EP2099044B1 - Switching mechanism - Google Patents

Description

An electric shift detent having a main power station comprising a drive shaft and a power take-off unit coupled thereto, the power take-off unit being mechanically coupled to movable contact carriers to effect closure of an electrical contact upon actuation of the drive shaft due to movement of the contact carriers, according to the preamble of the claim 1.

Such electrical switch racks have long been known and described in relevant standards, e.g. in EN 60947-1: 2004 (IEV 441-14-10, IEV 441-14-12). They are used in particular for load switches, switch disconnectors or DC switches.

The drive shaft of the Hauptrastwerks is usually directly connected to a handle that allows the user to operate the drive shaft, which is subsequently coupled directly to the output unit, which in turn is directly coupled to one or more movable contact carriers. By turning the handle thus one or more contacts can be opened or closed.

The movement of the output unit takes place against two springs, which are designed as Totpunktfedern, so that the springs counteract the rotational movement of the output unit first and thus complicate it and support the rotational movement of the output unit after exceeding the dead center and thus facilitate. Since the drive shaft is directly coupled to the output unit, ie. without mechanical delay element, the springs also act directly on the output unit. The release of the locking mechanism takes place after exceeding the dead center of the springs very fast, but can also by the user due to the direct effect of the springs on the output unit be blocked or delayed with appropriate sensitivity even at will.

A disadvantage has thus been found that when switching such electrical Schaltrastwerke, ie. when closing the contacts, the user can quickly change the handle after exceeding the dead center of the springs by sensitive the spring force counteracting between closed contacts and open contacts and thus can provoke the formation of an arc. At the same time there is the risk of so-called contact bounce (short-term, unwanted repeated opening and closing of a contact) in known such electrical Schaltrastwerken during the closing process. As a result, depending on the load to be switched, voltage spikes, which cause noise emissions in the HF range and can interfere with other equipment in the environment sensitive via the coupling in lines. Far more serious, however, are the effects of the shutdown spark resulting from the contact bounce. These lead to continuous evaporation and thus to wear or even destruction of the contact materials.

To avoid the disadvantages described so-called hand-independent Schaltrastwerke are known in which after triggering, ie. After exceeding the dead center closing or opening the contacts by hand can not be delayed or even blocked. Such a mechanism is, for example, in the rear derailleur according to the WO 2005/076302 A1 implements, in which an indirect coupling of actuator unit and output unit is realized via a combination of spring elements. The movement of the output unit takes place against two springs, which are designed as dead center springs. The mechanical connection of actuator and output unit is given by a coil spring, the switching operations at the beginning counteracts, and this supports after exceeding the dead center, so that the switching action is independent of hand.

When switching off, ie. However, when opening the contacts, these prior art electrical Schaltrastwerke have the disadvantage that they allow in the case of welded due to a short circuit contacts, however, an almost complete rotation of the handle. The dead center pushes the handle despite welded and thus live contacts to about 5 ° before their off position. In other words, a person operating the handle often does not recognize whether the contacts are actually separated due to the position of the handle. In practice, such manual electrical switchgear assemblies are usually coupled to a mechanical safety mechanism that allows opening of the live components only when the handle is in the off position, assuming that the contacts are reliably isolated in this case. Practice has shown, however, that in the example described with welded contacts due to a short circuit, an opening despite mechanical safety measures was possible because the handle was blocked just before the off position.

It is therefore an object of the present invention to provide an electrical switching raster, which prevents the disadvantages described and applies a high closing force for closing the contacts and provides increased reliability in welded contacts or in view of the occurrence of contact bounce.

According to the invention this is in an electrical Schaltrastwerk with a drive shaft and an output unit coupled thereto comprising the main drive unit, wherein the output unit is mechanically coupled to movable contact carriers to cause upon actuation of the drive shaft, the closing or opening of an electrical contact due to the movement of the contact carrier achieved in that an additional detent mechanism is provided with an actuating unit and a mechanically coupled thereto switching shaft unit which is coupled to the drive shaft of the Hauptrastwerks via a mechanical translator unit which has at least one drag intake, which cooperates with drag elements of the actuating unit and the switching shaft unit to the movement to transmit the actuator unit to the switching shaft unit, wherein the mechanical translator unit by means of at least one designed as Übertotpunktfeder spring element against a Be movement thereof is biased to urge the translator unit in its initial or final position and to allow a hand-independent movement of the actuating unit movement of the switching shaft unit.

This makes it possible to couple the actuator unit indirectly to the switching shaft unit, so that a time-delayed rotation of the switching shaft unit in response to a rotation of the actuator unit is possible. At the same time, the characteristics of the main station and those of the additional station overlap.

The use of a mechanical translator unit is reliable, cost-effective and also uncritical with regard to the standardized safety requirements.

The desired indirect coupling of actuating unit and switching shaft unit can be carried out due to the drag elements both the towed elements of the operating unit and drag elements of the switching shaft unit receiving.

In order to allow a secure fixation of the translator unit in its initial or final position or to allow the so-called hand-independent movement of the switching shaft unit of the actuator, it is provided in the invention that the translator unit is biased by at least one spring element against movement thereof and the at least one spring element is designed as an over-center spring and urges the translator unit in its initial or final position.

The design of the two switching raster works is preferably carried out so that the switching moments of the two switching raster factories are added by their coupling at closing of the electrical contacts or on the other hand, when opening the or the electrical contacts a low breaking moment applied.

According to a particularly preferred embodiment of the invention, it is provided that the drag intake corresponds in shape to at least a portion of the trajectory of the towed elements and seen the length of the drag intake in the direction of movement of the towed elements and the dimension of the towed elements are coordinated so that when moving the Actuator both a hand-independent movement of the same with respect to the translator unit or the translator unit with respect to the switching shaft unit is possible as well as a directly coupled movement, in which the actuator unit, the translator unit or the translator unit tows the switching shaft unit due to the movement of the actuator unit.

As a result, a rotation of the actuating unit is possible over a predetermined angle of rotation, without rotating the translator unit and / or the switching shaft unit or the translator unit and subsequently also the switching shaft unit to perform a rotation, although the actuator unit is not rotated or blocked by the user ,

According to a further embodiment of the invention, it is provided that the towing receptacles are formed in a circular arc and the drag elements form a sector of a cylinder jacket and protrude into the towing receptacles. Due to this configuration of the towing receptacles or the towing elements, a particularly simple construction of a switch latch according to the invention is possible, since the rotational movement of the actuating unit can be used directly for the towing operations.

The arrangement of the translator unit between the actuator and the switching shaft unit, as well as the rotatable arrangement of the translator unit, actuator and switching shaft unit about a common axis results in a particularly space-saving embodiment of the invention.

According to a further embodiment of the invention, which is particularly advantageous in terms of manufacturing technology, it is provided that the at least one drag intake is designed as a passage opening in the translator unit and the at least one drag element of the actuation unit and the control shaft unit protrudes into the drag intake from mutually opposite sides of the translator unit.

In order to enable a safe operation of the electrical switching latching device, in particular a low breaking moment, it is provided in a preferred embodiment of the invention that the output unit of the Main ram is biased by at least one main spring element against movement of the same.

