EP0586733B1 - Snap action driving arrangement for circuit breakers - Google Patents

Abstract

The snap-action drive for switching the switch (10) on and off quickly has an input shaft (12) which can rotate backwards and forwards between the first limit position (18) and the second limit position (18') and has a clamping lever (16). The drive lever (22) is seated in a rotationally fixed manner on the output shaft (14), which is parallel to the input shaft (12). The drive lever (22) can rotate under the force of the energy storage spring arrangement (26) from the switched-off position (24) into the switched-on position (24') and back. The energy storage spring arrangement (26) has a helical spring (28) which acts as a prestressed compression spring and whose spring ends (36, 36') are each supported on a lug (32, 34) which, for their part, interact via driver stops (52, 54, 56, 58) with the clamping lever (16) and the drive lever (22). An interlock device supports the output shaft (14) in its switched-off and switched-on positions (24, 24') against the force of the helical spring (28), which can be stressed during rotation of the input shaft (12), until the input shaft (12) has reached the corresponding unlatching position. <IMAGE>

Description

The present invention relates to a jump drive for quickly switching electrical switches on and off according to the preamble of claim 1.

A jump drive of this type is known from US-A-4,253,487. This has an input shaft that can be rotated by hand between two end positions over a crank with a double-arm tensioning lever. An output shaft with a double-armed drive lever, which can be rotated back and forth between an off and an on position, runs parallel to the input shaft. Between the arms of the input shaft and output shaft, a compression spring of a spring-loaded arrangement is arranged, the compression springs canceling each other's prestress when the input and output shafts are parallel to one another. The output shaft is held in the switch-off and switch-on position by a switch-on or switch-off pawl acting on the drive lever against the force of the compression spring that can be tensioned when the input shaft is rotated. Shortly before the input shaft reaches the corresponding end position, the clamping lever runs onto the relevant pawl to release the drive lever and thus the output shaft. After the switching operation has ended, the drive lever again runs parallel to the tensioning lever. To perform an opposite switching operation, the input shaft is rotated in the opposite direction, whereby the other compression spring is now tensioned to actuate the output shaft.

A disadvantage of this spring drive is that it requires its own compression spring for switching on and switching off. Furthermore, the switch-off and switch-on positions of the output shaft cannot be reliably achieved by the force of the pressure springs, since the effect of the two pressure springs is canceled out in these positions.

Another jump drive is disclosed in DE-C-32 17 255. The input shaft is connected to a parallel intermediate shaft via a gear pair. This carries a one-armed clamping lever and the parallel output shaft also has a drive lever. The tension lever and the drive lever are firmly connected to the spring ends of a coil spring. A locking device prevents the input shaft from being able to be turned into its end positions unless the output shaft is also in the switch-on or switch-off position, the locking device being designed such that the output shaft moves the last few degrees into the switch-on and switch-off position from the input shaft is inevitably rotated. This ensures that the switch-on and switch-off positions are reached when the coil spring is relaxed in these positions. This spring drive is disadvantageous in that it requires an intermediate shaft, since the input and output shafts must have opposite directions of rotation.

Furthermore, a jump drive, in which the input shaft and the output shaft are arranged coaxially to one another, is known from DE-AS 1 236 632. The spring-loaded arrangement has two coaxial bends Coil springs, with only one spring acting in the switch-off direction, but both in the switch-on direction, so that different drive energies are available depending on the switch direction. If the output shaft does not move under the action of the spring-loaded arrangement after the locking position of the input shaft has been exceeded, a forced coupling is produced between these shafts. Another forced clutch ensures when switching on that the output shaft is brought fully into the on position. This spring drive has a considerable depth in the direction of the waves.

It is an object of the present invention to further develop the known spring drive in such a way that the on and off position can be reached safely with a single coil spring while maintaining the small overall depth.

This object is achieved by a generic jump drive, which has the features of claim 1. According to the invention, the coil spring interacts with each of its spring ends via driver elements with the tensioning lever and the drive lever. The helical spring is thus clamped both between the driver elements interacting with the tensioning lever and between the driver elements interacting with the drive lever. Since the coil spring is pretensioned according to the invention, the input and output shaft are coupled to one another at least under a force which corresponds to the pretension of the coil spring, regardless of their mutual position. So long the movement of the output shaft counteracts a force that is less than the biasing force of the coil spring, the two shafts are firmly coupled. In other words, the output shaft is in any case pushed into the switch-on or switch-off position at least with the biasing force of the coil spring. The coil spring can be subjected to pressure or tension. However, it acts when switched on and when switched off in the same direction, namely always as a compression spring or always as a tension spring under pre-tension.

