EP1094479B1 - Mechanism for actuating circuits - Google Patents

Abstract

The device includes an operating shaft (7) coupled to a drive shaft (9) via a gear. A drive may be a manually operated crank handle and/or a drive motor. The gear is a ratchet gear with at least one ratchet wheel (32,33) with ratchet teeth (37), and at least two double ratchets (18,19). Ratchet tips (31) engage with the teeth.

Description

The invention relates to an actuating device for actuating current paths according to the preamble of claim 1. Such an actuating device is known from US-A-3,475,981 known.

For actuators for electrical switching devices, such as. Low, medium or high voltage switching devices, there is the requirement by means of small actuation torques with the interposition of a transmission to provide high torque for the direct actuation of switching assemblies. For this purpose, the actuating means between the drive shaft and the actuating shaft to a transmission. Typical gear ratios of such transmissions amount to at least 1: 400 with motor operation and reach up to approx. 1: 2000, for manual operation approx. 1: 5 to 1: 100. The switching operation of such a switching device may take less than one to several seconds.

Actuators with spur gears are known from the prior art. However, spur gears must have many gear stages in order to realize a corresponding reduction ratio and thus become very expensive, expensive and large. In addition, they have no self-locking effect.

The state of the art also includes actuators with planetary gears. The provision of planetary gears is very costly and it also lacks the self-locking effect.

When using worm gear in actuators you can indeed their Use self-locking properties, but they have a high friction and thus a poor efficiency. In addition, the actuating shaft is offset with the drive shaft crosswise, which is often considered disadvantageous.

For actuators that act in two directions of drive and drive the switching device directly in the input and Ausschalttrichtung, come either reversibly drivable transmission or only acting in a drive direction gear together with a corresponding link coupling used.

The latter arrangements, which, for example, from the DE 196 05 711 A1 in positions 9 to 14 of the Fig. 1 Although have become known, although characterized by a relatively low overall cost, but have a number of disadvantages. So additional components for the handlebar coupling are required. This requires a correspondingly large installation space. In addition, the respective switching operation always presupposes the complete drive movement of the preceding switching operation, which is why an already started switching operation must always be completed. During an already started switching movement is a reversal of the switching movement is not possible.

The present invention is therefore based on the object to propose an actuating device which has an extremely simple and therefore cost-reversible transmission. In addition, the above-described disadvantages of the prior art to be remedied.

The invention solves this problem by an actuating device according to claim 1.

The object according to the invention has the advantage that such a pawl transmission in production and assembly is very inexpensive. In addition, an initiated actuation of the switching operation can be reversed at any time before reaching the respective end position of the switching device. Due to the fact that when a rotating drive shaft in each case a pawl tip is engaged with the ratchet, it is excluded that a return of the ratchet wheel against the direction of rotation of the actuating shaft is possible.

According to an advantageous embodiment of the invention, the ratchet gear teeth on two opposing rows of teeth for receiving the respective engaging in the ratchet gear ratchet tips, wherein the two rows of teeth can also overlap. Depending on the pawl engagement so a left or right rotation of the actuating shaft is generated. In the overlapping areas of the rows of teeth, the teeth must be designed to be acted upon on both sides.

According to a development of the invention, it is provided that the two eccentrics are arranged offset on the drive shaft preferably at an angle of 1800 to each other. As a result, upon rotation of the drive shaft, a uniform engagement and lifting of the pawl tips reached the two double pawls.

In a further development of the invention, the double latches are configured symmetrically. In addition, the pitch of the ratchet teeth is slightly smaller than twice the eccentric center eccentricity to the center axis of the drive shaft. It is assumed that only one ratchet wheel is present on the actuating shaft, or two identical, aligned Rinkenradscheiben.

A particularly preferred development of the invention is characterized in that the two double pawls are designed asymmetrically such that the tooth pitch of the ratchet wheel is slightly smaller than four times the eccentric center of the eccentric center to the central axis of the drive shaft. Such asymmetrical double pawl has a short and a long half of the pawl. Advantageously, the difference between a short and a long half of the catch is slightly more than half of the pitch of the ratchet wheel.

Another embodiment of the invention provides that on the actuating shaft two mutually parallel ratchet wheels are present, with a double pawl on the at least one drive shaft for engagement in each one Ratchet wheel is provided. Depending on the configuration of the switching device can be provided that the two ratchet wheels are identical and are either offset from one another or aligned on the one actuating shaft.

A preferred embodiment of the invention provides that the two double pawls are designed symmetrically, that the rows of ratchet teeth of the two ratchet wheels are offset by half a pitch and that the pitch of the two ratchet wheels slightly smaller than four times the eccentricity of the eccentric center to the central axis the drive shaft is. Such a configuration has the advantage that due to the mutually offset ratchet wheels in symmetrical double pawls, the tooth pitch is not slightly less than twice, but slightly smaller than four times the eccentric center of the eccentric center to the central axis of the drive shaft. Due to such a pitch, the teeth of the ratchet wheel are much more stable, which is particularly important for double-sided loading of the individual teeth of crucial importance.

Another preferred embodiment of the invention provides that the actuating device for Three-position switch is executed and has a current path closing, one the current path separating and a current path connecting to ground switching position. Three-position switches have the advantage that only one movable switching element has two switching functions. In addition, three-position switch space and space saving and therefore cost. They also have the advantage that the earthing function does not require any breaking capacity. Since a three-position switch is an either / or switch, also no locking of the individual switch positions against each other is required.

In a further development of the invention, it is provided that the three-position switch in the neutral position of the actuating shaft separates the current path that closed after a rotational angle of the actuating shaft of about 90 ° in one direction of rotation of the current path and from about 90 ° in the other direction, the current path to earth connected is. Such an arrangement of the three-position switch has proven to be particularly advantageous in practice.

In one embodiment of the invention, it is provided that at least two drive shafts which can be driven independently of one another are provided with eccentrics with double pawls disposed thereon, over which the Actuating shaft is actuated in the various switching positions. Due to the two independently driven drive shafts an unambiguous assignment of a drive shaft is achieved to a switching position. Switching through the actuator in all three switching positions by turning only one drive shaft is therefore excluded.