Here, the at least one main spring element is preferably designed as Übertotpunktfeder, which urges the output unit in its initial or final position. After overcoming a dead center due to a rotation of the output unit it is automatically transported to its initial or final position.

Although the drive shaft could also be coupled to the output unit indirectly or via various translator units, a direct coupling of the drive shaft to the output unit is provided in a preferred, because component-economical variant of the invention.

In a further preferred embodiment of the invention, it is provided that in the off position of the actuating unit, the drag intake allows a movement of the at least one drag element of the actuating unit in only one direction. In this way, it is clearly defined in which direction a switch-off movement of the actuating unit has to take place.

In order to enable a delayed entrainment of the tow member of the control shaft unit, which likewise projects into the tow receptacle, so that the translator unit rotated by the tow elements of the actuating unit can be prestressed by means of the at least one spring element, it is provided in a preferred embodiment of the invention that Position of the actuating unit, the tow receiver has a lying in the trajectory of the towing member of the actuator first freewheeling portion, which allows a relation to the translator unit independent first movement of the actuating unit.

A sufficiently large bias of the translator unit, which, after overcoming the dead center of the at least one spring element causes an automatic conveyance of the translator unit and thus the switching shaft unit in their on position, is made possible by the first freewheeling section is between 35 ° and 45 °.

The biasing and after overcoming the dead center of at least one spring element taking place automatic and fast conveying the translator unit and thus the switching shaft unit in their on position has the consequence that during a switch-on of the actuator, the formation of a contact elements of the contact carrier damaging electric arc is prevented.

By according to a preferred embodiment of the invention in the OFF position of the operating unit, the towed element of the switching shaft unit is viewed at a, relative to a leading in the on position first direction of movement of the towing element, the rear boundary wall of the tow receiver, a movement of the switching shaft unit is forced, as soon as the at least one drag element of the actuating unit sets the translator unit in rotation.

By according to a further preferred embodiment of the invention in the on position of the actuating unit, the drag element of the actuating unit is viewed at a, relative to a leading in the off position second direction of movement of the towing element, front boundary wall of the drag intake is arranged in the case of in the off Position leading rotation of the actuator unit an immediate, ie Undelayed entrainment of the translator unit causes.

To even during the turn-off movement of the operating unit, a biasing of the at Translated unit articulated to allow at least one spring element, which subsequently allows a completed conveying the translator unit and thus the switching shaft unit in its off position with little effort, it is provided in a further preferred embodiment of the invention that in the on position of the actuator unit between the trailing element of the switching shaft unit and a, viewed relative to a leading in the off position second direction of movement of the towing element, the rear boundary wall of the tow receiver a second freewheel section is arranged. The second freewheeling section is preferably between 35 ° and 45 °.

Here, in a particularly preferred embodiment of the invention, it is provided that, in the ON position of the actuating unit, the towing element of the control shaft unit is arranged on the front boundary wall of the tow take-up, viewed relative to a second movement direction of the towing element in the OFF position.

The biasing and after overcoming the dead center of the at least one spring element taking place automatic and fast conveying the translator unit and thus the switching shaft unit in the off position in turn has the consequence that prevents the emergence of the contact elements of the contact carrier damaging electric arc during a turn-off movement of the actuator becomes.

Fig.1

eine Schrägansicht eines Hauptrastwerks samt daran gekoppelter Schaltmodule

Fig.2

ein mit einem Zusatzrastwerk versehenes erfindungsgemäßes elektrisches Schaltrastwerk in Schrägansicht

Fig.3

eine Seitenansicht des erfindungsgemäßen elektrischen Schaltrastwerks gemäß Blickrichtung 34 in Fig.2

Fig.4

eine Vorderansicht des erfindungsgemäßen elektrischen Schaltrastwerks gemäß Blickrichtung 35 in Fig.2

Fig.5

eine Draufsicht auf das erfindungsgemäße elektrische Schaltrastwerks gemäß Fig.3

Fig.6

eine Schnittdarstellung durch das erfindungsgemäße elektrische Schaltrastwerk entlang Linie C-C in Fig.5

Fig.7

eine Schnittdarstellung durch das erfindungsgemäße elektrische Schaltrastwerk entlang Linie D-D in Fig.5 (Vertikalschnitt durch das Hauptrastwerk)

Fig.8

eine Schnittdarstellung durch das erfindungsgemäße elektrische Schaltrastwerk entlang Linie E-E in Fig.5 (Vertikalschnitt durch eines der Schaltmodule)

Fig.9

eine partielle Schnittdarstellung von in eine Schleppaufnahme einer Übersetzereinheit eingreifenden, in Aus-Stellung befindlichen Schleppelementen einer Schaltwelleneinheit gemäß einem horizontal durch das in Fig.3 ersichtliche Zusatzrastwerk geführten Schnitt

Fig.10

eine partielle Schnittdarstellung von in eine Schleppaufnahme einer Übersetzereinheit eingreifenden, in Aus-Stellung befindlichen Schleppelementen einer Betätigungseinheit gemäß einem horizontal durch das in Fig.3 ersichtliche Zusatzrastwerk geführten Schnitt

Fig.11

eine partielle Schnittdarstellung von in die Schleppaufnahme der Übersetzereinheit eingreifenden, in Ein-Stellung befindlichen Schleppelementen der Schaltwelleneinheit gemäß einem horizontal durch das in Fig.3 ersichtliche Zusatzrastwerk geführten Schnitt

Fig.12

eine partielle Schnittdarstellung von in eine Schleppaufnahme der Übersetzereinheit eingreifenden, in Ein-Stellung befindlichen Schleppelementen der Betätigungseinheit gemäß einem horizontal durch das in Fig.3 ersichtliche Zusatzrastwerk geführten Schnitt

Fig.13

einen Drehmomentverlauf des erfindungsgemäßen elektrischen Schaltrastwerks während einer Einschaltbewegung

Fig.14

einen Drehmomentverlauf des erfindungsgemäßen elektrischen Schaltrastwerks während einer Ausschaltbewegung

The invention will now be explained in more detail with reference to an embodiment. Showing:

Fig.1

an oblique view of a Hauptrastwerks complete with coupled switching modules

Fig.2

an inventive electrical Schaltrastwerk provided with a Zusatzrastwerk in an oblique view

Figure 3

a side view of the electrical Schaltrastwerks invention according to viewing direction 34 in Fig.2

Figure 4

a front view of the electrical Schaltrastwerks according to the invention according to viewing direction 35 in Fig.2

Figure 5

a plan view of the inventive electrical Schaltrastwerks according to Figure 3

Figure 6

a sectional view through the electrical Schaltrastwerk invention along line CC in Figure 5

Figure 7

a sectional view through the electrical Schaltrastwerk invention along line DD in Figure 5 (Vertical section through the main bridge)

Figure 8

a sectional view through the electrical Schaltrastwerk invention along line EE in Figure 5 (Vertical section through one of the switching modules)

Figure 9

a partial sectional view of engaging in a drag intake of a translator unit, located in the off position towed elements of a switching shaft unit according to a horizontal through the in Figure 3 apparent additional ratchet guided cut