Further preferred embodiments of the jump drive according to the invention are specified in the dependent claims.

Fig. 1

in Ansicht einen Teil eines Sprungantriebs mit einer Federspeicheranordnung in Ausschaltstellung, teilweise geschnitten entlang der Linie I-I der Fig. 2;

Fig. 2

der in der Fig. 1 gezeigte Teil des Sprungantriebs in einem Schnitt entlang der Linie II-II der Fig. 1;

Fig. 3

in gleicher Darstellung wie Fig. 2 den Teil des Sprungantriebs in Ausschaltstellung bei gespannter Federspeicheranordnung vor Freigabe der Abgangswelle zum Einschalten;

Fig. 4

in Ansicht den in der Fig. 1 gezeigten Teil des Sprungantriebs in Einschaltstellung;

Fig. 5

den in der Fig. 4 gezeigten Teil des Sprungantriebs in einem Schnitt entlang der Linie V-V;

Fig. 6

in gleicher Darstellung wie Fig. 5 den in der Fig. 4 gezeigten Teil des Sprungantriebs in Einschaltstellung, aber mit für das Ausschalten gespannter Federspeicheranordnung kurz vor Freigabe der Abgangswelle zum Ausschalten;

Fig. 7

in gleicher Darstellung wie Fig. 1 eine weitere Ausbildungsform eines Teils des Sprungantriebs;

Fig. 8

den in der Fig. 7 gezeigten Teil des Sprungradantriebs in Seitenansicht;

Fig. 9

eine erste Ausbildungsform einer Verriegelungsvorrichtung des Sprungantriebs beim Abstützen der Abgangswelle in Ausschaltstellung;

Fig. 10

die Verriegelungsvorrichtung gemäss Fig. 9 beim Abstützen der Abgangswelle in Einschaltstellung;

Fig. 11

in gleicher Darstellung wie in Fig. 1 eine Ausbildungsform des Sprungantriebs mit zwei Schraubenfedern in Ausschaltstellung;

Fig. 12

in Ansicht die Ausbildungsform gemäss Fig. 11 in Einschaltstellung;

Fig. 13

eine zweite Ausbildungsform der Verriegelungsvorrichtung beim Abstützen der Abgangswelle in Ausschaltstellung; und

Fig. 14

die Verriegelungsvorrichtung nach Fig. 13 beim Abstützen der Abgangswelle in Einschaltstellung.

The present invention will now be explained in more detail with reference to the drawing. It shows purely schematically:

Fig. 1

in view a part of a spring drive with a spring-loaded arrangement in the off position, partially cut along the line II of Fig. 2;

Fig. 2

the part of the jump drive shown in Figure 1 in a section along the line II-II of Fig. 1.

Fig. 3

in the same representation as FIG. 2, the part of the spring drive in the switched-off position with the spring-loaded arrangement tensioned before the output shaft is released for switching on;

Fig. 4

in view the part of the spring drive shown in Figure 1 in the on position.

Fig. 5

the part of the jump drive shown in Figure 4 in a section along the line VV.

Fig. 6

in the same representation as FIG. 5, the part of the spring drive shown in FIG. 4 in the switched-on position, but with the spring-loaded arrangement tensioned for switching off shortly before the output shaft is released for switching off;

Fig. 7

in the same representation as Figure 1, a further embodiment of part of the jump drive.

Fig. 8

the part of the jump wheel drive shown in Figure 7 in side view.

Fig. 9

a first embodiment of a locking device of the jump drive when supporting the output shaft in the off position;

Fig. 10

the locking device of Figure 9 when supporting the output shaft in the on position.

Fig. 11

in the same representation as in Figure 1, an embodiment of the spring drive with two coil springs in the off position.

Fig. 12

in view the training form according to FIG 11 in the on position.

Fig. 13

a second embodiment of the locking device when supporting the output shaft in the off position; and

Fig. 14

the locking device of FIG. 13 when supporting the output shaft in the on position.