In a variant of the three-position switch actuator, the ratchet wheels or the ratchet wheel each have only one row of teeth for engaging the double pawls of the respective actuated drive axle, so that a rotation of that drive shaft in the engagement region, the ratchet wheels or the ratchet wheel are not or is without Actuation of the actuating shaft is freely rotatable. This avoids that upon actuation of the one drive shaft, due to the actuation of the other drive shaft, a collision or a blocking state in the actuator is possible.

In a particularly preferred embodiment of the three-position switch actuator is provided that by rotation of a drive shaft, the actuating shaft can only be rotated by a little more than 90 ° and turned back. It is at a further rotation of the corresponding drive shaft, the actuating shaft is not further rotated. This is particularly advantageous if the drive is a drive motor, which travels after reaching the corresponding switch position, without this being allowed to influence the switch position.

A further preferred embodiment of the three-position switch actuator is characterized in that an engagement prevention device, in particular a rocker arm, to avoid simultaneous engagement of the double pawls of both drive shafts with simultaneous actuation of both drive shafts is present. This ensures that, in particular when the disconnector is switched off, simultaneous engagement of the pawls with simultaneous actuation of both drive shafts is precluded.

An embodiment of the invention provides that the present on the drive shafts double latches in each case engage in different arranged on the actuating shaft ratchet wheels. Advantageously, this may be the case when four ratchet wheels are present on the actuating shaft, wherein two ratchet wheels are each offset by half a pitch in relation to each other and for engaging each of a drive shaft existing two double pawls serve.

In another embodiment of the three-position switch actuating device, the double pawls present on the drive shafts only engage in a ratchet wheel present on the actuating shaft. In such an embodiment of the invention is intended to the case in which only a ratchet wheel is present and sitting on the two drive shafts two double pawls, which are asymmetrical and each have a long and a short latch arm.

In a further embodiment of the invention, it is provided that the ratchet wheel toothing of a ratchet wheel has different ratchet toothed sections with at least partially different rows of teeth for engaging the respective pawl tips of the corresponding double pawls. Such Klinkenradverzahnungsabschnitte are particularly needed if a plurality of independently operable double pawls on a ratchet come into engagement.

A variant of the invention provides that the teeth of the rows of teeth, which are acted upon from one side only by a pawl tip, have a beveled rear edge. On such a rear edge, the Run the latch tip well without operating the actuation shaft or damaging the latch tip.

Another preferred embodiment of the invention is characterized in that the teeth of the rows of teeth, which are acted upon by pawl tips from both sides, on both sides have a, in particular to the Klinkenradumfang approximately at right angles formed, attack surface for acting on the pawl tips. Such a configuration of the corresponding teeth has proven to be particularly stable and therefore advantageous.

In a further embodiment of the invention, the ratchet wheel or the ratchet wheels only partially a ratchet gear teeth. In the areas in which no interference of pawl tips is provided on tooth flanks, so a Klinkenradverzahnung can fail on the ratchet wheel. It is also conceivable that no full ratchet wheels, but only Klinkenradsegmente be used.

Advantageously, the force application of the pawl tip on the ratchet wheel or the ratchet wheels is largely tangential. This ensures the largest possible lever arm. An easy to Ratchet wheel center directed force component ensures the secure engagement of the pawl tips on the corresponding ratchet wheel.

In a variant of the invention, the spread angle between two pawl arms of a double pawl is so great that it is ensured that during the engagement of the pawl tip of a pawl arm between the other pawl and the ratchet wheel sufficient free play is present. For a certain reliability of the actuator is achieved.

In a further embodiment of the invention, an influence of the movement sequence of the double pawl due to the net mass of the double pawl is negligible by the friction clutch. Thus, the otherwise labile behavior of the double pawls on the eccentrics is stabilized so far that an uncontrolled influence is excluded by the intrinsic masses of the double pawls.

A further embodiment of the invention provides that the guide elements on the double pawls or molded with corresponding rigid abutments corresponding cam tracks are. The friction clutches, because of their small friction torque, the double pawls only in the correct sequence for engagement on the bring desired side and to leave the unwanted side, if the pivoting movements of the double pawls are not hindered by external moments on the ratchet wheel. If one reverses, for example, in the course of actuation of a drive shaft, the direction of rotation of the drive shaft, the last engaging or pushing pawl half of a double paw could still be engaged in a high friction between pawl tip and engaging tooth engagement, while the opposite half working with the Double pawl already, in the opposite direction, comes into engagement. It would thus occur an absolute blocking situation of the actuator. Therefore, it must be ensured that in particular a forced lifting of a possibly jammed half of the pawl is brought about. This compulsory lifting takes place with one half of the double pawl in a suitably connected curved track, which is supported on an abutment so that it, assigned to the respective eccentric, to an engagement prevention or in the case of an already engaged double pawl for compulsory lifting the same comes.

In a further embodiment of the invention, the actuating shaft is held by means of locking elements in the switching positions. This avoids that Switch positions due to, for example, magnetic current forces or vibrations of the switching device can be changed.

Another, particularly advantageous embodiment of the invention provides that a drive shaft drives the associated eccentric shaft via an existing between the drive shaft and the eccentric gear, in particular a spur gear. As a result, in particular a change in direction of the eccentric shaft relative to the drive shaft is achieved, which can be ensured that when turning the drive shaft a corresponding switch closed, and can be opened by turning to the left.

Further advantageous embodiments and details of the invention will be apparent from the following description in which the invention with reference to the embodiments illustrated in the drawings is described and explained in more detail.

Fig. 1

zwei Einstrichschemen für einen elektrischen Abzweig mit einem Trennschalter und einem Dreistellungsschalter,

Fig. 2

eine Betätigungseinrichtung bei einem Trennschalter in Vorderansicht,

Fig. 3

einen Längsschnitt durch die Betätigungseinrichtung nach Fig. 2,

Fig. 4

den Bewegungsablauf einer Doppelklinke an einem Klinkenrad,

Fig. 5

eine Betätigungseinrichtung für einen Dreistellungsschalter mit zwei Antriebswellen und je zwei Doppelklinken auf jeder Antriebswelle,

Fig. 6

die Draufsicht auf eine andere Betätigungseinrichtung für einen Dreistellungsschalter,

Fig. 7 - 10

verschiedene Schnitte durch die Betätigungseinrichtungen nach Fig. 6,

Fig. 11

ein Klinkenrad mit Klinkenradverzahnung der Betätigungseinrichtung nach Fig. 6 und

Fig. 12

die Betätigungseinrichtung nach Fig. 6 in schematischer Darstellung.