Figure 10

a partial sectional view of engaging in a drag receiving a translator unit, located in the off position towed elements of an operating unit according to a horizontal through the in Figure 3 apparent additional ratchet guided cut

Figure 11

a partial sectional view of engaging in the drag intake of the translator unit, in one-position drag elements of the switching shaft unit according to a horizontal through the in Figure 3 apparent additional ratchet guided cut

Figure 12

a partial sectional view of engaging in a drag intake of the translator unit, in-position towed the Operating unit according to a horizontal through the in Figure 3 apparent additional ratchet guided cut

Figure 13

a torque curve of the electrical Schaltrastwerks invention during a switch-on

Figure 14

a torque curve of the electrical Schaltrastwerks invention during a turn-off

Fig.1 shows an electric shift ram 1 with a main ram 2, in whose substantially cuboidal housing 16, a drive shaft 3 is rotatably mounted. On either side of Haupastastwerks 2 any number of switching modules 6 is arranged. In the present embodiment, three switching modules 6 are provided with also substantially cuboidal housings 17 on the left and right of the main workstation 2, which are coupled via coupling means 21 in each case with the adjacent switching modules 6.

Like a in Figure 8 shown vertical section through such a switching module 6, is arranged in each housing 17 of the switching module 6 is a rotatably mounted about a rotation axis 28 and preferably substantially cylindrically shaped contact carrier 5. In the example made of plastic contact carrier 5 two made of a conductive material first contact portions 24 are arranged. The two first contact portions 24 are each arranged in a peripheral region of the contact carrier 5 and electrically conductively connected to one another by means of a connecting portion 26 passing through the contact carrier 5.

Each of the switching modules 6 is provided with two insertion openings 18, in which not shown electrical conductors insertable and to within the switching module housing 17th arranged contact terminals 22 by means of screw 23 can be fastened. The rigidly mounted in the switch module housing 17 contact terminals 22 each have a contact carrier 5 facing second contact portion 25 and are contacted by the first contact portions 24 of the contact carrier 5.

In the illustration of the module element 6 according to Figure 8 the second contact portions 25 of the contact terminals 22 are currently contacted by the first contact portions 24 of the contact carrier 5, so that a conductive contact between the two attached to the contact terminals 22 electrical conductors is made (on position of the contact carrier 5).

Like also in Figure 8 can be seen, each bent by about 90 ° relative to the connecting portion 26 first contact portions 24 of the contact carrier 5 are each provided by an adjusting spring 27, which exert a spring force in the direction of the corresponding second contact portion 25 of the contact terminals 22. A provision of such adjusting springs 27 causes - in the on position of the contact carrier 5 - even in the case of operational wear or material removal at the facing end faces of the contact portions 24, 25 yet reliable electrical contact between the first and second contact portions 24th , 25 is guaranteed.

A turn of the in Figure 8 illustrated contact carrier 5 in the clockwise direction would solve the electrical contact between the first contact portions 24 and the second contact portions 25 and carry the contact carrier 5 from its on position to an off position, not shown, in which held in the contact terminals 22 electrical conductors no longer electrically connected to each other.

A rotation of the contact carrier 5 in its on or in its off position is effected by a rotary actuation of the arranged in the main ram 2 drive shaft 3. The actuation of the drive shaft 3, which takes place in a manner which is described in more detail below, has the consequence that a drive unit 3 coupled to the drive shaft 3 engages in a coupling device 21 of the switching module 6 adjacent to the main workstation 2 and causes a rotation of the contact carrier 5. In the present exemplary embodiment, the coupling device 21 is formed integrally with the contact carrier 5 or as an extension of the contact carrier 5 passing through the switching module housing 17 (see FIG Fig.1 ).

In the Figure 7 , which is a sectional view along the section lines DD through a in Figure 5 1 shows an apparent output unit 4 which has an essentially disc-shaped coupling section 29 which passes through the housing 16 of the main ram 2 and is aligned about an axis aligned with the axis of rotation 28 of the contact carrier 5 - also referred to below as rotation axis 28 for the sake of simplicity - Is rotatably mounted.

Since the main ram 2 and the output unit 4 arranged therein operated in the present embodiment, two on both sides of the main ram 2 rows of switching modules 6, the output unit 4 has two opposing coupling portions 29, which pass through the housing 16 of the main ram 2 and a clutch with allow the coupling device 21 of each adjacent switching module 6.

For coupling the coupling portion 29 of the output unit 4 with the coupling device 21 of the switching module 6, the coupling portion 29 of the output unit 4 at one of the Drive shaft 3 repellent or the adjacent switching module 6 assigning side of a (not shown) father profile, which in a (in Fig.1 apparent, however, in this representation facing away from the main jib 2) nut profile 21a of the coupling device 21 of the switching module 6 engages.

The coupling portion 29 of the output unit 4 further comprises on one of the drive shaft 3 assigning side in Figure 7 only partially visible toothing 30, in which engages provided on the drive shaft 3 counter teeth in the manner of a pinion. In this way, a rotational movement of the drive shaft 3 about the main axis 14 in a rotational movement of the output unit 4 and the two coupling portions 29 to the orthogonal to the main axis 14 extending rotation axis 28 is translated.

As Figure 7 shows further, the output unit 4 of the main ram 2 is biased by means of two executed as Übertotpunktfedern for triggering the Hauptrastwerks 2 main spring elements 15 against movement of the output unit 4. For articulation of the main spring elements 15, the output unit 4 is provided with two arranged in the peripheral region of the coupling portions 29 first support members 31, while on an inner side of the housing 16 of the Hauptrastwerks 2 corresponding further support members 32 are arranged. The longitudinal axes of the main spring elements 15 in this case run essentially tangentially to the circumference of the coupling sections 29 of the output unit 4.

Figure 6 shows a sectional view along the section lines CC through the in Figure 5 In this case, it can be seen how the mutually adjacent switching modules 6 and the contact carrier 5 mounted therein are also coupled together by means of their coupling means 21, so that a rotation of the in the main ram 2 mounted output unit 4 has a synchronous rotation of all contact carrier 5 of the switching modules 6 result. By an actuation or rotation of the drive shaft 3, which in turn has an operation or rotation of the output unit 4 of the main ram 2 result, so any number of switching modules 6 can be switched on and off simultaneously or can be held in the switching modules 6 contact carrier 5 be moved simultaneously in an on or in an off position.

According to the invention for actuating the drive shaft 3 of the Hauptrastwerks 2 in Fig.2 Apparently, on the main workstation 2 according to Fig.1 attachable additional latch 7 is provided.

That in the FIGS. 3 and 4 in side views according to the viewing directions 34 and 35 in Fig.2 shown, mounted on the Hauptrastwerk 2 additional latch 7 comprises an actuator 8 and a mechanically coupled thereto switching shaft unit 9 which is mechanically coupled directly to the drive shaft 3 of the main ram 2, the additional ratchet 7 according to the invention of the movement of the actuator 8 hand-independent movement of the switching shaft unit. 9 allows. The movements of the actuating unit 8 and the switching shaft unit 9 are again rotational movements about the main axis 14.

The drive shaft 3 of the main ram 2 and the switching shaft unit 9 of the additional ram 7 may be formed integrally in a special embodiment.