The snap drive shown in the figures is provided for the rapid switching on and off of electrical switches 10 schematically indicated in FIG. 1, in particular load switches, disconnectors and earth switches for medium and high voltage. It has an input shaft 12 and an output shaft 14 spaced parallel to it. On the input shaft 12, a tension lever 16 sits in a rotationally fixed manner, which, from a first end position 18 indicated by solid lines in FIG. 1 and dash-dotted in FIG. 4, runs counterclockwise (by approximately an angle of 80 °) into a position shown in FIG. 1 dash-dotted and in Fig. 4 indicated by solid lines second end position 18 'and can be rotated back again. The input shaft 12 is rotated by means of rotary means 20, which is indicated schematically in FIG. 1, for example by hand by means of a crank which can be plugged onto the input shaft 12 or electrically by means of a geared motor.

On the output shaft 14 connected to the switch 10, a drive lever 22 is seated in a rotationally fixed manner. It moves from a switch-off position 24 indicated by solid lines in FIG. 1 and in dash-dotted lines in FIG. 4 in a counterclockwise direction (also approximately at an angle of 80 °) into one 1 in dash-dot lines and in FIG. 4 switch-on position 24 'shown in solid lines and again is rotatable back.

A spring-loaded arrangement 26 interacts with the tensioning lever 16 and drive lever 22 and thus with the input shaft 12 and the output shaft 14, the coil spring 28 acting as a compression spring thereof being connected to the tensioning lever 16 and drive lever 22 via a link arrangement 30.

The tab arrangement 30 has a double tab 32 with two identical tabs 32 'and a single tab 34 arranged between the latter and displaceable relative thereto in the direction of the longitudinal extent. The helical spring 28 encompasses the tab arrangement 30 and, with its spring end 36 facing the tensioning lever 16, is supported on the double tab 32 via a perforated disk 38 and a pin 40. The pin 40 penetrates through the seat plate at right angles to the spring axis 28 'and thus at right angles to the longitudinal extension of the tab arrangement 30 and an elongated hole-like recess 42 of the individual tab 34 which extends in the longitudinal direction of the tab arrangement 30. The spring end facing the drive lever 22 is supported in an analogous manner 36 'also via a perforated disk 38' and a pin 40 'on the individual tab 34. The pin 40 'passes through the tabs 32' of the double tab 32 through a slot-like recess 44, which extends in the longitudinal direction of the tab arrangement 30, and fits tightly over the single tab 34.

The tabs 32 'have an elongated hole-like further recess 46 on their tension lever-side end region, this further recess 46 and the recess 42 of the individual plate 34 overlapping and in the region of the Overlap are penetrated by a driving pin 48 arranged on the tensioning mist 16. Another driving pin 50 is arranged on the drive lever 22; the latter extends through the recess 44 of the double strap 32 outside the end 34 ′ of the single strap 34 on this side.

The tabs 32 'of the double tab 32 interact with the driving pin 48 via a first driving stop 52 and with the further driving pin 50 via a second driving stop 54. The first driving stop 52 is formed by the end of the further recess 46 facing the spring end 36 and the second driving stop 54 is formed by the end of the recess 44 facing away from this. At the same time, the individual tab 34 cooperates with its end of the recess 42 facing away from the spring end 36 'with the driving pin 48 as the first driving stop 56 and with the end 34' with the further driving pin 50 as the second driving stop 58.

In order to ensure that the output shaft 14 is entrained when switching on, as is described in more detail below, the tabs 32 'of the double tab 32 have at their end of the recess 44 facing the tensioning lever 16 a stop 60 and which cooperate with the pin 40' the individual tab 34 at its end of the recess 42 facing the drive lever 22 has a stop 62 which interacts with the driving pin 48. In a corresponding manner, the end of the further recess 46 of the double bracket 32 remote from the drive lever 22 interacts as a stop 64 with the driving pin 48 of the tensioning lever 16 in order to forcibly take the output shaft 14 with it when it is switched off.