Show it:

Fig. 1

two one-line schemes for an electrical feeder with a circuit breaker and a three-position switch,

Fig. 2

an actuator at a circuit breaker in front view,

Fig. 3

a longitudinal section through the actuator after Fig. 2 .

Fig. 4

the movement of a double pawl on a ratchet wheel,

Fig. 5

an actuating device for a three-position switch with two drive shafts and two double latches on each drive shaft,

Fig. 6

the top view of another actuator for a three-position switch,

Fig. 7 - 10

different cuts by the controls after Fig. 6 .

Fig. 11

a ratchet with Klinkenradverzahnung the actuator after Fig. 6 and

Fig. 12

the actuator after Fig. 6 in a schematic representation.

In the Fig. 1 For example, dashed lines A and B show two examples of typical electrical functions of branching off one particular medium-voltage switchgear, each with a different switch configuration.

The one-stroke scheme A shows a branch with a series connection of a circuit breaker 1 and a circuit breaker 2. In addition, a grounding switch 3 is provided which grounds the branch when the circuit breaker 2 and disconnector 1. However, such a switching configuration presupposes that there is a lock which ensures that the circuit breaker 1 only in the de-energized state, ie. H. can be operated with open circuit breaker 2. In addition, a further locking is necessary, which ensures that the earthing switch 3 can only be closed when the disconnector 1 is open. This prevents inadvertent grounding of the pantograph when the circuit breaker 1 is closed. The circuit breaker has an actuating device for manual and / or motor drive.

The one-stroke diagram B shows a branch with a series connection of a three-position switch 4 and a circuit breaker 2. The three-position switch 4 has three switch positions, namely disconnector ON, disconnector OFF and EARTH. If the circuit-breaker 2 is switched on in the position of the switch EARTH, the feeder will be earthed. Unlike the one-stroke scheme A, the three-position switch 4 does not require a lock between the disconnect and ground functions. However, a lock must nevertheless be present between the circuit breaker 2 and the disconnector functions of the three-position switch 4, which ensures that the disconnector function of the three-position switch 4 can only be actuated in the de-energized state, ie when the circuit breaker 2 is open. In addition, according to the one-stroke scheme B, it must be ensured that the three-position switch 4 can be moved in the direction of EARTH only when the power switch 2 is switched off. The three-position switch has an actuating device 5 for manual and / or motor drive.

The invention particularly relates to actuators for those in the Fig. 1 Switching devices shown, namely circuit breaker 1 and three-position switch 4. The actuators according to the invention have in common that they have reversibly driven gear, namely acting in two drive directions ratchet gear. The switching elements of disconnectors or Three-position switches are positively and directly driven and generate their actuators neither leading nor retreating moments.

In the Fig. 2 is an actuator 6 according to the invention, namely shown for a circuit breaker in the front view. The Fig. 3 shows the same actuator 6 in longitudinal section along the line AA. The actuating device 6 in this case has an actuating shaft 7 driving a current path, on whose free end a lever 8 for the transmission of motion is arranged on a switching device. The actuating shaft 7 is coupled via a pawl transmission with a drive shaft 9. The drive shaft 9 is, as in Fig. 3 can be clearly seen, driven by a manually operable crank 11. According to the invention, however, it can also be provided that in addition to the hand crank 11, a drive motor is present. The drive shaft 9 is formed as an eccentric shaft with two eccentrics 12 and 13. The two eccentrics 12 and 13 are offset by an angle of 1800 arranged to each other and are respectively rotatably connected by means of a pin 16 and 17 to the drive shaft 9.

On the two eccentrics 12 and 13 is one each Double pawl 18 and 19 conditionally arranged by means of a frictional friction clutch rotation. The friction clutch is achieved by means of a defined clamping, namely a frictional engagement between an existing on the eccentrics 12 and 13 and flange 21 and 22 between the double pawls 18 and 19 and lock washers 23 and 24 spring washers, such as corrugated springs.

The double pawls 18 and 19 have two pawl arms 26, 27, 28 and 29 spread apart by a spread angle, the pawl arms 26, 27, 28 and 29 each having a pawl tip 31 on the side facing away from the drive shaft 9.

As in Fig. 2 and Fig. 3 shown, two ratchet wheels 32 and 33 are arranged rotationally fixed on the actuating shaft 7. For rotationally fixed attachment of the two ratchet wheels 32 and 33, a rotatably connected to the actuating shaft 7 intermediate member 34 is present, on which the two ratchet wheels 32 and 33 are secured by means of fastening screws 36.

A friction clutch between the double pawls 18 and 19 and the eccentrics 12 and 13 is therefore necessary to ensure that z. B. in a clockwise rotation of Drive shaft 9 actually the right pawl arms 27 and 29 come to the ratchet wheels 32 and 33 for engagement and thus a right-handed drive torque is generated. For this purpose, a frictional connection must be generated via the friction clutches. This frictional engagement must stabilize the otherwise labile behavior of the double pawls 18 and 19 on the eccentrics 12 and 13 to such an extent that an uncontrolled influence by the intrinsic masses of the double pawls 18 and 19 is excluded.

The ratchet wheels 32 and 33 have along their circumference a ratchet gear teeth 37, in which the pawl tips 31 of the double pawls 18 and 19 can engage.

The ratchet gear teeth 37 of in Fig. 2 clearly recognizable ratchet wheel 32 has three different Klinkenradverzahnungsabschnitte 41, 42 and 43. The row of teeth associated with the ratchet gear portion 41 is engaged with the pawl tip 31 of the pawl arm 26 from only one side, and therefore has a bevelled trailing edge 44.