As in the sectional views according to Figure 6 and Figure 7 it can be seen, the coupling of the actuating unit 8 takes place with the switching shaft unit 9 via a mechanical translator unit 10th

A detailed representation of the translator unit 10 is in the Figures 9-12 seen. This show the FIGS. 9 and 10 one horizontally by the additional latch 7 according to Figure 3 guided sectional view, wherein the translator unit 10 is in an off position. This off-position of the translator unit 10 is accompanied by an already described off-position held in the switching modules 6 contact carrier 5 and with an off position held in the main ram 2, with the contact carriers 5 in engagement driven drive unit 4.

On the other hand, the show FIGS. 11 and 12 one horizontally by the additional latch 7 according to Figure 3 guided sectional view, wherein the translator unit 10 is in an on position. This on-position of the translator unit 10 is accompanied by a likewise already described on position of the contact carriers 5 held in the switching modules 6 or with an on position of the output unit 4 held in the main ram 2.

As in Figure 9 As can be seen, the translator unit 10 arranged within a housing 36 of the additional ram mechanism 7 has a substantially cylindrical body which is rotatable about the main axis 14 against the bias of two spring elements 13.

The spring elements 13 are in this case designed as Übertotpunktfedern and urge the translator unit 10 in its initial or final position or in their on or off position. For articulation of the spring elements 13, the actuating unit 8 is provided with two arranged in the peripheral region of the translator unit 10 first articulation 37, while on an inner side of the housing 36 of the additional latching 7, two corresponding further articulation elements 38 are arranged. The longitudinal axes of Spring elements 13 in this case run substantially tangentially to the circumference of the translator unit 10.

Within the housing 36 of the additional latching mechanism 7, first and second stop elements 39, 40 are provided, which can be contacted by first and second contacting sections 41, 42 of the translator unit 10. According to the present embodiment, two first stop elements 39 and two second stop elements 40 and two first Kontaktierabschnitte 41 and two second Kontaktierabschnitte 42 are provided, wherein the first and second stop members 39, 40 and the two Kontaktierabschnitte 41, 42 each about 180 ° relative to the Main axis 14 are offset.

In the in the FIGS. 9 and 10 shown off position of the translator unit 10, the two first stop members 39 are contacted by the two first Kontaktierabschnitten 41 of the translator unit 10, while in the in the FIGS. 11 and 12 shown one position of the translator unit 10, the two second stop members 40 are contacted by the two second Kontaktierabschnitten 42 of the translator unit 10. Thus, while in the off position of the translator unit 10, the first two Kontaktierabschnitte 41 of the translator unit 10 are pressed by the spring elements 13 against the corresponding first stop portions 39 of the Zusatzrastwerk housing 36 and thus the translator unit 10 is set in the off position, so in the on position of the translator unit 10, the two second contacting sections 42 of the translator unit 10 are pressed by the spring elements 13 against the corresponding second stop sections 40 of the main latch housing 36 and the translator unit 10 thus fixed in the on position.

The Kontaktierabschnitte 41, 42 of the translator unit 10 are arranged in the present embodiment of a substantially trigonal, projecting from the scope of the translator unit 10 flange, wherein two opposing, substantially tangent to the circumference of the translator unit 10 extending side surfaces of the trigonal flange element as the first or as second contacting portion 41, 42 serve. The first articulation elements 37 intended for holding the spring element 13 are in each case articulated centrally on the trigonal flange element, that is to say between the two contacting sections 41, 42.

As also in the Figures 9-12 can be seen, the translator unit 10 has two opposing Schleppaufnahmen 11, which are formed as substantially parallel to the main axis 14 extending through holes in the translator unit 10. Here, the tow shots 11 are each formed as a circular arc, concentric with the main axis 14 extending slots which extend in the present embodiment each over an angular range of 75 °. Each drag intake 11 has a first end portion 11a and a second end portion 11b, which are each in the form of substantially radially to the main axis 14 extending boundary walls.

The already mentioned actuating unit 8 has a in the sectional views according to the Figures 10 and 12 apparent, disposed within the housing 36 of the additional ram 7 rotational element 43 and a rigidly connected to the rotary member 43 and from the Zusatzrastwerk-housing 36 in a direction away from the main ram mechanism protruding shaft portion 8a (see also Figure 6 ). The in Fig.2 apparent, cylindrical shaft portion 8a of the actuator unit 8 extends along the main axis 14 of the electrical Schaltrastwerks first and is provided with a profiling, which allows a positive connection with a handle, not shown, for example, an angle handle.

In the present embodiment, the electrical Schaltrastwerk 1 is provided with a cover 33, which allows attachment of the electrical Schaltrastwerks 1 to a door of a control box, not shown. After screwing the covering element 33 arranged on the actuating unit 8, only the shaft section 8a of the actuating unit 8 or the handle placed on the shaft section 8a protrudes beyond a front side of the control box door facing the user.

The rotatable about the main axis 14 rotation member 43 of the actuator 8 is formed substantially cross-shaped and has two opposing, substantially radially to the main axis 14 extending first transverse arms 43a, at their end regions in each case a drag element 12a is arranged, which in an associated drag intake 11 protrudes. In the present exemplary embodiment, the towing elements 12a of the actuating unit 8 are each formed integrally with the rotary element 43 or with its first transverse arms 43a and project from the transverse arms 43a at an angle of 90 °.

In a part of the additional ratchet housing 36 facing the main ram 2, the already mentioned ripple shaft unit 9 directly coupled to the drive shaft 3 of the main ram station 2 is rotatably mounted. The additional lock housing 36 is in this case with a in Figure 6 and Figure 7 provided opening 53 through which the switching shaft unit 9 and / or preferably rigidly coupled to the switching shaft unit 9 drive shaft 3 protrude.

Also, the switching shaft unit 9 is provided with two tow elements 12b, which protrude into the trailing shots 11, but of one of the tow elements 12a of the actuator 8 opposite or according to Figure 3 lower side (shown in the sectional views according to Figure 9 and 11 ). The towing elements 12a of the actuating unit 8 and the drag elements 12a of the switching shaft unit 9 therefore each project into a common drag intake 11 and point towards each other, but without intersecting the path of movement of the respective opposing towed element 12a, 12b.

It should be noted that in the sectional views according to the Figures 9-12 are partial sectional views. The translator unit 10, the spring elements 13 and the stop elements and contacting sections 39-42, which are arranged in the housing 36 of the additional ratchet mechanism 7, are each shown in a top view, ie uncut, while only the rotational element 43 of the actuation unit 8 engaging in the translator unit 10 and the selector shaft unit 9 or the drag elements 12a, 12b of these components cut, so are shown hatched. To better understand these partial incisions are in Figure 3 two sections AA and BB drawn. The horizontal section through the additional ratchet 7 according to the section line AA results in a sectional view of the rotary member 43 of the actuator 8 and their associated towed elements 12a, as in the Figures 10 and 12 seen. The horizontal section through the additional ratchet 7 according to the section line BB runs slightly below the section line AA and results in a sectional view of the tow elements 12b of the switching shaft unit 9, as in the Figures 9 and 11 seen.