A locking device 66 controlled by the input shaft 12 interacts with the output shaft 14 and is described in more detail below in connection with FIGS. 9 and 10. This locking device 66 holds the output shaft 14 in its switch-off position 24 when it is switched on, until the input shaft 12 reaches a switch-in / unlocking position 68 when rotating from the first end position 18 in the direction toward the second end position 18 ', as in FIG Position driving pin 48 is indicated. The stroke which the driving pin 48 travels from the first end position 18 to the switch-on-unlatching position 68 is indicated by the double arrow E in FIG. 3. Likewise, when switching off, the output shaft 14 is held in the switch-on position 24 'until the tensioning lever 16 overcomes a switch-off decay position 68' from its second end position 18 'in the direction toward the first end position 18, which is shown in FIG. 6 by being in this position driving pin 48 is indicated. The stroke that this driving pin 50 travels from the second end position 18 'to the switch-off-unlatching position 68' is indicated by the double arrow A in this figure. Since switching on the switch 10 requires more energy than switching off, the stroke E is greater than the stroke A.

7 and 8 show the spring-loaded arrangement 26, with another possible embodiment of the plate arrangement 30. The difference from the plate arrangement 30 shown in FIGS. 1 to 6 is that the single plate 34 now as a tube 70 and the double plate 32 as that Single tab 72 extending through tube 70 are formed. Corresponding are the recess 42 cooperating with the pins 40, 40 ', the driving pin 48 and further driving pin 50 on the tube 70 and the recess 44 and further recess 46 on the tab 72. The end of the tube 70 on the output shaft side and the axial ends of the recesses 42, 44, 46 on the tube 70 and on the tab 72 act in the same manner as in the embodiment according to FIGS. 1 to 6 as driving stops 52, 54, 56, 58 and stops 60,62,64. In this regard, reference is made to the description above.

The locking device 66 shown in FIGS. 9 and 10 has a control slide 74 which can be moved back and forth in the direction of the double arrow S and which cooperates with its two control cams 76, 76 'with two mutually opposite control lugs 78, 78' of a cross-shaped release lever 80 . The trigger lever 80 is articulated on one end to a holding lever 82 which is non-rotatably seated on the output shaft 14 and is articulated at the other end with the free end of a rocker 84 mounted in a fixed position. The rocker 84 is pressed against a stop pin 88 by a compression spring 86, so that the rocker 84 abutting the stop pin 88 and the trigger lever 80 are in an over-center position when the output shaft 14 is in the switch-off position 24 and switch-on position 24 '.

The control slide 74, which is displaceably guided via an elongated hole guide pin guide 90 parallel to the spring axis 28 ′ and the longitudinal extent of the link arrangement 30, is articulated via a connecting link 92 to a control lever 94 which is non-rotatably seated on the input shaft 12. In the 9, the control slide 74 is shown in its position corresponding to the first end position 18 of the input shaft 12, in which the output shaft 14 is in the switch-off position 24. Compared to this position, the control slide 74 is displaced when the input shaft 12 is brought into the second end position 18 'into a corresponding position shown in FIG. 10. 10 shows the mutual dead center position of the release lever 80 and the rocker 84 in the switched-on position 24 '. In the switch-off position 24, the first control lug 78 projects into the path of movement of the first control cam 76 (FIG. 9), and in the switch-on position 24 'the second control lug 78' engages in the path of movement of the second control cam 76 '(FIG. 10).

The locking device 66 functions as follows: If the input shaft 12 is turned from its first end position 18 (FIG. 9) counterclockwise towards the second end position 18 'in order to switch on the switch 10, the first control cam 76 runs onto the first control lug 78 and takes this with it, which entails rotating the release lever 80 around its connecting pin with the holding lever 82 in the counterclockwise direction. The rocker 84 is raised against the force of the compression spring 86 from the stop pin 88. As soon as the input shaft 12 reaches the switch-on unlatching position 68 (cf. FIG. 3), the axis of the connecting pin mentioned crosses the straight line between the bearing axis of the rocker 84 and its connection to the release lever 80, which is equivalent to the dead center position being exceeded. As a result, the output shaft 14 is released so that it moves into the switch-on position 24 'under the force of the spring-loaded arrangement 26. pivots. The trigger lever 80 also rotates about the linkage to the rocker 84 by a little more than 180 ° into the other over-dead center position shown in FIG. 10, where the output shaft 14 is prevented from rotating in the direction toward the switch-off position 24. To switch off, the input shaft 12 is pivoted clockwise from its second end position 18 'towards the first end position 18. The second control cam 76 'runs onto the second control lug 78' and takes it with it, which now results in the rotation of the trigger lever 80 clockwise around the linkage to the holding lever 82. The rocker 84 is in turn lifted off the stop pin 88. As soon as the input shaft 12 has reached the disengaging-unlatching position 68 '(FIG. 6), the axis of the connection mentioned crosses the extension of the straight line between the bearing axis of the rocker 84 and its articulation to the release lever 80, so that the mutual dead center position is now eliminated . Under the force of the spring-loaded arrangement 26, the output shaft 14 is now pivoted back into the switch-off position 24, which entails turning the trigger lever 80 into the position shown in FIG. 9.

