EP3271929B1 - Energy accumulator for an on-load tap changer, and on-load tap changer comprising an energy accumulator - Google Patents

Description

The invention relates to an energy store for an on-load tap changer and an on-load tap changer with an energy store.

An energy store, often also referred to as an energy store, is used in an on-load tap changer with an output shaft, an input shaft and a diverter switch to convert a continuous, slow rotary movement of the output shaft, which is driven by a motor at a constant speed, into a sudden, rapid rotary movement of the input shaft that drives the diverter switch. Numerous energy stores are already known which enable the sudden rotation of the drive shaft with the aid of a storage spring. The principle is always the same: the output shaft, driven by the motor at a constant speed, tensions the storage spring to a maximum point, and after this maximum point is exceeded, the storage spring relaxes suddenly and drives the drive shaft suddenly.

DE 28 06 282 B1 . EP 0 355 814 A2 . DE 10 2005 027 524 B3 . DE 10 2005 027 527 B3 . DE 10 2010 020 130 A1 and EP 2 760 034 A1 each describe an on-load tap-changer with an energy store, which comprises a storage spring, a gear, a frame for the gear, an eccentric, a pull-up slide and a spring slide. The transmission includes an input hub and an output hub. Because of these sledges, such energy stores are also referred to as sled energy stores.

In these known on-load tap changers, the output shaft is connected to the input hub in a rotationally fixed manner. The input hub is non-rotatably connected to the eccentric. The eccentric is positively connected to the mounting slide. The storage spring is supported between the pull-up slide and the spring slide. The pull-up slide and the jump slide can move back and forth independently of one another between two end positions relative to the frame along a linear guide. The jumping sled is positively connected to the output hub.

Consequently, the eccentric forms, together with the mounting slide, a tensioning element which is designed such that it engages the tensioning element and then when the input hub is rotated, the storage element tensions, and the jump carriage forms a relaxation element which is designed such that it engages the storage element to drive the output hub and then drives the output hub when the storage element is relaxed.

DE 10 2006 008 338 B3 and DE 10 2009 034 627 B3 each describe an on-load tap-changer with an energy store, which comprises a storage spring, a gear, a frame for the gear, a drive element in the form of a gearwheel with two axially projecting stop faces and a crank with a crank pin. The transmission includes an input hub and an output hub. Because of this crank, such energy stores are also referred to as crank energy stores.

In these known on-load tap changers, the output shaft is connected to the input hub in a rotationally fixed manner. The input hub is non-rotatably connected to the drive element. The drive element and the crank can rotate back and forth relative to one another between a first end position and a second end position. The stop surfaces correspond to the crank in such a way that the first stop surface bears on a first side of the crank in the first end positions and the second stop surface bears against a second side of the crank in the second end position, these sides being opposite one another. Consequently, the drive element is positively connected to the crank in these end positions. The storage spring is pivoted with a free end on the crank pin and is pivotably supported on the frame with a fixed end. The free end can move back and forth between two end positions relative to the fixed end along a linear guide. The crank is coupled to the output hub.

Consequently, the crank, together with the drive element, forms a tensioning element which is designed such that it engages with the storage element for tensioning and then tensions the storage element when the input hub is rotated, and the crank forms a relaxation element which is designed such that it is for driving the output hub attacks the storage element and then drives the output hub when the storage element is relaxed.

Against this background, the invention proposes the subject matter of the independent claims. Advantageous further developments and embodiments of the invention are described in the dependent claims.

The invention proposes an energy store according to claim 1.

A variable translation means is here understood to mean, for example, a translation means with variable translation, that is to say that its translation depends on the angular position of the input hub or on the angular position of its input side, which is coupled to the input hub and, in particular, connected in a rotationally fixed manner. The translation means can in particular be designed in such a way that when the input hub rotates from a first angular position to a second angular position, the translation becomes larger or smaller or the sign changes or remains the same or is infinite.