The teeth of the row of teeth of Klinkenradverzahnungsabschnitts 42 are acted upon from both sides by the pawl tips 31 of the two pawl arms 26 and 27 of the double pawl 18 and therefore have a Klinkenradumfang approximately at right angles trained attack surface 46 for bidirectional loading of the latch tips 31.

The teeth of the row of teeth of the Klinkenradverzahnungsabschnitts 43 are acted upon only by the pawl tip 31 of the pawl arm 27 of the double pawl 18, and therefore have on its rear side a beveled edge 44.

The ratchet wheel 32 has, as in Fig. 2 clearly recognizable, an untoothed ratchet wheel 47 on. An engagement of a pawl tip 31 in this untoothed portion 47 is not possible, ie in this area a rotation of the actuating shaft 7 is not possible.

The ratchet wheel 33, which is arranged parallel to the ratchet wheel 32 and on which the pawl tips 31 of the double pawl 19 engage, corresponds in terms of the geometry of the ratchet teeth 37 to the ratchet wheel 32 and is offset by half a tooth pitch relative to the ratchet wheel 32 on the actuating shaft 7. This has the advantage that the tooth pitch of the two ratchet wheels 32 and 33 can be configured slightly smaller than four times the eccentricity of the eccentric center of the eccentric 12 and 13 to the central axis of the drive shaft 9. By such a configuration The teeth are much more stable due to the larger tooth pitch, which is particularly crucial for double-sided acted upon teeth of Klinkenradverzahnungsabschnitts 42. Here are the double pawls 18 and 19, as in Fig. 2 can be clearly seen, designed symmetrically.

The double pawl movement of the two double pawls 18 and 19 with rotating drive shaft 9 is guided according to the invention by guide elements, namely of the double pawls 18 and 19 integrally formed cam tracks 51 and 52. These cam tracks 51, 52 correspond to rigid abutments, namely with the two guide screws 53rd and 54. Due to the support of the cam tracks 51 and 52 on the guide screws 53 and 54 takes place with rotating drive shaft 9 always a forced levy of the respective pawl tip 31 from the ratchet teeth 37. In addition, the spread angle between the respective pawl arms 26 and 27 and 28 and 29 of a double pawl 18 and 19 so large that it is ensured that during the engagement of the pawl tip 31 of a pawl arm 26 or 28 between the other pawl arm 27 or 29 and the ratchet wheel 32 or 33 sufficient free play is present and thereby the rotational movement of Ratchet wheel 32 or 33 not disturbed or impaired.

The Fig. 2 shows the two pawl arms 18 and 19 in a neutral center position, in which none of the pawl tips 31 is in engagement with the ratchet wheel 32 or 33. However, such a neutral center position does not occur with rotating drive shaft 9, since due to the friction clutch of the double pawls 18 and 19 with the eccentrics 12 and 13 always a force component is present, which causes each a pawl tip 31 is in engagement with the ratchet 37 , As a result, a return of the ratchet wheel 32 or 33 against the direction of rotation of the actuating shaft 7 is excluded in particular. The in the Fig. 2 shown neutral center position of the pawl arms 18 and 19 is, however, go through when changing direction of rotation of the drive shaft 9.

The actuator 6, the in Fig. 2 and Fig. 3 is shown is also surrounded by two housing walls 56 and 57, which are mounted by means of four mounting screws 61 with associated spacers 62.

Due to the geometric configuration of the two double pawls 18 and 19 and the Klinkenradverzahnungen 37 of the two ratchet wheels 32 and 33, the actuating shaft 7 can be rotated back by a output angle of slightly more than 180 ° in one direction and again.

How out Fig. 2 can be clearly seen, the toothed portion of the ratchet wheel 32 extends over slightly more than 270 ° to allow half a revolution of the actuating shaft 7. In this case, the teeth of the ratchet wheels 32 and 33 deliberately not led beyond the maximum required area to cause about the lack of further intervention at the same time a Abtriebswinkelbegrenzung, which is just then very advantageous if the drive shaft 9 is driven by a motor and a motor after-run, eg ., May cause no further rotation of the actuating shaft 7 due to the engine flywheel.

The drive shaft 9 and the actuating shaft 7 is secured by means of lock washers 63 on the housing 56 and 57.

In the Fig. 4 is the double pawl 18 with the two pawl arms 26 and 27 shown in engagement with the ratchet wheel 32. In this case, four different positions of the double pawl 18 are shown at a direction indicated by the arrow 66 clockwise rotation of the eccentrically mounted double pawl 18. The eccentric center moves in a circular path over the four points A, B, C, D. Upon rotation of the drive shaft 9, the eccentric center moves from position A to B. This has a movement of the pawl tip 31 of the pawl arm 27 of the position A to the position B result, ie the pawl arm 27 is lifted out of its engaged position, which is effected in particular due to the expiring on the guide screw 53 cam track 51. In position B, the pawl arm 27 is in the maximum retracted position. Upon further rotation of the drive shaft 9, due to which the eccentric center is rotated from position B to position C, the pawl tip 31 of the pawl arm 27 reaches the engaged position C on the ratchet wheel 32. If the drive shaft 9 is further rotated, so that the eccentric center of C after D is moved, this leads to a pushing movement of the pawl tip 31 from the position C to the position D, which is the maximum thrust position. Due to this pushing movement, the ratchet wheel 32 is rotated one step to the right. If the drive shaft 9 is rotated further to the right, the latch tip 31 is moved out of the position D into the position A due to the interplay of the cam track 51 with the guide screw 53. As the drive shaft 9 continues to rotate, the cycle described is repeated.

According to the invention, it is provided that, as in Fig. 2 and 3 described, another double pawl is present, which is arranged offset by 180 ° on the drive shaft 9.

This ensures that there is always a pawl tip of the two double pawls upon rotation of the drive shaft 9 in one direction in engagement with the Klinkenradverzahnung or the toothing of another ratchet wheel, whereby a return of the ratchet wheels against the direction of rotation of the actuating shaft 7 is excluded.