Corresponding to the circular arc shape of the towing receptacles 11, the towing elements 12a, 12b of the actuation unit 8 and the selector shaft unit 9 form a sector of a cylinder jacket and protrude into the tow receptacles 11 of the translator unit 10 in a direction substantially parallel to the main axis 14. A width of the trailing shots 11 measured radially to the main axis 14 is greater than a width of the trailing elements 12a, 12b which is also measured radially to the main axis 14.

With regard to the geometrical configuration of the drag intake 11, it can be said that the drag intake 11 corresponds in shape to at least one section of the trajectory of the towing elements 12a, 12b and the length of the tow intake 11, viewed in the direction of movement of the tow elements 12a, 12b, and the dimension of Towing elements 12a, 12b are coordinated so that upon movement of the actuator unit 8 both an independent movement of the same with respect to the translator unit 10 and the translator unit 10 with respect to the control shaft unit 9 is possible as well as a directly coupled movement, in which the actuator unit 8 the translator unit 10 or the translator unit 10, the switching shaft unit 9 tows due to the movement of the actuator unit 8, so that a total of a hand-independent movement of the switching shaft unit 9 of the actuator unit is possible.

The two abovementioned boundary walls of the drag intake 11, which correspond to the first and second end sections 11a, 11b, are hereinafter referred to as front or rear boundary walls, depending on the current direction of movement of the towed element 12b. In this context, as the front boundary wall always those boundary wall or that End section 11a, 11b understood, on which a drag element 12a, 12b located within the drag intake 11 is currently moving, while the rear boundary wall is that boundary wall or that end section 11a, 11b, from which a drag element 12a located within the tow catch 11, 12b currently moved away.

It should be noted that those end portions 11a, 11b or boundary walls of the tow dogs 11, which are contacted by the tow elements 12a of the operating unit 8 in the manner described in more detail below, do not necessarily, as in Figs Figures 9-12 shown and resulting due to the execution of the tow mounts 11 as a simple through holes, in a congruent arrangement to those end portions 11a, 11b or boundary walls of the tow mounts 11, which are contacted by the tow elements 12b of the switching shaft unit 9, must be arranged. On the other hand, it would also be possible in an alternative embodiment of the tow mounts 11 that the tow elements 12a of the actuating unit 8 and the tow elements 12b of the switching shaft unit 9 are each assigned their own boundary walls.

The rotational element 43 of the actuating unit 8 further comprises two offset by about 90 ° to the first transverse arms 43a second transverse arms 43b. The second transverse arms 43b also extend substantially radially to the main axis 14 and in the present embodiment each have the shape of an involute tooth.

Each of the second transverse arms 43b hereby has two involute sliding surfaces 47, 48 arranged on either side of a vertex 46, which are contacted by a round end section 44a of a contacting arm 44 during rotation of the actuating unit 8. The contacting arm 44 is is hinged to a bearing element 49 within the housing 36 of the additional latching mechanism 7 and is pressed against one of the first transverse arms 43a of the rotation element 43 by means of a tension spring 45 hinged to the end section 44a of the contacting arm 44, in order to prevent a biasing of the rotation element 43 against an actuation movement in the direction of the input shaft. or the off position of the operating unit 8 to allow.

In an in Figure 10 shown starting position or off position of the actuating unit 8 and the rotary member 4 are the drag elements 12a respectively in the region of the second end portion 11b of the tow receiver 11, so considered at the-relative to the first direction of movement 50 of the towed element 12b - rear boundary wall of the tow receiver 11 , In this off position of the actuating unit 8, the drag intake 11 allows a movement of the tow elements 12a of the operating unit 8 in only one direction, namely in the direction of the first direction of movement 50 leading into the on position of the actuating unit 8.

As in Figure 10 Furthermore, a longitudinal extent of the drag element 12a of the actuation unit 8 measured along the first movement direction 50 is less than a longitudinal extent of the tow receptacle 11 measured along the first movement direction 50, so that the tow receptacle 11 has a freewheel section lying in the trajectory of the tow element 12a of the actuation unit 8 11c. This freewheeling section 11 c, which may preferably extend over an angular range of 35 ° to 45 °, permits independent movement of the actuating unit 8 in the off position relative to the translator unit 10.

If the actuator 8 and the rotary member 43 from the in Figure 10 shown initial position or off position by means of an occurring in a first direction of movement 50 actuation movement in rotation, so there is initially an idle rotation of the rotation element 43, during which the translator unit 10 is not yet rotated or not yet by the tow elements 12a of the rotation element 43rd is dragged along. Only after this idle rotation, which in the embodiment according to Figure 10 extends over a the freewheeling portion 11c corresponding angular range of 30 °, the - relative to the leading in the on position first movement direction 50 of the towing element 12b considered - rear boundary wall (corresponding to the first end portion 11a) of the tow receiver 11 from towed element 12a of the rotary member 43 contacted and the translator unit 10 subsequently dragged along by the tow member 12a along the first direction of movement 50 over an angular range of 45 °, until the translator unit 10 is automatically forwarded by the spring elements 13 articulated at the second contacting sections 42 and the contacting sections 42 finally at the second stop elements 40 of the additional lock housing 36 find a stop, so that the translator unit 10 now in its final position or on position according to Figure 12 located. The actuation unit 8 or the rotation element 43 has thus been rotated by a total of 75 ° about the main axis 14 - following the first direction of movement 50 - by means of the spring elements 13 to move the translator unit 10 automatically from its initial position or independent of the movement of the actuation unit 8 To effect off position in its end position or on position (the translator unit 10 has thereby rotated by 90 °).

During this movement of the translator unit 10, the spring elements 13 articulated on the translator unit 10 are first of all compressed successively and can, after passing the first articulated elements 37 on a longitudinal axis 52 of the additional latch housing 36 (see FIG Figure 10 ), so after overcoming a dead center, expand again in a the second stop elements 40 of the Zusatzrastwerk housing 36 facing direction, which has the consequence that the spring elements 13 quickly into an in Figure 12 Jump over the position shown and thus trigger the locking mechanism. Thus, while at the beginning of in the first direction of movement 50 taking place actuating movement must be overcome by the spring elements 13 of the actuating movement opposite resistance, the translator unit 10 after completed rotation of the actuator 8 by an angle of 75 ° in the first direction of movement 50 (which is a passing of first articulation elements 37 on the housing longitudinal axis 52 corresponds) spring-assisted and therefore automatically transported into its final position or on position. The actuation unit 8 or the rotation element 43 are also rotated after insertion of the "snap-on" by an angle of 15 ° -following the first direction of movement 50 -but without a manual effort being necessary for this. The according to Figure 12 In its on-position rotary element 43 and the actuating unit 8 together with the handle, not shown, so compared to their off position shown in Figure 19 have experienced a rotation by a total of 90 °.

In the on position of the actuation unit 8, the towing elements 12a of the actuation unit 8 arrive at the second end section 11b of the tow receptacle 11 or at the front boundary wall of the tow receptacle 11, viewed relative to a second movement direction 51 of the towed element 12b leading to the off position for lying.

The mentioned, tensioned by means of tension springs 45 Kontaktierarme 44 serve to the actuating unit 8 already during their idle rotation, so even before contacting the first end portion 11a of the drag intake 11 by the drag element 12a of the rotation element 43, oppose a defined resistance and thus a "flutter to prevent the operating unit 8 during its operation.