The translation of the translation means is defined, for example, as ü = vE: vA, where vE is the input speed with which the input side of the translation means coupled to the input hub moves, and vA the output speed with which the output side of the translation means coupled to the storage element moves emotional. If, for example, the input side and the output side of the translation means are rotatable, then the translation can also be expressed, for example, by ü = nE: nA, where nE is the input speed of the input side, and nA is the output speed of the output side. Consequently, a large or small translation ü means a low or high output speed vA = vE: ü.

The translation means of the proposed energy store enables an oscillating pivoting movement of the output hub between its first and second angular positions, regardless of the direction of rotation of the input hub. An oscillating pivoting movement is understood here to mean that the output hub first rotates in a first direction from a predefined first angular position to a predefined second angular position when the input hub is rotated in a first direction from a predefined first angular position by a predefined differential angle, and that , then the input hub either in an opposite, second direction back to its first angular position or further in the first direction the difference angle is rotated, then the output hub rotates in an opposite, second direction from its second back to its first angular position.

• ein Spannelement, das derart ausgebildet ist, dass es zum Spannen an dem Speicherelement angreift und dann bei Drehung der Eingangsnabe das Speicherelement spannt;
• ein Entspannelement, das derart ausgebildet ist, dass es zum Antreiben der Ausgangsnabe an dem Speicherelement angreift und dann beim Entspannen des Speicherelementes die Ausgangsnabe antreibt;
  wobei
• das Getriebe derart ausgebildet ist, dass es
  • beim Entspannen und/oder Antreiben der Ausgangsnabe das Spannelement dem Entspannelement mit einer gewünschten und/oder vorgegebenen Geschwindigkeit nachfährt oder nachfahren kann; und/oder
  • beim Entspannen und/oder Antreiben der Ausgangsnabe das Entspannelement nachdrückt oder nachdrücken kann.

Each proposed energy store preferably comprises

• a tensioning element which is designed such that it engages the tensioning element for tensioning and then tensiones the storage element when the input hub rotates;
• a relaxation element which is designed such that it engages the storage element to drive the output hub and then drives the output hub when the storage element is relaxed;
  in which
• the transmission is designed such that it
  • when relaxing and / or driving the output hub, the tensioning element follows or can follow the relaxation element at a desired and / or predetermined speed; and or
  • when relaxing and / or driving the output hub, the relaxation element presses or can press.

In this case, the translation means, when relaxing and / or driving the output hub, enables the tensioning element to be traversed relative to the tensioning element at a desired and / or predetermined speed, which can in particular be greater than the speed during tensioning.

If the storage element is defective or blocked or inhibited, or if the on-load tap-changer has difficult operating conditions compared to normal operating conditions or in overload situations, the relaxation and / or driving of the output hub can take place more slowly than under normal operating conditions and even so slowly that the tensioning element catches up with the relaxation element attacks on the storage element as when clamping. In this case, the translation means enables the expansion element to be re-pressed, in that the input hub drives the output hub directly and without delay via the tensioning element and the expansion element.

The tensioning element and the relaxation element can be designed in any manner as required, for example as in the case of a slide energy store or a crank energy store.

• wenigstens eine Kurbel, die an das Speicherelement und an das Getriebe gekoppelt ist.

Each proposed energy store preferably comprises

• at least one crank that is coupled to the storage element and to the transmission is.

The crank in particular forms at least part of the tensioning element and / or at least part of the relaxation element.

The proposed energy store can be designed in any manner as required and can include, for example, at least one or no additional elastic storage element and / or at least one or no additional gear and / or at least one or no additional transmission means.

Each storage element can be designed in any manner as required, for example as a tension coil spring or compression coil spring or gas compression spring or elastomer spring.

Each translation means can be designed in any manner as required and include, for example, at least one gear with an uneven and / or adjustable translation, which is preferably a cam gear or coupling gear or stepping gear or continuously variable gear or CVT (Continuously Variable Transmission) or flow gear or gear pair of two elliptical gears is formed.