In the Fig. 5 is shown another embodiment of an actuator 71 according to the invention, namely for a three-position switch, which connects a branch 72 with a busbar 73 or with an earthing contact 74. It must be provided that each of the two switching operations can be performed by hand from a separate, distinctive drive device. In addition, at the same time an inadmissible switching through, for. B. from the position disconnector ON via the center position disconnector OFF in the position of grounding to be prevented.

The actuator 71 according to Fig. 5 has four ratchet wheels 76, 77, 78 and 79, which are arranged parallel to each other on an actuating shaft 81 rotatably. One or more (eg, three) switching elements 82 are connected to the actuating shaft 81, which (in the position shown) separates the branch 72 from the earth contact 74 as well as the busbar 73.

Simplifying is in FIG. 5 chosen a representation as if the switching element 82 is mounted directly on the actuating shaft 81. As a result, upon rotation of the actuating shaft 81 by approximately 90 ° to the right, the disconnecting switch of the three-position switch 71 is closed and the branch 72 is connected to the busbar 73. Upon rotation of the actuating shaft 81 to the left by approximately 90 °, the branch 72 is connected to the earth contact 74. The total operating angle of the actuating shaft 81 is in this embodiment at a little more than 180 ° and is generated by the fact that two actuators according to the Fig. 2 and 3 equipped with a modified toothed area and set to the common operating shaft 81. Their initial and final positions are each suitably coordinated with each other, such as in Fig. 5 is shown.

This three-position switch actuator 71 after Fig. 5 has two drive shafts 83 and 84 which are independently drivable by means of a hand crank or by a drive motor. On the drive shaft 83, two double pawls 86 and 87 are arranged via two eccentrics, via which the two ratchet wheels 76 and 77 which are arranged offset one half pitch to each other on the actuating shaft 81, are driven. Due to the corresponding Tooth pitch of the ratchet wheels 76 and 77, the operating shaft 81 can be rotated by rotation of the drive shaft 83 only by an angle of slightly more than 90 °, namely in the selected representation of the shown, neutral center position of the switching element 82 to the connection of the switching element 82 with the Earth contact 74.

Corresponding to the drive shaft 83, two double pawls 88 and 89 are each disposed on the eccentric on the drive shaft 84. The two left ratchet wheels 78 and 79 are, according to the ratchet wheels 76 and 77, also offset by half a pitch on the actuating shaft 81. The toothing of the two ratchet wheels 78 and 79 is such that via a rotation of the drive shaft 84, the actuating shaft 81 by an angle of only slightly more than 90 ° from the neutral center position of the switching element 82 for closing the circuit breaker, d. H. for connection of the switching elements 82 with the busbar 73, can be rotated.

The ratchet wheels 76, 77, 78 and 79 with the corresponding teeth, in which the double pawls 86, 87, 88 and 89 engage, are arranged so that, except for the center position of the actuating shaft 81, the actuating shaft 81 can be driven only by one of the two drive shafts 83 or 84 in each case. The respective non-active drive shaft 83 or 84 then engages with their double pawls 86, 87 or 88, 89 either on edentulous portions of the corresponding ratchet wheel 76, 77, 78 or 79 or on flattened back sides, whereby no rotation of the actuating shaft 81 by the non-active Drive shaft 83 or 84 can be done.

Due to the teeth of the ratchet wheels after Fig. 5 It is ensured that the double pawls 76, 77, 78 and 79 hit upon reaching the desired switch positions on edentulous portions of the corresponding ratchet wheel 76, 77, 78 or 79 and thus no further rotational movement of the actuating shaft 81 takes place, especially if the corresponding drive shaft 83 or 84 is further rotated by, for example, the tail of a drive motor.

According to the Figures 2 and 3 have the double pawls 86 to 89 on their, the respective ratchet wheels 76 to 79 side facing cam tracks 91 and the cam tracks 91 corresponding guide screws 92, which lead the course of the double pawl movement with rotating drive shaft 83 or 84.

In the Fig. 6 to 10 Another embodiment of an actuator 96 for a three-position switch according to the invention is shown. The three-position switch actuator 96 has, as in Fig. 6 can be seen well, two drive shaft 98 and 99, each with a hand crank 101, being turned off by turning the drive shaft 98 of the earth or turned off by turning left and turned right turn the drive shaft 99 of the separator or turned off in left turn. In the Fig. 6 In addition, a position indicator 102 is shown on an actuating shaft 103 in the switch position disconnector OFF, earth OFF. By turning the drive shaft 98 clockwise, the actuating shaft 103 is rotated with the position indicator 102 to the switch position Erder ON. By clockwise rotation of the drive shaft 99, the switching element 102 is set to the switch position isolator ON. A connected to the actuating shaft 103 via the drive lever 105 linkage 110 leads to the actuated switching elements.

In the Fig. 7 is a section along the line YZ after Fig. 6 shown, wherein the position indicator 102 is rotated by 180 °. In this case, the actuating shaft 103 and the rotationally fixed to the actuating shaft 103 connected position indicator 102 can be clearly seen. On the actuating shaft 103 is also a ratchet wheel 104 via Fixing screws 106 rotatably arranged, wherein the ratchet 104 consists of two identical, on the actuating shaft 103 in alignment ratchet wheels 107 and 108 consists. It is obvious in the practical application, instead of the two Klinkenradecheiben 107 and 108 to use an integrally formed, solid ratchet wheel.

Out Fig. 7 It is also clear that the actuating shaft 103 between two housing walls 109 and 111, which are connected to each other by means of spacer screws 112, is rotatably mounted.

In the Fig. 8 is a section through the three-position shift actuator 96 after Fig. 6 shown along the line EF. Clearly visible are the two drive axles 98 and 99 with the rotatably mounted hand cranks 101. In this case, the drive shaft 98 is formed as an eccentric shaft on which two eccentrics 113 are offset by 180 ° to each other. On the eccentrics 113 is a double pawl 116 and 117 by means of a friction clutch conditionally rotatably arranged.