11 and 12 show, in the same representation as FIGS. 1 and 4, a spring drive, the spring-loaded arrangement 26 of which has two coil springs 28, 28 ''. The tensioning lever 16 seated on the input shaft 12 and the drive lever 22 arranged on the output shaft 14 are double-armed and each helical spring 28, 28 '' acting as a compression spring acts via the corresponding tab arrangement 30, 30 'with the corresponding arms of the tensioning lever 16 and the drive lever 22 together. 11 and 12 associated with the lower coil spring 28 Tab arrangement 30 is identical to the tab arrangement shown in FIGS. 1 to 6. The structure of the tab arrangement 30 'shown above also essentially corresponds to that of the lower tab arrangement 30, whereby it is arranged in reverse, so that the area facing the tensioning lever 16 in the lower spring storage arrangement 26 and lower tab arrangement 30 now faces the drive lever 22 and vice versa . When switched on, the lower spring-loaded arrangement 26 and tab arrangement 30 thus have the same effect as the arrangement shown in FIGS. 1 to 6 when switched on, whereas the spring-loaded arrangement 26 and tab arrangement 30 shown in FIGS. 11 and 12 above have the same effect when switched on as the arrangement of FIGS. 1 to 6 when switching off. The only constructive difference is that in the upper link arrangement 30 the further recess 46 of the individual link 34 is not designed like an elongated hole but as an open recess at the end of the individual link 34 on this side. The take-out shaft is forcibly carried along when switching off through the further recess 46 in the double link 32 of the lower link arrangement 30.

The embodiment of the locking device 66 shown in FIGS. 13 and 14 has a double-armed control lever 74 'which is freely rotatably mounted on the output shaft 14 and which, with its two control cams 76, 76' arranged on one lever arm, with the two control lugs 78, 78 located opposite one another 'of the cross-shaped trigger lever 80 cooperates. The holding lever 82, which is non-rotatably seated on the output shaft 14, is pivotably connected to one end of the release lever 80, which in turn is connected is hinged at its other end to the stationary rocker 84. In contrast to the embodiment shown in FIGS. 9 and 10, the rocker 84 is urged by the compression spring 86 in the upward direction against the stop pin 88, so that the rocker 84 abutting the stop pin 88 and the release lever 80 are in their off position 24 (FIG. 13) and switch-on position 24 '(FIG. 14) of the output shaft 14 located in an over-center position.

The connecting link 92 connects the input shaft 12 to the control lever 74 ', in that the former is articulated on one end to the control lever 94 which is non-rotatably seated on the input shaft 12 and on the other to the lever arm of the control lever 74' remote from the control cams 76, 76 '.

The basic mode of operation of this embodiment of the locking device 66 is the same as that shown in FIGS. 9 and 10. 13, the control lever 74 'is in its position corresponding to the first end position 18 of the input shaft 12 and the output shaft 14 is in the switched-off position 24. When the input shaft 12 is pivoted counterclockwise into the second end position 18' shown in FIG the control lever 74 'is also pivoted counterclockwise. The trailing control cam 76 runs onto the corresponding control lug 78 and takes it with the trigger lever 80 being rotated in the counterclockwise direction in order to link it to the holding lever 82. As soon as the release lever 80 and the rocker 84 exceed their mutual dead center position, the outgoing shaft 14 is released so that it is under the force of the spring-loaded arrangement 26 (compare FIGS 7, 11, 12) is pivoted into the switch-on position 24 '. The rocker 84 and the release lever 80 come into their other over-dead center position shown in FIG. 14.

To switch on, the input shaft 12 is rotated clockwise from its second end position 18 ', with the result that the control cam 76' now runs onto the control lug 78 'and takes it with it until the trigger lever exceeds its dead center position with the rocker 84. As a result, the output shaft 14 is released for switching off.