• das Getriebe derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in einer ersten Richtung aus einer vorgegebenen ersten Winkelstellung in eine vorgegebene zweite Winkelstellung das Speicherelement spannt und dabei die Ausgangsnabe steht;
• das Speicherelement derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in dieser Richtung aus der zweiten Winkelstellung in eine vorgegebene dritte Winkelstellung sich entspannt und dabei die Ausgangsnabe aus einer ersten Winkelstellung in eine zweite Winkelstellung dreht.

It is preferably provided that

• the transmission is designed such that it
  • upon rotation of the input hub in a first direction from a predetermined first angular position to a predetermined second angular position, the storage element is tensioned and the output hub is stationary;
• the storage element is designed such that it
  • when the input hub rotates in this direction from the second angular position to a predetermined third angular position, the output hub rotates from a first angular position to a second angular position.

During this rotation from the first to the second angular position, the output hub is in particular in its first angular position.

• das Getriebe derart ausgebildet ist, dass
  • bei Drehung der Eingangsnabe in dieser Richtung aus der zweiten in die dritte Winkelstellung und/oder beim Entspannen die Übersetzung des Übersetzungsmittels kleiner als beim Spannen ist.

It is preferably provided that

• the transmission is designed such that
  • when the input hub rotates in this direction from the second to the third angular position and / or when the pressure is released, the translation of the translation means is smaller than when clamping.

• das Getriebe derart ausgebildet ist, dass
  • bei Drehung der Eingangsnabe in dieser Richtung aus der ersten in die zweite Winkelstellung die Übersetzung des Übersetzungsmittels größer als ein vorgegebener Schwellenwert ist; und/oder
  • bei Drehung der Eingangsnabe in dieser Richtung aus der zweiten in die dritte Winkelstellung die Übersetzung des Übersetzungsmittels kleiner als dieser Schwellenwert oder als ein vorgegebener anderer Schwellenwert ist.

It is preferably provided that

• the transmission is designed such that
  • when the input hub rotates in this direction from the first to the second angular position, the translation of the transmission means is greater than a predetermined threshold value; and or
  • when the input hub rotates in this direction from the second to the third angular position, the translation of the transmission means is less than this threshold value or as a predetermined other threshold value.

• das Getriebe derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in dieser Richtung aus der dritten Winkelstellung in eine vorgegebene vierte Winkelstellung die Ausgangsnabe blockiert;
• und/oder das Getriebe derart ausgebildet ist, dass
  • bei dieser Drehung aus der dritten in die vierte Winkelstellung die Übersetzung des Übersetzungsmittels unendlich ist.

It is preferably provided that

• the transmission is designed such that it
  • when the input hub rotates in this direction from the third angular position into a predetermined fourth angular position, the output hub is blocked;
• and / or the transmission is designed such that
  • with this rotation from the third to the fourth angular position, the translation of the translation means is infinite.

During this rotation, the transmission blocks the output hub, in particular in its second angular position.

• das Getriebe derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in dieser Richtung aus einer vorgegebenen fünften Winkelstellung, die vor der ersten Winkelstellung liegt, in die erste Winkelstellung das Speicherelement nicht spannt und dabei die Ausgangsnabe steht.

It is preferably provided that

• the transmission is designed such that it
  • when the input hub is rotated in this direction from a predetermined fifth angular position, which lies before the first angular position, into the first angular position, the storage element is not tensioned and the output hub is stationary.

During this rotation, the output hub is in its first angular position in particular.

• das Getriebe derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in dieser Richtung aus der fünften Winkelstellung in eine vorgegebene Zwischenwinkelstellung, die zwischen der fünften und ersten Winkelstellung liegt, die Ausgangsnabe blockiert;
• und/oder das Getriebe derart ausgebildet ist, dass
  • bei dieser Drehung aus der fünften Winkelstellung in die Zwischenwinkelstellung die Übersetzung des Übersetzungsmittels unendlich ist.

