. The spring element 13 is consequently coiled onto the first roller 12 from the second roller 14.
During the coiling process, the first roller 12 and the second roller 14 are moved in opposite directions.
The achievement as a result is that in the tensioned state of the emergency drive 11, that is when the spring element 13 is completely tensioned onto the first roller 12, the spring element 13 is coiled in opposition to a preferred direction of rotation.
If the emergency drive 11 is then left to its own devices, the tension in the spring element 13 is released by it being coiled onto the second roller 14.
As a result of the resultant movement of the first roller 12 or of the second roller 14, the driven shaft 9 is driven until the desired end position is reached.
In the case of the valve closing devices 1 shown according to the invention, a constant force spring motor 28 according to
The statement relating to
The constant force spring motor 28 of the emergency drive 11 according to
A tensioning arrangement in which the spring elements 13 form a double-flight winding is produced as a result, i.e. a winding in which the spring elements 13 form layers which follow one after another alternately in the radial direction.
When the energy is released, each of the spring elements 13 is tensioned around a separate roller 14.
The drive shaft 38 (cf.
In the case of further exemplary embodiments, more than three spring elements 13 cooperate with one common roller 12 in order to form a multi-layered winding in the tensioned state. It can also be provided that said single, double or multi-layered winding defines the energy-releasing state. Here too, it is favorable when the drive shaft 38 is/are coupled with the roller or the rollers 12, 14 which is/are tensioned by the spring element or spring elements when the energy is released.
Another tensioning device 15 can be seen in
Tensioning the emergency drive 11 can also be executable from the operation of the actuating drive 2 without a separate tensioning device 15.
Frequently the size of the reducing gear ratio of the gearing arrangement 20 (no self-locking in this case) is chosen such that it is not possible to tension the emergency drive 11 by way of the motor 4. A tensioning device 15 is present in this case.
In the case of a further exemplary embodiment, tensioning the emergency drive 11 can be made possible and carried out in a combination, that is an interaction, between the actuating drive 2 and the device 15.
The valve closing device 1 comprises a sensor 36 for this purpose. The sensor 36 can be realized as a positioning sensor, speed sensor, torque sensor or in any other manner in order to detect a rotational movement of the driven shaft 9 and/or to differentiate between a standstill of the driven shaft 9.
A regulating device 37 is set up in this connection such that a rotational movement of the input shaft 10 is compensated for by the actuating drive 2 by a movement of the planet gear carrier 17 precisely in such a manner that a desired rotational movement of the driven shaft 9, for example a standstill, is achieved. Consequently, the achievement can be, for example, that the connected valve 3 is not moved during the tensioning of the emergency drive 11. For example, a valve of the valve 2 can be held in the open position or in the closed position in this way.
It can be seen in
From the representations according to
It can be seen in any case that the gear ratio between the driven shaft 9 and the input shaft 10 is one to one.
Planet gears 18 which produce the coupling between the input shaft 10 and the driven shaft 9 are arranged in each case on a planet gear carrier 17.
If the planet gear carrier 17 is blocked, the direct gearing ratio is produced between the driven shaft 9 and the input shaft 10. In this connection, the direction of rotation of the movement is reversed.
The emergency drive 11 cooperates with the planet gear carrier 17 by means of the geared wheel 34 and moves said planet gear carrier.
In this way, the torque introduced at the input point 29 by means of the input shaft 10 can be added to the torque introduced at the input point 29 by the emergency drive 11 by means of planet gear carrier 17.
The exemplary embodiment according to
The overriding gear arrangement 16 is realized in this case as an epicyclic gearing arrangement and has an planet gear carrier 17, in this case realized as a planet carrier which carries planet gears 18 which are realized in each case here as a planet gear. The planet gears 18 form in each case a planet gear block 43.
The overriding gear arrangement 16 has a first sun wheel 44 and a second sun wheel 45 which are aligned coaxially with respect to one another.
The first sun wheel 44 is non-rotatably connected to the input shaft 46 of the overriding gear arrangement 16. The second sun wheel 45 is non-rotatably connected to the output shaft 47 of the overriding gear arrangement 16.
The input shaft 46 of the overriding gear arrangement 16 merges into the input shaft 10 of the valve closing device 8 or is rigidly coupled with said valve closing device.
The output shaft 47 of the overriding gear arrangement 16 merges into the output shaft 9 of the valve closing device 8 or is rigidly coupled with said valve closing device.
The sun wheels 44, 45 mesh in each case with the planet gears 18 of the planet gear blocks 43. As a result, there is a power train between the input shaft 46 and the output shaft 47.
The number of teeth on the sun wheels 44, 45 differs slightly from one another such that there is a gear ratio of almost one, but not precisely one, between the input shaft 46 and the output shaft 47 when the planet gear carrier 17 is held.
In this connection, flank forms, in particular the profile shifts, of the sun wheels 44, 45 are chosen so as to be different such that the points of engagement with the planet gears 18 are the same for both sun wheels 44, 45. The planet gears 18 are in each case integral and consequently comprise in each case a uniform number of teeth.
Consequently, a four-wheel planetary gearing arrangement is formed in the described manner as an epicyclic gearing arrangement.