The operation of the spring drive according to the invention is as follows: if the input shaft 12 is in its first end position 18 and the output shaft 14 is in the switched-off position 24, as shown in FIGS. 1 and 2 and 11, the spring end 36 of the prestressed coil spring 28 is supported the first driving stop 52 of the double strap 32 on the driving pin 48 of the tensioning lever 16. Furthermore, the double strap 32 with the second driving stops 54 bears on the other driving pin 50 on the one hand and the single tongue 34 with its second driving stop 58 on the other pin 50 on the other hand. As a result, the switch-off position 24 of the output shaft 14 is given.

If the input shaft 12 is now turned counterclockwise to switch on, the double bracket 32, which rests on the driving pin 48 with its first driving stop 52, is taken along, so that the spring end 36 on this side in the direction of the spring axis 28 'onto the other spring end 36' for further tensioning of the coil spring 28 is moved. The Spring end 36 'cannot deflect, since the individual tab 34 presses with its second driving stop 58 against the further driving pin 50. However, due to the locking device 66 blocking the output shaft 14, as shown in FIGS. 9 and 11, this cannot escape. When the release position 68 (FIG. 3) is reached by the tensioning lever 16, the coil spring 28, 28 ″ is further tensioned in accordance with the stroke E. The stored spring energy is now available for switching on the switch 10. In the on-unlatching position 68, the locking device 66 releases the outgoing shaft 14, which leads to rapid switching on by moving the outgoing shaft 14 into the on position 24 '. The coil spring 28, 28 ″ relaxes again by its stroke B by the stroke E, as can be clearly seen in FIGS. 4 and 5 in comparison to FIGS. 1 and 2.

The switch-on unlatching position 68 is not far from the second end position 18 ′ of the input shaft 12.

If for some reason the output shaft 14 does not move after the release-unlatching position 68 is exceeded after the release by the locking device 66, the stops 60 run onto the pin 40 'and the pin 40 onto the stop 62, which leads to a forced take-along further driving pin 50 and thus the output shaft 14 through the second driving stop 58 of the individual plate 34 until the input shaft 12 has reached the second end position 18 '.

To turn off the input shaft 12 from the in 4 and 5 shown second end position 18 'rotated clockwise towards the first end position 18. The spring end 36 'is brought towards the spring end 36 in the direction of the spring axis 28' by the individual tab 34 which bears against the driving pin 48 with its first driving stop 56. This in turn results in the further tensioning of the helical spring 28, 28 ″ corresponding to the stroke A up to the switch-off-unlatching position 68 ′, see FIG. 6. The stroke A is smaller than the stroke E when the switch 10 is switched off required energy is less than the energy for switching on. In the off-unlatching position 68 ', the locking device 66 releases the output shaft 14, after which it moves under the force of the helical spring 28, 28''from the on position 24' in a clockwise direction towards the off position 24. In this case, the double tab 32 with its first driving stops 52 again comes into contact with the driving pin 48 and the further driving pin 50 runs onto the second driving stop 58 of the single tab 34. The energy not required for switching off is taken up again by the helical spring 28. A switch-off brake can therefore be dispensed with. Since the speed of rotation of the input shaft 12 is generally much lower than the speed of the output shaft 14 when switching, the output shaft 14 is then moved synchronously with the input shaft 12 into the switch-off position 24 when it is fully returned to the first end position 18. The spring drive is now ready to be switched on again.

Should the output shaft 14 not turn off when switched off after the release by the locking device 66 move the switch-on position 24 ', this is in turn coupled to the forced take-along to the input shaft 12 by the driving pin 48 running onto the stops 64 of the double bracket 32 and taking the further driving pin 50 with them via the second driving stops 54.

If the forced coupling of the output shaft 14 to the input shaft 12 can be dispensed with when switching on and / or switching off, the stops 60 and 62 or the stop 64 must be omitted, this can be done by correspondingly extending the recesses 42, 44 and the further recess 46 done. If necessary, this further recess 46 can be made open, as shown in FIGS. 11 and 12 above.

Of course, the clamping lever 16 can also be used as a control lever for the pawl device 66. In this case, the connecting strap 92 is articulated directly to the tensioning lever 16. Likewise, the drive lever 22 can also serve as a holding lever. In this case, the trigger lever 80 is articulated to the drive lever 22.