It is preferably provided that

• the transmission is designed such that it
  • upon rotation of the input hub in this direction from the fifth angular position to a predetermined intermediate angular position which lies between the fifth and first angular position, the output hub is blocked;
• and / or the transmission is designed such that
  • with this rotation from the fifth angular position to the intermediate angular position, the translation of the transmission means is infinite.

During this rotation, the transmission blocks the output hub, particularly in its first angular position.

• das Getriebe derart ausgebildet ist, dass
  • bei Drehung der Eingangsnabe in dieser Richtung aus der fünften Winkelstellung oder einer vorgegebenen Zwischenwinkelstellung, die zwischen der fünften und ersten Winkelstellung liegt, in die erste Winkelstellung die Übersetzung des Übersetzungsmittels kleiner als beim Spannen ist.

It is preferably provided that

• the transmission is designed such that
  • when the input hub rotates in this direction from the fifth angular position or a predetermined intermediate angular position, which lies between the fifth and first angular position, into the first angular position, the translation of the transmission means is smaller than when clamping.

• das Getriebe und das Speicherelement derart ausgebildet sind, dass sie zusammen
  • bei Drehung der Eingangsnabe in dieser Richtung aus der zweiten Winkelstellung in die dritte Winkelstellung die Ausgangsnabe aus ihrer ersten Winkelstellung oder aus einer Zwischenwinkelstellung, die zwischen ihrer ersten und zweiten Winkelstellung liegt, in ihre zweite Winkelstellung drehen oder drehen können;
• oder das Getriebe derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in dieser Richtung aus der zweiten in die dritte Winkelstellung anstelle des Speicherelementes die Ausgangsnabe aus ihrer ersten Winkelstellung oder aus einer Zwischenwinkelstellung, die zwischen ihrer ersten und zweiten Winkelstellung liegt, in ihre zweite Winkelstellung dreht oder drehen kann.

It is preferably provided that

• the transmission and the storage element are designed such that they are together
  • upon rotation of the input hub in this direction from the second angular position to the third angular position, the output hub can rotate or rotate from its first angular position or from an intermediate angular position which lies between its first and second angular positions to its second angular position;
• or the transmission is designed such that it
  • when the input hub is rotated in this direction from the second to the third angular position, the output hub rotates or can rotate from its first angular position or from an intermediate angular position that lies between its first and second angular positions to its second angular position instead of the storage element.

• das Getriebe derart ausgebildet ist, dass es
  • bei Drehung der Eingangsnabe in dieser Richtung und zwischen der zweiten und dritten Winkelstellung verhindert, dass die Ausgangsnabe ihre zweite Winkelstellung um mehr als einen vorgegebenen Abweichungswinkel verlassen kann.

It is preferably provided that

• the transmission is designed such that it
  • when the input hub rotates in this direction and between the second and third angular positions, it prevents the output hub from leaving its second angular position by more than a predetermined deviation angle.

• das Getriebe umfasst
  • wenigstens eine Kurvenscheibe, die wenigstens eine Kurve und die Eingangsnabe umfasst;
  • wenigstens einen Abtaster, der die Kurve abtastet;
• und/oder das Getriebe umfasst
  • ein Antriebszahnrad mit einer Schwenkachse, das den Abtaster radial zur Schwenkachse versetzt trägt; und/oder
  • ein Abtriebszahnrad, das die Ausgangsnabe umfasst und an das Speicherelement gekoppelt ist; und/oder
  • eine erste, insbesondere freilaufartige Kupplung mit einem vorgegebenen ersten Winkelspiel, die zwischen das Antriebszahnrad und das Speicherelement geschaltet ist; und/oder
  • eine zweite, insbesondere freilaufartige Kupplung mit einem vorgegebenen zweiten Winkelspiel, die zwischen das Speicherelement und das Abtriebszahnrad geschaltet ist.