In the case of further exemplary embodiments, each planetary gear block 43 comprises two separate planetary gears which are coupled non-rotatably on a common shaft and in each case only mesh with one of the two sun wheels 44, 45, as is shown as an example in
In the case of said type of overriding gear arrangement 16 according to
In the exemplary embodiment according to
The emergency drive 11 is coupled to the planet gear carrier 17 by means of the toothed wheel 34. As a result, there is a reduction gear ratio between the toothed wheel 34 and the output shaft 47 of 10 or more than 10. In the exemplary embodiment, the gear ratio between the input shaft 46 and the output shaft 47 with the toothed wheel 34 held is precisely at 1.1, and the gear ratio between the toothed wheel 34 and the output shaft 47 with the input shaft 46 held is precisely at 10. In the case of a further exemplary embodiment, the gear ratio between the input shaft 46 and the output shaft 47 with the toothed wheel 34 held is precisely at 1.066 and the gear ratio between the toothed wheel 34 and the output shaft 47 with the input shaft 46 held is precisely at 15. Other numeral values are also realizable as a result of choosing the number of teeth.
The overriding gear arrangement 16 consequently overrides the rotational movements on the input shaft 46 and on the toothed wheel 34 to form a rotational movement on the output shaft 47. The torques are added up in this connection.
It is obvious that—in contrast to the otherwise similar arrangement according to FIG. 7—the rotational movement between the input shaft 46 and the output shaft 47 is not reversed, but is transmitted in the same direction.
Apart from this, the explanations relating to
In the case of a further exemplary embodiment according to
Apart from this, the statements relating to
It can also be seen in
The emergency drive 11 is lockable during mains operation and releasable in the event of mains failure using the locking device 19.
For this purpose, the locking device 19 comprises a self-locking gearing arrangement 20 which blocks a power train from the overriding gear arrangement 16 to the emergency drive 11, in one sense of direction.
The emergency drive 11, in this case, is not tensioned by the motor 4, but by means of the separate tensioning device 15.
If no self-locking gearing arrangement 20 is present, the emergency drive 11 can be tensioned by means of the overriding gear arrangement 16—for example with the driven shaft 9 held.
As an alternative to or in addition to the self-locking gearing arrangement 20, the locking device 19 comprises a pawl 21 which interacts in a blocking manner with a gearing part 22 in the locking position.
To this end, the pawl 21 engages in a corresponding recess 23 on the gearing part 22. The pawl 21 consequently locks in both senses of direction to the emergency drive 11 and from the emergency drive 11.
When the locking device 19 is released, the gearing part 22 is drivable by way of the emergency drive 11. The pawl 21 consequently blocks the emergency drive 11 in the engaged position.
The power train in normal operation from the motor 4 to the drive shaft 9 is consequently shown. Once again the symbol “x” marks a power train interrupted by locking.
The locking device 19 has a disengaging device 24, by way of which the pawl 21 can be disengaged out of the recess 23 of the gearing part 22.
The disengaging device 24 is realized in this connection as an electrically actuatable lifting magnet. The lifting magnet can comprise a return spring which is not shown in any detail and is known per se.
It is obvious that the pawl 21 is realized on the free end of a toggle lever 25.
From the partially sectioned representation according to
The disengaging device 24 consequently engages in a transverse manner with reference to the direction of movement of the extended toggle lever 25 (cf.
The achievement as a result of using a toggle lever 25 can be that at the start of the disengaging movement a large force can be introduced onto the pawl 21 as the power transmission ratio of the disengaging device 24 to the pawl 21 with the toggle lever 25 extended is very favorable.
Consequently, it is possible to overcome large holding forces at the pawl 21 which are brought about as a result of clamping the gearing part 22.
Components and functional units that are the same or similar functionally and/or structurally to the previously described exemplary embodiments are designated with the same references and are not described again separately. The statements relating to
The valve actuating assembly 1 according to
The advantage of this, for example, is that the gearing 7 and the output 5 are able to be omitted in relation to
In the case of the exemplary embodiment according to
The emergency drive 11 has a drive shaft 38 which can also be seen in the previously described Figures. This drive shaft 38 is non-rotatably coupled with a toothing part 42.
Three constant force spring motors 28, 39, 40 are uniformly distributed along the circumference of the toothing part 42 and cooperate with said toothing part.
In the case of further exemplary embodiments, a different number of constant force spring motors cooperate therewith.
The constant force spring motors 28, 39, 40 drive the common toothing part 42 together such that the individual torques of the constant force spring motors 28, 39, 40 are added up.
The constant force spring motors 28, 39, 40 are consequently connected in parallel together. Each of the constant force spring motors 28, 39 and 40 apply in each case a third of the overall required torque.
Each constant force spring motor 28, 39, 40 is drivingly connected to the toothing part 42 by means of a gearing arrangement 41, here a multi-stage reducing gear for speed reduction.
Apart from this, the function of each of the constant force spring motors 28, 39, 40 taken in isolation is as described previously. The statements consequently apply in a corresponding manner to
In the case of a valve closing device 8 with a driven shaft 9 for connection to a valve 3 and an input shaft 10 for connection to an actuating drive 2, it is proposed, for driving the driven shaft 9 in the event of mains failure, to realize an emergency drive 11 as a constant force spring motor 28 and/or to join a power train from the emergency drive 11 to the driven shaft 9 with a power train from the input shaft 10 to the driven shaft 9 by means of an overriding gear arrangement 16 and/or to lock and to release the emergency drive 11 by way of a locking device 19.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2013 003 810.3 | Mar 2013 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2014/000558 | 3/5/2014 | WO | 00 |