As in Fig. 8 is shown, at the end remote from the hand crank 101 of the drive shaft 99, a spur gear 118 is arranged, which is an eccentric 119th driving further spur gear 121 meshes. On the eccentric shaft 119, two eccentric 113 are arranged with arranged thereon double pawls 122 and 123 corresponding to the drive shaft 98. The existing between the drive shaft 99 and the eccentric shaft 119, consisting of the two spur gears 118 and 121 gear causes a default is met, which requires that a switch is closed by clockwise rotation of a drive shaft and opened by turning to the left.

In the Fig. 9 is a section of the three-part switch 96 of Fig. 7 shown along the line AB. In this case, the ratchet wheel 107 can be clearly seen with the associated ratchet gear. On the ratchet teeth of the ratchet wheel 104 and the two ratchet wheels 107 and 108 is in the description of the Fig. 11 received closer.

In the Fig. 9 are the two ratchet wheel 107 driving double pawls 117 and 123 clearly visible on the respective eccentrics 113. The eccentricity of the eccentric 113 is slightly more than the fourth part of a tooth pitch of the ratchet wheel 104. This ensures that in one revolution of the drive shaft 98 or 99, the ratchet wheel 104 is moved by a tooth pitch and the double pawls 117 and 123 can engage with certainty in the teeth of the ratchet wheel 104. The double pawls 117 and 123 have the peculiarity that they are designed asymmetrically and each have a long pawl arm 126 and a short latch arm 127. The latch arms of the double pawls 117 and 123 are advantageously designed so that the difference between the length of a long pawl arm 126 to a short latch arm 127 is half the pitch of the ratchet wheel 104.

How out Fig. 10 which shows a section through the Fig. 8 is shown along the line CD, the double pawls 122 and 116 are configured in accordance with the double pawls 123 and 117, wherein the double pawls 122, 123 and 116, 117 laterally mounted on the eccentric shaft 119 and the drive shaft 98 are mounted. This results, together with the extent of eccentrically arranged with slightly more than a quarter pitch eccentrics 113 and their angular position of 180 ° to each other in the maximum Spreitzstellung a maximum offset of the two associated latch tips of slightly more than a whole tooth pitch. Advantageously, a maximum offset of about 1.2 times a pitch and in the Nachholstellung a game with half the difference between tooth length and 4facher Exzenterhub, thus a secure engagement of the double pawls 122, 123 and 116, 117 Even under high load and thus any associated elastic deformations is guaranteed even after a certain wear. One revolution of the drive shaft 98 or 99 thereby gives the actuating shaft 103 a rotation which corresponds to the angle of a tooth pitch. Due to the use of long latch arms 126 and correspondingly short latch arms 127, an offset of the rows of teeth on the ratchet 104, as he according to the embodiments of Fig. 2 and 3 such as Fig. 5 was present, be avoided. Advantage of in the Fig. 6 to 10 illustrated embodiment of the invention is that only a ratchet 104 is used to implement a three-position switch actuator 96.

To guide the movement of the double pawls 122, 123 and 116, 117 with rotating drive shafts 98 or 99 are provided as guide elements on the double pawls 122, 123 and 116, 117 cam tracks 128, which run on guide screws 129. The guide screws 129 are arranged for reasons of space in the double pawls 116, 117 and 122, 123 existing windows 131.

Out FIGS. 9 and 10 It is clear that the ratchet wheel 104 and the two ratchet wheels 107 and 108 have a recess 132 along which the Actuating shaft 103 facing away from the border on rotation of the actuating shaft 103, a pin member 133 runs. The pin element 133 is pressed against the ratchet wheel 104 or the ratchet wheel disks 107 and 108 via a flat plate 135 by means of a spring 134. The recess 132 has in the switching positions locking bays 136, in which the pin member 133 engages upon reaching the switching position, whereby the actuating shaft 103 is held in the corresponding switching positions. In the in FIG. 10 shown position, the pin member 133 is engaged in a latching bay 136. This ensures that magnetic current forces, vibrations or other external forces can not cause a change in the switching position. Upon rotation of the ratchet wheel 104, the pin member 133 is lifted out of the latching bay 136 against the spring force of the spring 134, due to the geometric configuration of the recess 132.

In the Fig. 9 such as Fig. 10 a rocker arm 137 is clearly shown, which is provided to avoid simultaneous engagement of the double pawls 116, 117 and 122, 123 with simultaneous actuation of the two drive shafts 98 and 99. The rocker arm 137 is rotatably mounted about an axis 138. The function of rocker lever 137 is added in the description of the figures Fig. 12 explained.

• 10 im Linksdrehsinn beaufschlagbare Zahnflanken 151,
• 10 im Rechtsdrehsinn beaufschlagbare Zahnflanken 152,
• je 3 linke und drei rechte Zahnflanken sind überlagert, so dass Rechteckzähne 153 entstehen,
• das Abwälzbild enthält somit sechs linksseitige, sechs rechtsseitige und vier symmetrische und somit 16 Ausnehmungen,
• das Abwälzbild beider Klinkenradscheiben ist gleich, der jeweilige Beginn liegt in diesem Beispiel bei 156,8° versetzt, da die Zahnflanken mit einem Abstand von 9,8° angeordnet sind und 16 Zahnflanken je Klinkenradhälfte vorhanden sind.

In the Fig. 11 is the Klinkenradverzahnung the ratchet 104 of the FIGS. 9 and 10 for an example, which applies at a total operating angle of about 180 ° application. The ratchet wheel 104 has a total of 20 counterclockwise and 20 clockwise acting tooth flanks, which are alternately distributed in groups of ten tooth flanks over about 310 ° of Klinkenradumfanges and thereby in two areas, over a length of three right and three left Tooth flanks, overlay. Since the ratchet wheel 104 has two symmetrical halves, the consideration of a ratchet wheel half is sufficient. For such a ratchet wheel half:

• 10 acted upon in left direction tooth flanks 151,
• 10 in the right direction acted upon tooth flanks 152,
• each 3 left and three right tooth flanks are superimposed so that rectangular teeth 153 arise,
• the rolling image thus contains six left-sided, six right-sided and four symmetrical and thus 16 recesses,
• the rolling image of both ratchet wheel is the same, the respective beginning is offset in this example at 156.8 °, since the tooth flanks are arranged at a distance of 9.8 ° and 16 tooth flanks each Klinkenradhälfte are present.