It is preferably provided that

• includes the transmission
  • at least one cam disk that includes at least one curve and the input hub;
  • at least one scanner that scans the curve;
• and / or includes the transmission
  • a drive gear with a pivot axis that the scanner radially to Offset pivot bearing; and or
  • an output gear that includes the output hub and is coupled to the storage element; and or
  • a first, in particular free-wheel-type clutch with a predetermined first angular play, which is connected between the drive gear and the storage element; and or
  • a second, in particular free-wheel-type clutch with a predetermined second angular play, which is connected between the storage element and the driven gear.

Both the drive gear and the driven gear can, if necessary, be replaced by another suitable gear element, for example by a chain wheel or a pulley.

• das Getriebe umfasst
  • wenigstens einen Sperrmechanismus, der an die Ausgangsnabe und insbesondere an das Abtriebszahnrad gekoppelt ist;
• der Sperrmechanismus derart ausgebildet ist, dass er
  • bei Drehung der Eingangsnabe in dieser Richtung und zwischen der zweiten und dritten Winkelstellung verhindert, dass die Ausgangsnabe ihre zweite Winkelstellung um mehr als den Abweichungswinkel und/oder in Richtung zu ihrer ersten Winkelstellung hin verlassen kann; und/oder
  • in der zweiten Winkelstellung der Ausgangsnabe verhindert, dass die Ausgangsnabe die zweite Winkelstellung in Richtung zu der ersten Winkelstellung hin verlassen kann; und/oder
  • in einer Zwischenwinkelstellung der Ausgangsnabe, die zwischen ihrer ersten und zweiten Winkelstellung liegt, verhindert, dass die Ausgangsnabe diese Zwischenwinkelstellung in Richtung zu der ersten Winkelstellung hin verlassen kann; und/oder
  • bei Drehung der Ausgangsnabe aus ihrer zweiten in ihre erste Winkelstellung verhindert, dass die Ausgangsnabe in ihrer Zwischenwinkelstellung stehen bleibt.

It is preferably provided that

• includes the transmission
  • at least one locking mechanism which is coupled to the output hub and in particular to the output gear;
• the locking mechanism is designed such that it
  • upon rotation of the input hub in this direction and between the second and third angular positions, prevents the output hub from being able to leave its second angular position by more than the deviation angle and / or in the direction of its first angular position; and or
  • in the second angular position of the output hub prevents the output hub from leaving the second angular position in the direction of the first angular position; and or
  • in an intermediate angular position of the output hub, which lies between its first and second angular positions, prevents the output hub from leaving this intermediate angular position in the direction of the first angular position; and or
  • upon rotation of the output hub from its second to its first angular position prevents the output hub from remaining in its intermediate angular position.

• das Getriebe umfasst
  • ein erstes Zahnrad oder A-Zahnrad, das mit dem Antriebszahnrad kämmt; und/oder
  • ein zweites Zahnrad oder B-Zahnrad, das insbesondere mit dem A-Zahnrad insbesondere über die erste Kupplung gekoppelt ist; und/oder
  • ein drittes Zahnrad oder C-Zahnrad, das insbesondere mit dem B-Zahnrad kämmt; und/oder
  • ein viertes Zahnrad oder D-Zahnrad, das mit dem Abtriebszahnrad kämmt und insbesondere mit dem C-Zahnrad insbesondere über die zweite Kupplung gekoppelt ist.

It is preferably provided that

• includes the transmission
  • a first gear or A gear that meshes with the drive gear; and or
  • a second gear or B gear, which is coupled in particular to the A gear, in particular via the first clutch; and or
  • a third gear or C gear that meshes with the B gear in particular; and or
  • a fourth gear or D gear, which meshes with the driven gear and in particular is coupled to the C gear, in particular via the second clutch.

If necessary, each of these gears can be replaced by another suitable gear element, for example a chain wheel or a pulley.