In this case, the end portion 44a of the Kontaktierarms 44 slides at the onset of actuation movement in the first direction of movement 50 first at the according to Figure 10 moving clockwise second sliding surface 48 of the second transverse arm 43b of the rotary member 43 (which the rotation member 43, a resistance against the first direction of movement 50 opposes), while the end portion 44a of the Kontaktierarms 44 after passing through the vertex 46 of the second transverse arm 43b of the rotary member 43 at the first sliding surface 47 of the second transverse arm 43b of the rotary member 43 slides along (which causes a support of the actuating movement along the first direction of movement 50 and a torque application of the rotary member 43). Both in the initial position or off position and in the end position or on position of the translator unit 10, the convex end portion 44a of the contacting arm 44 is located in a recess of the rotation element 43 provided between the first transverse arm 43a and the second transverse arm 43b.

It should be noted that in the Figures 10 and 12 only one of the two Kontaktierarme 44 is equipped with a tension spring 45. In a preferred embodiment of the translator unit 10, however, both Kontaktierarme 44 are equipped with a tension spring 45, so that in the Figures 10 and 12 shown right Kontaktierarm 44 in one mirrored to the left illustrated contacting arm 44 arranged position is to imagine.

Since, as already mentioned, the towing elements 12b of the control shaft unit 9 protrude into the towing receptacles 11, with the above-described actuation cycle of the actuation unit 8 or the translator unit 10 also a movement of the selector shaft unit 9 and thus an actuation of the coupled with the switching shaft unit 9, in the main ram 2 mounted drive shaft 3.

However, the towing elements 12b of the switching shaft unit 9 are dragged without delay by the drag-receiving element 11, which is set in rotation by means of the towing elements 12a of the actuating unit 8, to the translator unit 10. Undelayed entrainment of the towing elements 12b of the control shaft unit 9 is accomplished by placing them in the OFF position of the actuating unit 8 on the second end portion 11b of the tow retainer 11 or on the rear boundary wall of the tow retainer 11, viewed relative to the first direction of movement 50 of the tow member 12b are.

As based on Figure 9 As can be understood, the towing elements 12b of the switching shaft unit 9 are thus conveyed along a contact direction through the second end sections 12b and the rear boundary walls of the towing receptacles 11 along the first direction of movement 50, until an on position according to Figure 11 is reached. Like the towing elements 12a of the operating unit 8, the towing elements 12b of the control shaft unit 9 are in the on position also in the region of the second end section 11b of the tow receptacle 11 or at the second movement direction 51, which is now in the on position relative to the actuating unit 8 Towing element 12b considered - front boundary walls of the tow receiver 11.

As a result of an actuation of the switching shaft unit 9, the drive shaft 3 mounted in the main ram mechanism 2 and, subsequently, the output unit 4 rotatable about the rotation axis 28 and thus the contact carrier 5 mounted in the switching modules 6 are actuated, respectively, respectively, from an off position to an on position Position (as already described in detail in the introduction).

• Da sich in der Ein-Stellung sowohl die Schleppelemente 12a der Betätigungseinheit 8 als auch die Schleppelemente 12b der Schaltwelleneinheit 9 im Bereich des zweiten Endabschnitts 11b der Schleppaufnahme 11 befinden (oder anders ausgedrückt, sich die Schleppelemente 12a und 12b an den - relativ zur die Betätigungseinheit 8 wieder in ihre Ein-Stellung führenden zweiten Bewegungsrichtung 51 betrachtet - vorderen Begrenzungswänden der Schleppaufnahme 11 befinden), hat eine der zweiten Bewegungsrichtung 51 folgende Drehung der Betätigungseinheit 8 zur Folge, dass die Übersetzereinheit 10 direkt, d.h. ohne Verzögerung von den Schleppelementen 12a der Betätigungseinheit 8 mitgeschleppt wird. Dieser Drehung der Übersetzereinheit 10 bzw. der Betätigungseinheit 8 wirken wiederum die bereits beschriebenen Federelemente 13 entgegen.

Transporting the actuating unit 8 and the switching shaft unit 9 from the in the FIGS. 11 and 12 shown one-positions back in the in the FIGS. 9 and 10 shown off-positions, which subsequently also causes a conveying of the output unit 4 and thus the mounted in the switching modules 6 contact carrier 5 in the off position, is carried out as follows:

• Since both the towing elements 12a of the operating unit 8 and the towing elements 12b of the switching shaft unit 9 are in the on position, in the region of the second end portion 11b of the tow receiver 11 (or in other words, the towing elements 12a and 12b at the - relative to the operating unit 8 again in their on-position leading second direction of movement 51 considered - front boundary walls of the tow receiver 11 are), one of the second direction of movement 51 following rotation of the actuating unit 8 with the result that the translator unit 10 directly, ie without delay from the tow elements 12a of the actuator 8 is dragged. This rotation of the translator unit 10 or the actuating unit 8 in turn counteract the spring elements 13 already described.

Because of the arrangement of the drag elements 12b of the switching shaft unit 9 at the front boundary walls or in the region of the second end portions 11b of Towing receptacle 11 and due to the already described above dimensioning of the towed elements 12b of the switching shaft unit 9 (whose along the second direction of movement 51 measured longitudinal extent is less than the longitudinal extension of the tow receiver 11) a in Figure 11 shows drawn second freewheeling portion 11d, the towed elements 12b of the switching shaft unit 9 are dragged by the translator unit 10 only after rotation of the actuating unit 8 by an angle corresponding to the second freewheeling portion 11d of 40 °. Contacting the towing elements 12b of the switching shaft unit 9 through the first end sections 11a or through the - viewed relative to the second direction of movement 51 - rear boundary walls of the tow receiver 11 takes place only after the second freewheeling portion 11d following a second direction of movement 51 following rotation of the translator unit 10 has reduced to zero.

If the towing elements 12b of the switching shaft unit 9 are contacted by the booster unit 10 after overcoming the free-wheeling section 11d, a synchronous movement of the actuating unit 8 and the switching shaft unit 9 follows the second movement direction 51 over a further angular range of preferably 5 °, until finally (the actuating unit 8 has been rotated at this time by 45 ° from the on position in the direction of the off position), in turn a "snapping" of the spring elements 13 and automatically conveying the actuator unit 8 and the switching shaft unit 9 in their off positions according to the FIGS. 9 and 10 starts.

In turn, the spring elements 13 articulated on the translator unit 10 are initially compressed successively during this movement of the translator unit 10 in the second direction of movement 51 and can, after passing the first articulated elements 37 on the longitudinal axis 52 of FIG Additional lock housing 36, so after overcoming a dead center, expand again in a the first stop elements 39 of the Zusatzrastwerk housing 36 facing direction until the first Kontaktierabschnitte 41 of the translator unit 10 come to the first stop elements 39 of the Zusatzrastwerk housing 36 to the stop.