This in Fig. 11 described ratchet wheel 104 leads to a translation in which with 10 revolutions of the respective drive shafts each slightly more than 90 ° output angle of the actuating shaft is generated. Finer or coarser pitches can be used to generate larger or smaller gear ratios with adjusted eccentric strokes.

In the Fig. 12 are the two identical, aligned parallel and ratchet wheel discs 107 and 108 of the ratchet 104 after the Fig. 7 shown on the actuating shaft 103. Also visible are the double pawls 122 and 116, which are provided for engagement with the ratchet wheel 108, and the double pawls 123 and 117, which cooperate with the ratchet wheel 107. The double pawl 122 and 123 is disposed on the eccentric shaft 119 via a respective eccentric 113, which are arranged offset 180 ° to each other. Accordingly, the two double pawls 116 and 117 are arranged on the drive shaft 98.

In the Fig. 12 is the pawl tip of the short ratchet arm of the double pawl 123 engaged with a tooth edge 154 of the ratchet wheel 107. Clearly visible is a rocker lever 137, along the axis of rotation 138 between the respective short latch arms 127 of the two double pawls 123 and 116 is arranged. In the neutral center position of the ratchet wheel discs 107 and 108 may be in the in Fig. 12 shown embodiment, only the short pawl arms 127 of the two double pawls 123 and 116 engage tooth flanks on the ratchet wheel 107 and 108, respectively. The long pawl arms 126 of the two double pawls 117 and 122 can not engage in the ratchet wheel teeth 107 and 108 due to lack of tooth flanks in their thrust positions and can thus cause no rotation of the two ratchet wheel disks 107 and 108, respectively. For this reason, a rocker arm 137 is sufficient to avoid the simultaneous engagement of the double pawls 116 and 126 between the short pawl arms 127 of the two double pawls 116 and 123.

On the short latch arms 126, pins 155 are provided which cooperate with the rocker arm 137 in such a way that only one latch arm can come into engagement with the ratchet wheel disk 107 or 108 on account of the respective rocker arm position. The rocker lever 137 allows for an either-or-engagement. This intervention prevention is required only in the exact center position of the actuator 96. Basically, in this middle position, alternatively, the disconnector or the earthing switch must be able to be operated. Once the ratchet 104, the exact center position Already the teeth arrangement on the ratchet wheel discs 107 and 108 ensures that only the double pawls of either the drive shaft 98 or the eccentric shaft 119 on the ratchet wheel discs 107 and 108 can come into engagement.

Out Fig. 12 It is also clear that the drive shaft 98 and the eccentric shaft 119 form an angle of at least 90 ° plus a pitch, that is slightly more than 100 °. Such an arrangement allows the gearing for a three-position switch actuator to be housed on a ratchet wheel disk 107 or 108.

All in the description, the following claims and the drawings illustrated features may be essential to the invention both individually and in any combination.

Claims (27)