• wenigstens eine Kurbel, die an das Speicherelement und/oder an das C-Zahnrad gekoppelt ist.

Each proposed energy store preferably comprises

• at least one crank which is coupled to the storage element and / or to the C gear.

The crank in particular forms at least part of the tensioning element and / or at least part of the relaxation element.

• das Getriebe umfasst
  • wenigstens einen Lösemechanismus, der insbesondere an das B-Zahnrad gekoppelt ist;
• der Lösemechanismus derart ausgebildet ist, dass er
  • bei Drehung der Eingangsnabe in dieser Richtung und dann, wenn sich die Eingangsnabe in der zweiten Winkelstellung oder zwischen der zweiten und dritten Winkelstellung befindet, den Sperrmechanismus löst.

It is preferably provided that

• includes the transmission
  • at least one release mechanism, which is in particular coupled to the B gear;
• the release mechanism is designed such that it
  • upon rotation of the input hub in this direction and then when the input hub is in the second angular position or between the second and third angular positions, the locking mechanism is released.

• die Kurve derart ausgebildet ist, dass bei Drehung der Eingangsnabe in der ersten Richtung aus der fünften in die vierte Winkelstellung und bei Drehung der Eingangsnabe in einer entgegengesetzten, zweiten Richtung aus der vierten in die fünfte Winkelstellung die jeweiligen Bewegungen des Antriebszahnrades spiegelbildlich zueinander verlaufen; und/oder
• die Kurve derart ausgebildet ist, dass bei Drehung der Eingangsnabe in der ersten Richtung aus der fünften in die vierte Winkelstellung und bei Drehung der Eingangsnabe in der ersten Richtung aus der vierten Winkelstellung um denselben Differenzwinkel die jeweiligen Bewegungen des Antriebszahnrades spiegelbildlich zu zueinander verlaufen; und/oder
• die Kurve in sich geschlossen ist; und/oder
• die Kurve derart ausgebildet ist, dass der Differenzwinkel zwischen der vierten und fünften Winkelstellung 180° oder 90° oder 60° oder 45° oder einen ganzzahligen Bruchteil von 180° beträgt.

It is preferably provided that

• the curve is designed such that when the input hub rotates in the first direction from the fifth to the fourth angular position and when the input hub rotates in an opposite, second direction from the fourth to the fifth angular position, the respective movements of the drive gear run in mirror image to one another; and or
• the curve is designed such that when the input hub rotates in the first direction from the fifth to the fourth angular position and when the input hub rotates in the first direction from the fourth angular position, the respective movements of the drive gear run in mirror image to one another; and or
• the curve is closed; and or
• the curve is designed such that the difference angle between the fourth and fifth angular positions is 180 ° or 90 ° or 60 ° or 45 ° or an integer fraction of 180 °.

• einen Motor mit einer Abtriebswelle;
• einen Lastumschalter mit einer Antriebswelle;
• einen Energiespeicher, der gemäß dem ersten Aspekt ausgebildet ist;
  wobei
• die Eingangsnabe mit der Abtriebswelle drehfest verbunden ist;
• die Ausgangsnabe mit der Antriebswelle drehfest verbunden ist.

According to a second aspect, the invention proposes an on-load tap changer comprising

• an engine with an output shaft;
• a diverter switch with a drive shaft;
• an energy store, which is designed according to the first aspect;
  in which
• the input hub is rotatably connected to the output shaft;
• the output hub is rotatably connected to the drive shaft.

The proposed on-load tap changer can be designed in any manner as required and can comprise, for example, at least one or no additional motor and / or at least one or no additional diverter switch and / or at least one or no additional energy store.

Each motor can be designed in any manner as required, for example as a motor with constant or unchangeable or unregulated speed. It is preferably provided that the on-load tap-changer comprises at least one selector with a selector drive shaft which is connected to the driven shaft in a rotationally fixed manner or is the driven shaft. The selector preferably comprises at least two movable moving contacts which are connected in a rotationally fixed manner to the selector drive shaft.