For a better understanding of the functional mechanism of the electric switching mechanism 1 according to the invention are in the FIGS. 13 and 14 Torque curves during an actuation of the actuator 8 shown. The actuating unit 8, and thus also the not shown, arranged on the shaft portion 8a of the actuator 8 handle, are rotated during a promotion of the off position in the on position and vice versa in each case by a switching angle of 90 °. The in the FIGS. 13 and 14 The curve labeled "A" here describes in each case the resistance-related torque curve according to the components arranged in the additional detent mechanism 7, while the curve denoted by "B" in each case describes the resistance-related torque curve according to the components arranged in the main detent work 2 or associated therewith. The curve "A + B" illustrates a superposition or addition of the two curves "A" and "B" or the (resistance) torque curves illustrated by these curves.

At an in Figure 13 shown, to be read from left to right switching operation, in which the operating unit 8 is transported from its off position to its on position, it can be seen how initially (according to the provision of the already described freewheeling portion 11c) over an angular range of 30 ° a Leerdrehung the actuator 8 takes place, during which only one of the arranged in the additional latching 7 Kontaktierarmen 44 and 45 caused by its tension springs resistance must be overcome. Only from a switching path of 30 ° (the first end portions 11a of the drag intake 11 are contacted by the towing elements 12a of the actuating unit 8 at this time), prestressing of the spring elements 13 arranged in the additional detent 7 also takes place, or a resistance opposite to that of the spring elements 13 of the rotation of the actuating unit 8 has to be overcome , This caused by the spring elements 13 resistance or applied to overcome this resistance torque Md increases up to a switching angle of 75 ° linearly (see torque curve according to curve "A").

From a switching angle of 30 ° but also arranged in the main ram 2, hinged to the output unit 4 main spring elements 15 are biased because the tow elements 12b of the switching shaft unit 9 are now dragged by the translator unit 10. Also caused by the main spring elements 15 resistance or applied to overcome this resistance torque Md increases up to a switching angle of 75 ° linearly (see torque curve according to curve "B"), so that the spring elements 13 and the main spring elements 15 are biased synchronously and add the torque Md applied to build up these biases (see torque curve according to curve "A + B").

At a switching angle of 75 °, finally snap both arranged in the additional ram 7 spring elements 13 and arranged in the main ram 2 main spring elements 15, so that the actuator 8 and the shaft unit 9 according to the previously constructed and now again according to the curves "A" , "B" or "A + B" flattening bias voltage are automatically transported to their on position. In the on position, the actuating unit 8 or the handle has completed a rotation of 90 ° following the first direction of movement 50.

At an in Figure 14 shown, from right to left to read switching operation, in which the actuator unit 8 is moved from its on position back to its off position, it can be seen, as already directly upon the onset of rotation of the actuator 8 in the second direction of movement 51, a linearly increasing bias in the additional ram 7 arranged spring elements 13 takes place, since the translator unit 10 is dragged by the tow elements 12a of the actuator unit 8 immediately (see the according to Figure 14 right part of the curve "A").

Due to the provision of the already described second freewheeling section 11d of the towed receptacle 11, the towing elements 12b of the switching shaft unit 9 are only rotated by an angle of 40 ° in the second direction of movement 51 (which corresponds to a switching angle of 50 ° relative to the off position) is) carried along by the translator unit 10 so that the main spring elements 15 arranged in the main workstation 2 are also prestressed (see the linearly rising curve "B" in FIG Figure 14 ).

From completed rotation of the actuating unit 8 by 40 ° in the second direction of movement 51 and from the related to the off-position switching angle of 50 ° added by arranged in the additional detent 7 spring elements 13 and arranged in the Hauptrastwerk 2 main spring elements 15 conditional torque curves (see dot-dashed curve "A + B").

Now takes place over an angular range of 5 °, ie up to a switched on the off position angle of 45 °, a synchronous, the second direction of movement 51 following movement of the operating unit 8 and the switching shaft unit 9. At that time, at which the actuating unit was rotated by an angular range of 45 ° in the second direction of movement 51 (which also corresponds to an off-position related absolute switching angle of 45 °) snap again in the Additional ram 7 arranged spring elements 13 to, so that the actuator 8 is transported according to the previously constructed and now now again according to the curve "A" flattening bias voltage in its off position.

As based on Figure 14 However, even after reaching an off-position absolute switching angle of the operating unit 8 of 45 °, a further prestressing structure of the main spring elements 15 arranged in the main ram 2 takes place. However, this further preloading structure of the main spring elements 15 acts to actually relax or snap around Spring elements 13 of the additional latch 7 against. In other words, the snap-in spring elements 13 of the additional latching mechanism 7 now cause a prestressing of the main spring elements 15 of the main latching station 2.

The biasing structure of the main spring elements 15, which starts at an off-position absolute switching angle of 50 ° and takes place over an angular range of 45 ° in the second direction of movement 51, only ends with an absolute switching angle of 5 ° relative to the off position since the drive shaft 3 mounted in the main ram 2 is brought into a position by the selector shaft unit 9 only at this time, in which the main spring elements 15 snap over and thus trigger. Since the switching shaft unit 9 in turn is rotated by the applied by the spring elements 13 translator unit 10 in rotation, it is thus stored in the compressed spring elements 13 at the time of reaching the off position absolute switching angle of 45 ° spring force stored in another consequence of an automatic biasing and snapping the main spring elements 15 causes.

In the case of a short circuit of the electrical contacts of the contact carrier 5 or an operational welding the in Figure 8 shown first contact portions 24 of the contact carrier 5 with the corresponding second contact portions 25 of the contact terminals 22 of the switching module 6 is thus blocking the actuator 8 after rotation of the actuator 8 by about 50 ° in the second direction of actuation 51, so so still an open switching angle of about 40 ° from the off position remains.

That the operating unit 8 in the short circuit of the electrical contacts is not already after a rotation by 40 ° (ie at which time from which the switching shaft unit 9 is dragged by the translator unit 10) is due to the fact that the stored in the contact carrier 5 (in the one-position compressed) Justierfedern 27 relax with the onset of rotation of the contact carrier 5 and therefore arranged in the contact carrier 5 first contact portions 24 of the Justierfedern 27 in the direction of the contact terminals 22 associated second contact portions 25 pressed and kept in contact with this ( please refer Figure 8 ). The contact between the arranged in the contact carrier 5 first contact portions 24 and the stationary in the housing 17 of the switching module 6 arranged second contact portions 25 is, however, maintained only until the Justierfedern 27 have completely relaxed, which after rotation of the contact carrier by about 5 10 ° from his in Figure 8 shown on-position in the direction of its off position is the case.

While in conventional electrical hand-independent Schaltrastwerken in the case of short-circuit related welding of the contacts in a safety critical, almost complete rotation of the actuator unit 8 and whose handle was in the off position possible, then a rotation of the actuator 8 in the direction of off position in an inventive electrical Schaltrastwerk 1 thus already stopped much earlier and a occurring in one of the switching modules 6 short circuit is clearly obvious or opening of live components can be prevented.