1. Actuating arrangement (6, 71, 96) for actuating conducting paths, having an actuating shaft (7, 81, 103) which actuates a current path, having at least one drive shaft (9, 83, 84, 98, 99) which is driven by a drive and is coupled to the actuating shaft (7, 81, 103) by means of a transmission mechanism, in which case the drive may be a manually operable hand crank (11, 101) which is in driving connection with the drive shaft (9, 83, 84, 98, 99) and/or may be a drive motor, the transmission mechanism being a ratchet-and-pawl transmission mechanism which has at least one ratchet wheel (32, 33, 76-79, 104, 107, 108) having a set of ratchet-wheel teeth (37) and which has at least two double pawls (18, 19, 86-89, 116, 117, 122, 123), the at least one ratchet wheel (32, 33, 76-79, 104, 107, 108) being arranged on the actuating shaft (7, 81, 103) to be solid in rotation therewith, the drive shaft (9, 83, 84, 98, 99) taking the form of an eccentric-equipped shaft having at least two eccentrics (12, 13, 113), the double pawls (18, 19, 86-89, 116, 117, 122, 123) having two pawl arms (26-29, 126, 127) which are splayed at an angle of splay, the pawl arms (26, 27, 28, 29) each having, at the end remote from the drive shaft (9, 83, 84, 98, 99), a pawl-tip (31) which is designed to be able to engage in the sets of teeth (37) on the ratchet wheel (32, 33, 104, 107, 108), one pawl-tip (31) at a time being in engagement with the set of ratchet-wheel teeth (37) when the drive shaft rotates (9, 83, 84, 98, 99), and guiding members being present which guide the movement of the double pawls when the drive shaft (9, 83, 84, 98, 99) rotates, characterised in that, by means of friction coupling, respective double pawls (18, 19, 86-89, 116, 117, 122, 123) are arranged on the at least two eccentrics (12, 13, 113), to be conditionally solid in rotation therewith by means of a friction coupling arrangement.
2. Actuating arrangement (6, 71, 96) according to claim 1, characterised in that the set of ratchet-wheel teeth (37) has two lines of teeth (41, 43) oriented in opposite directions to receive the respective pawl-tips (31) which engage in the set of ratchet-wheel teeth (37), in which case the two lines of teeth (41, 43) may even overlap (42).
3. Actuating arrangement (6, 71, 96) according to claim 1 or 2, characterised in that the two eccentrics (12, 13, 113) on the drive shaft (9, 83, 84, 98, 99) are arranged to be offset relative to one another, preferably at an angle of 180°.
4. Actuating arrangement (6, 71) according to one of the foregoing claims, characterised in that the double pawls (18, 19, 86-89) are of a symmetrical configuration and in that the pitch of the set of ratchet-wheel teeth (37) is slightly less than twice the eccentricity of the centre of the eccentrics from the centre axis of the drive shaft (9, 83, 84).
5. Actuating arrangement (96) according to one of claims 1 to 3, characterised in that the double pawls (116, 117, 122, 123) are of an asymmetrical configuration such that the pitch of the teeth of the ratchet wheel (104) is slightly less than four times the eccentricity (98, 99) of the centre of the eccentrics from the centre axis of the drive shaft.
6. Actuating arrangement (6, 71) according to one of the foregoing claims, characterised in that present on the actuating shaft (7, 81) are at least two ratchet wheels (32, 33, 76-79) which are arranged parallel to one another, one double pawl (18, 19, 86-89) being provided on the at least one drive shaft (9, 93, 84) to engage in each ratchet wheel (32, 33, 76-79).
7. Actuating arrangement (6, 71) according to claim 6, characterised in that the two double pawls (18, 19, 86-89) are of a symmetrical configuration, in that the lines of teeth forming the sets of teeth (37) of the two ratchet wheels (32, 33, 76-79) are arranged to be offset by half the tooth pitch, and in that the pitch of the teeth of the two ratchet wheels (32, 33, 76-79) is slightly less than four times the eccentricity of the centre of the eccentrics from the centre axis of the drive shaft (9, 83, 84).
8. Actuating arrangement (71, 96) according to one of the foregoing claims, characterised in that the actuating arrangement (71, 96) takes the form of an actuating arrangement for three-position switches and has a switching position which closes the conducting path, a switching position which breaks the conducting path and a switching position which connects the conducting path to an earthing electrode.
9. Actuating arrangement (71, 96) according to claim 8, characterised in that the conducting path is broken when the actuating shaft (81, 103) is in the neutral position, and in that the conducting path is closed when the actuating shaft (81, 103) is at an angle of rotation of approximately 90° in one direction of rotation and is earthed when the actuating shaft (81, 103) is at an angle of rotation of approximately 90° in the other direction.
10. Actuating arrangement (71, 96) according to claim 8 or 9, characterised in that at least two drive shafts (83, 84, 98, 99) able to be driven independently of one another and having eccentrics (113) and double pawls (86-89, 116, 117, 122, 123) arranged thereon are present, by means of which drive shafts (83, 84, 98, 99) the actuating shaft (81, 103) can be actuated to the different switching positions.
11. Actuating arrangement according (71, 96) to one of claims 8 to 10, characterised in that the ratchet wheels (76-79) or ratchet wheel (104) each have only one portion having a line of teeth to engage the double pawls of the drive shaft (83, 84, 98, 99) which is actuated in the given case, thus enabling rotation of that drive shaft (83, 84, 98, 99) in whose region of engagement the ratchet wheels (76-79) or ratchet wheel (104) are or is not to be freely rotatable without actuating the actuating shaft (81, 103).
12. Actuating arrangement (71, 96) according to one of claims 8 to 11, characterised in that, by the rotation of one drive shaft (83, 84, 98, 99), the actuating shaft (81, 103) can be turned or turned back by only approximately 90° at a time.
13. Actuating arrangement (96) according to one of claims 8 to 12, characterised in that a device for preventing engagement, and in particular a rocking lever (137), is present to prevent the double pawls (116, 117, 122, 123) on both drive shafts (98, 99) from engaging simultaneously if both drive shafts (98, 99) are actuated simultaneously.
14. Actuating arrangement (71) according to one of claims 8 to 13, characterised in that the double pawls (86-89) present on the drive shafts (83, 84) engage in different respective ratchet wheels (76-79) arranged on the actuating shaft (81).
15. Actuating arrangement (96) according to one of claims 8 to 14, characterised in that the double pawls (116, 117,122, 123) present on the drive shafts (98, 99) engage in only one ratchet wheel (104) arranged on the actuating shaft (103).
16. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the set of teeth (37) of a ratchet wheel (32, 33, 76-79, 104) have, to engage the respective tips (31) of the corresponding double pawls (18, 19, 86-89, 116, 117, 122, 123) different portions (41, 42, 43) in which there are lines of teeth of which at least some differ from one another.
17. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the teeth (153) forming those lines of teeth to only one side of which pawl-tips (31) are applied have an inclined rear face.
18. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the teeth (153) forming those lines of teeth to both sides of which pawl-tips (31) are applied have a face for engagement for the pawl-tips (31) to be applied to on both sides, and in particular a face for engagement of this kind which is formed to be approximately at right angles to the circumference of the ratchet wheel.
19. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that only a portion or portions of the ratchet wheel (104) or ratchet wheels (32, 33, 76-79) has or have a set of teeth (37).
20. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the application of force to the ratchet wheel (32, 33, 76-79, 104) by the pawl-tips (31) takes place largely tangentially.
21. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the angle of splay between two arms (26-29, 126, 127) of a double pawl (18, 19, 86-89, 116, 117, 122, 123) is sufficiently large to ensure that, during the engagement of the tip (31) of one arm of a pawl, there is adequate clearance between the other arm of the pawl and the ratchet wheel (32, 33, 76-79, 104).
22. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that, because of the friction coupling, any effect caused by the course of movement of the double pawl, due in particular to the mass of the double pawl (18, 19, 86-89, 116, 117, 122, 123), can be ignored.
23. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the guiding members are cam tracks (51, 52, 128) which are formed on or in the double pawls (18, 19, 86-89, 116, 117, 122, 123) and which correspond to appropriate rigid mating supports (53, 54, 129).
24. Actuating arrangement (6, 71, 96) according to claim 23, characterised in that, because of the support which the cam tracks (51, 52, 128) have on the mating supports (53, 54, 129), a forced lifting of the respective pawl-tips (31) clear of the set of ratchet-wheel teeth (37) always takes place, and if required the lifting clear of the given mating pawl is controlled by means of the rocking lever according to claim 13.
25. Actuating arrangement (96) according to one of the foregoing claims, characterised in that the actuating shaft (103) is held in the switching positions by means of latching members (133, 136).
26. Actuating arrangement (6, 71, 96) according to one of the foregoing claims, characterised in that the switching position is closed by clockwise rotation of the given actuating shaft (9, 83, 84, 98, 99) and is opened by anticlockwise rotation.
27. Actuating arrangement (6, 71, 96) according to the foregoing claim, characterised in that one drive shaft (99) drives the associated eccentric-equipped shaft (119) via gearing, and in particular spur gearing (118, 121), which is present between the eccentric-equipped shaft (119) and the drive shaft (99).

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