The explanations and explanations for one of the aspects of the invention, in particular for individual features of this aspect, also apply analogously to the other aspects of the invention.

Embodiments of the invention are explained in more detail below by way of example with reference to the accompanying drawings. The details in the drawings are to be interpreted only as explanatory, but not restrictive. The reference numerals contained in the claims are not intended to limit the scope of the invention in any way Limit way, but only refer to the embodiments shown in the drawings.

FIG. 1

eine bevorzugte Ausführungsform eines Laststufenschalters mit einem Energiespeicher;

FIG. 2

eine erste Ansicht einer bevorzugten Ausführungsform des Energiespeichers der FIG. 1 mit einem Sperrmechanismus in einer ersten Ausführungsform;

FIG. 3

eine zweite Ansicht des Energiespeichers aus FIG. 2;

FIG. 4

eine dritte Ansicht des Energiespeichers aus FIG. 2;

FIG. 5

eine vierte Ansicht des Energiespeichers aus FIG. 2;

FIG. 6

eine fünfte Ansicht des Energiespeichers aus FIG. 2;

FIG. 7

eine Schnittansicht einer beispielhaften Ausführungsform einer ersten Kupplung für den Energiespeicher;

FIG. 8

eine Schnittansicht einer beispielhaften Ausführungsform einer zweiten Kupplung für den Energiespeicher;

FIG. 9

eine Unteransicht einer beispielhaften Ausführungsform einer Kurvenscheibe für den Energiespeicher;

FIG. 10

eine zweite Ausführungsform des Sperrmechanismus;

FIG. 11

eine dritte Ausführungsform des Sperrmechanismus.

The drawings show in

FIG. 1

a preferred embodiment of an on-load tap-changer with an energy store;

FIG. 2

a first view of a preferred embodiment of the energy storage FIG. 1 with a locking mechanism in a first embodiment;

FIG. 3

a second view of the energy storage FIG. 2 ;

FIG. 4

a third view of the energy storage FIG. 2 ;

FIG. 5

a fourth view of the energy storage FIG. 2 ;

FIG. 6

a fifth view of the energy storage FIG. 2 ;

FIG. 7

a sectional view of an exemplary embodiment of a first clutch for the energy storage;

FIG. 8th

a sectional view of an exemplary embodiment of a second clutch for the energy storage;

FIG. 9

a bottom view of an exemplary embodiment of a cam for the energy storage;

FIG. 10

a second embodiment of the locking mechanism;

FIG. 11

a third embodiment of the locking mechanism.

In FIG. 1 A preferred embodiment of an on-load tap changer 10 is shown schematically, which comprises, for example, a motor 11 with an output shaft 12, a diverter switch 13 with an input shaft 14, an energy store 15 and a selector 16. The diverter switch 13 and the selector 16 are designed in a known manner and are therefore not shown in detail. The selector 16 comprises a plurality of fixed contacts (not shown) and two movable moving contacts (not shown) and is coupled to the output shaft 12 for driving the moving contacts. The diverter switch 13 comprises a movable changeover contact unit (not shown) and is coupled to the drive shaft 14 for driving the changeover contact unit. The drive shaft 14 is coupled via the energy store 15 to the output shaft 12, which the motor 11 drives at a constant speed during a switching operation of the on-load tap changer 10.

In FIG. 2 . FIG. 3 . FIG. 4 . FIG. 5 . FIG. 6 A preferred embodiment of the energy store 15 is shown schematically in different views. The energy store 15 includes, for example, a transmission, an elastic storage element 17, a crank 18, which couples the storage element 17 to the transmission, and a frame (not shown in FIG. 3 . 4 . 5 ) with an upper and lower frame plate 19 ', 19 "as well as struts which connect the frame plates 19 to one another. The storage element 17 has a fixed end (left in FIG. 2 ) pivotally mounted on the frame plates 19 and with an opposite, movable end (right in FIG. 2 ) rotatably mounted on the crank 18.