LIST OF REFERENCE NUMBERS

1

Electric switching mechanism

2

Primary position work

3

drive shaft

4

driven unit

5

contact support

6

switching module

7

Additional detent mechanism

8th

operating unit

8a

shank portion

9

Switch shaft unit

10

The translator unit

11

slow uptake

11a

first end portion of the drag intake 11

11b

second end portion of the tow receiver 11

11c

first freewheel portion of the tow receiver 11

11d

second freewheeling section of the drag intake 11

12a

Towing elements of the operating unit 8

12b

Towing elements of the switching shaft unit 9

13

spring element

14

axis

15

Main spring element on output unit 4

16

Housing of the main station 2

17

Housing of the switching module 6

18

insertion

19

mounting holes

20

support element

21

coupling device

22

Contact terminals

23

screw elements

24

first contact sections (on contact carrier 5)

25

second contact sections (at contact terminals 22)

26

connecting portion

27

Justierfedern

28

Rotation axis (of the contact carrier 5)

29

Coupling section of the output unit 4

30

gearing

31

first support elements

32

additional support elements

33

cover

34

first viewing direction

35

second line of sight

36

Housing of the additional latch 7

37

first coupling elements (to output unit 4)

38

second hinge elements (on additional latch housing 36)

39

first stop elements

40

second stop elements

41

first contacting section

42

second contacting section

43

Rotational element (actuator unit 8)

43a

first cross arms

43b

second transverse arms

44

Kontaktierarm

45

tension springs

46

vertex

47

first sliding surface

48

second sliding surface

49

storage element

50

first direction of movement (from off to on position)

51

second direction of movement (from on to off position)

52

Longitudinal axis of the additional ratchet housing 36th

53

Opening in the additional lock housing 36

A

Torque curve - additional locking mechanism

B

Torque History - Main Workpiece

Claims (17)

1. An electrical switch latching mechanism (1), comprising main latching mechanism (2) having a drive shaft (3) and an output unit (4) coupled thereto, wherein the output unit (4) is mechanically coupled to movable contact carriers (5) in order to produce the closing and opening of an electrical contact due to the movement of the contact carriers (5) when the drive shaft (3) is actuated, characterized in that an auxiliary latching mechanism (7) is provided having an actuation unit (8) and an actuating shaft unit (9) which is mechanically coupled thereto and which is coupled to the drive shaft (3) of the main latching mechanism (2) via a mechanical combiner unit (10) which comprises at least one tow retainer (11) which cooperates with towing elements (12a, 12b) of the actuation unit (8) and the actuating shaft unit (9) in order to transmit the movement of the actuation unit (8) to the actuating shaft unit (9), wherein the mechanical combiner unit (10) is pretensioned by means of at least one spring element (13), which is arranged as an over-centre helper spring, against a movement thereof in order to push the combiner unit (10) to its initial or end position and in order to enable a movement of the actuating shaft unit (9) which is manually independent of the movement of the actuation unit (8).
2. An electrical switch latching mechanism according to claim 1, characterized in that the coupling of the auxiliary latching mechanism (7) to the main latching mechanism (2) produces an addition of the switching torques of the two latching mechanisms during the closing of the electrical contact.
3. An electrical switch latching mechanism according to claim 1 or 2, characterized in that the tow retainer (11) corresponds with respect to its shape at least to one section of the motion path of the towing elements (12a, 12b), and the length of the tow retainer (11), as seen in the direction of movement of the towing elements (12a, 12b), and the dimension of the towing elements (12a, 12b) are adjusted to each other in such a way that during the movement of the actuation unit (8) both an independent movement of the same is possible with respect to the combiner unit (10) or the combiner unit (10) with respect to the actuating shaft unit (9) and also a direct coupled movement in which the actuation unit (8) tows the combiner unit (10) or the combiner unit (10) tows the actuating shaft unit (9) as a result of the movement of the actuation unit (8).
4. An electrical switch latching mechanism (1) according to one of the claims 1 to 3, characterized in that the tow retainers (11) are arranged in the manner of a circular arc and the towing elements (12a, 12b) form a sector of a cylinder jacket and protrude into the tow retainers (11).
5. An electrical switch latching mechanism (1) according to one of the claims 1 to 4, characterized in that the combiner unit (10) is arranged between the actuation unit (8) and the actuating shaft unit (9).
6. An electrical switch latching mechanism (1) according to one of the claims 1 to 5, characterized in that the combiner unit (10), the actuation unit (8) and the actuating shaft unit (9) are rotatably arranged about a common axis (14).
7. An electrical switch latching mechanism (1) according to one of the claims 1 to 6, characterized in that the at least one tow retainer (11) is arranged as a through-opening in the combiner unit (10), and the at least one towing element (12a, 12b) of the actuation unit (8) and the actuating shaft unit (9) protrudes into the tow retainer (11) from mutually opposite sides of the combiner unit (9).
8. An electrical switch latching mechanism (1) according to one of the claims 1 to 7, characterized in that the output unit (4) of the main latching mechanism (2) is pretensioned by means of at least one main spring element (15) against a movement of the same.
9. An electrical switch latching mechanism (1) according to claim 8, characterized in that at least one main spring element (15) is arranged as an over-centre helper spring and pushes the output unit (4) to its initial or end position.
10. An electrical switch latching mechanism (1) according to one of the claims 1 to 9, characterized in that the driver shaft (3) is directly coupled to the output unit (4).
11. An electrical switch latching mechanism (1) according to one of the claims 1 to 10, characterized in that in the off position of the actuation unit (8) the tow retainer (11) enables a movement of the at least one towing element (12a) of the actuation unit (8) in only one direction.
12. An electrical switch latching mechanism (1) according to one of the claims 1 to 11, characterized in that in the off position of the actuation unit (8) the tow retainer (11) has a freewheeling section (11a) situated in the motion path of the towing element (12a) of the actuation unit (8), which freewheeling section enables a first movement of the actuation unit (8) which is independent with respect to the combiner unit (10).
13. An electrical switch latching mechanism (1) according to claim 12, characterized in that the first freewheeling section (11a) is between 35° and 45°.
14. An electrical switch latching mechanism (1) according to one of the claims 1 to 13, characterized in that in the off position of the actuation unit (8) the towing element (12b) of the actuating shaft unit (9) is arranged on a boundary wall of the tow retainer (11) which is at the rear as seen relative to a first direction of movement (50) of the towing element (12b) leading to the on position.
15. An electrical switch latching mechanism (1) according to one of the claims 1 to 14, characterized in that in the on position of the actuation unit (8) the towing element (12a) of the actuation unit (8) is arranged on a boundary wall of the tow retainer (11) which is at the front as seen relative to a second direction of movement (51) of the towing element (12a) leading to the off position.
16. An electrical switch latching mechanism (1) according to one of the claims 1 to 15, characterized in that in the on position of the actuation unit (8) the towing element (12b) of the actuating shaft unit (9) is arranged on the boundary wall of the tow retainer (11) which is at the front as seen relative to a second direction of movement (51) of the towing element (12b) leading to the off position.
17. An electrical switch latching mechanism (1) according to claim 16, characterized in that in the on position of the actuation unit (8) a second freewheeling section (11d) is provided between the towing element (12b) of the actuating shaft unit (9) and a boundary wall of the tow retainer (11) which is at the rear as seen relative to a second direction of movement (51) of the towing element (12b) leading to the off position, wherein the second freewheeling section (11d) lies preferably between 35° and 45°.

Images