It is also possible to bring only one coil spring into effect in a spring-loaded arrangement with two coil springs for switching on and off. For this purpose, the corresponding driving stops are omitted, for example on the double strap or the single strap.

It is also conceivable to adjust the position of the control cams on the control slide. This allows the energy of the spring-loaded arrangement to be adapted to the individual switch.

Claims (10)

1. Jump drive for the rapid connection and disconnection of electrical switches, especially of on-load switches, isolating switches and grounding switches for medium and high voltage, having a primary shaft (12) which exhibits a tension lever (16) and can be rotated to and fro between two end settings (18, 18'), having a thereto parallel delivery shaft (14) which can be rotated to and fro between a disconnect (24) and a connect (24') setting and exhibits a drive lever (22), having a spring-loading arrangement (26) having at least one helical spring (28, 28"), which interacts by its spring ends (36, 36'), movable relative to each other in the direction of the spring axis (28'), with the tension lever (16) and the drive lever (22), and having a detachable supporting device (66) for supporting the delivery shaft (14) in the disconnect (24) and connect (24') settings, counter to the force of the spring-loading arrangement (26) which can be tensioned upon the rotation of the primary shaft (12) from the respective end setting (18, 18') in the direction of the other end setting, up to an unlatching setting (68, 68') of the primary shaft (12) preceding the respective other setting (18', 18), characterized in that the helical spring (28, 28") interacts by each of its spring ends (36, 36'), via driver elements (52, 54, 56, 58), with the tension lever (16) and the drive lever (22) and is held pre-tensioned between the driver elements (52, 54, 56, 58).
2. Jump drive according to Claim 1, characterized by means, which are active after at least the one unlatching setting (68, 68') has been crossed by the primary shaft (12), for the enforced transportation of the delivery shaft (14) by the primary shaft (12).
3. Jump drive according to Claim 1 or 2, characterized in that the spring ends (36, 36') are each supported on a butt strap (32, 34) and each butt strap (32, 34) respectively exhibits a driver element (52, 54, 56, 58) for the tension lever (16) and the drive lever (22).
4. Jump drive according to Claims 2 and 3, characterized in that the means for the enforced transportation of the delivery shaft (22) exhibit a stop (60, 62, 64) disposed on a butt strap (32, 34), this stop (60, 62, 64) being distanced from a therewith interacting counter-stop (40, 40', 48, 50) at least by the length of travel (E, A) from the corresponding end setting (18, 18') up to the unlatching setting (68, 68') concerned.
5. Jump drive according to Claim 4, characterized in that the butt straps (32, 34) embraced preferably by the helical spring (28, 28") exhibit longhole-like recesses (42, 44, 46) which are passed through by driving members (48, 50), which are disposed on the tension lever (16) or on the drive lever (22) and interact with the driver elements (52, 54, 56, 58), and in that the driver elements (52, 54, 56, 58) and, where appropriate, the stop (60, 62, 64) are formed at the ends of the recesses (42, 44, 46) on the butt straps (32, 34).
6. Jump drive according to one of Claims 3 to 5, characterized in that the one butt strap (34) is formed by a tube (70) which is passed through by the other butt strap (32).
7. Jump drive according to one of Claims 1 to 6, characterized in that the tensioning path (A) of the helical spring (28) in the one switching direction, preferably in the disconnect direction, up to the corresponding unlatching setting (68') is less than the tensioning path (E) in the other switching direction, so that the helical spring (28) absorbs the energy which is not required by the switch (10).
8. Jump drive according to one of Claims 1 to 7, characterized in that the spring-loading arrangement (26) exhibits two helical springs (28, 28") which respectively interact with an arm of the twin-armed tension and drive levers (16, 22), the one helical spring (28, 28"), where appropriate, interacting by one of its spring ends, via just a single driver, with the tension lever or the drive lever.
9. Jump drive according to one of Claims 1 to 8, characterized in that the supporting device (66) exhibits a rocker (84) and a trip lever (80), which is pivotably mounted on said rocker, is connected to the delivery shaft (14) and can be actuated by the primary shaft (12), the rocker (84) and the trip lever (80) being located, in their locking settings, in a mutual dead centre position.
10. Jump drive according to Claim 9, characterized in that the trip lever (80) exhibits control bosses (78, 78') which interact with control cams (76, 76') on a control element (74, 74') connected to the primary shaft (12).

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