The transmission includes, for example, a cam plate 20 (not shown in FIG FIG. 5 ) with an input hub 201 and a groove-shaped curve 202 ( FIG. 3 ) in its underside, a scanner 21 scanning curve 202 ( FIG. 3 ), a drive gear 22 with a pivot axis 221, an output gear 23 with an output hub 231 and a flywheel 232, a first and second clutch 24, 25 ( FIG. 2 . 5 . 6 ), a locking mechanism 26 in a first embodiment with a first and second pawl 261, 262 and a first and second locking lug 263, 264, an A gear 27, a B gear 28, a C gear 29, a D gear 30 and a release mechanism with a first and second release bolts 31 ', 31 ".

The input hub 201 is rotatably connected to the output shaft 12 (not shown). The output hub 231 is non-rotatably connected to the drive shaft 14 (not shown). The drive gear 22 carries the scanner 21, which is radially offset from the pivot axis 221 and projects upwards into the curve 202. Cam 20 and scanner 21 together form a cam mechanism, which represents a variable translation means, which is connected between the input hub 201 and the storage element. The A gear 27 meshes with the drive gear 23. The B gear 28 is coupled to the A gear 27 via the first clutch 24. The C gear 29 meshes with the B gear 28. The D gear 30 is coupled to the C gear 29 via the second clutch 25 and meshes with the driven gear 23. The crank 18 is connected to the C gear 29 in a rotationally fixed manner , The drive gear 22 is thus coupled to the storage element 17 via the A gear 27, the first clutch 24, the B gear 28, the C gear 29 and the crank 18. The output gear 23 is thus coupled to the storage element 17 via the D gear 30, the second clutch 25, the C gear 29 and the crank 18.

The driven gear 23 lies below the lower frame plate 19 ″ and the flywheel 232 is fastened to the underside of its toothing. Each pawl 261, 262 is pivotably mounted on the top of the flywheel 232 radially outside the toothing and has one at its radially outer free end Pawl claw for gripping the associated latching lug 263, 264 when latching in, whereas its radially inner free one The end serves as a stop for the associated release bolt 31 ', 31 "when notching. The detents 263, 264 are fastened to the underside of the lower frame plate 19" radially outside the pawls 261, 262 and each have a flat radially inward running surface and a steep radially outward extending locking surface that connects to the radially inner end of the ramp surface. The release bolts 31 ', 31 "are attached to the B gear 28 and protrude through an arcuate slot in the lower frame plate 19" down to the level of the associated pawl 261, 262. By suitable rotation of the B gear 28, each release bolt can 31 ', 31 "to be released against the inner free end of the associated pawl 261, 262 and its pawl claw swings radially inward away from the respective locking lug 263, 264 against the biasing force of an associated biasing spring which is supported on the flywheel 232.

In FIG. 7 and FIG. 8th exemplary embodiments of the first and second clutch 24, 25 are shown schematically in a cross section at right angles to the respective axis of rotation. The clutches 24, 25 are each designed in a freewheeling manner and in the manner of a claw clutch and each have a predetermined first or second angular play, which allows a correspondingly limited freewheeling in each direction of rotation.

The first clutch 24 ( FIG. 7 ) comprises a first clutch claw 24 'with a first and second stop surface 241 ( FIG. 5 . 6 ), 242 and a second clutch claw 24 "with a third and fourth stop surface 243, 244 ( FIG. 5 ). The first clutch claw 24 ′ is fastened to the underside of the A gear 27 and the second clutch claw 24 ″ to the top of the B gear 28.

The operation of the first clutch 24 is as follows: If the A gear 27 from the in FIG. 5 position shown is rotated clockwise, then the first clutch claw 24 'in the clockwise direction FIG. 7 turned. FIG. 7 shows an intermediate position in which the abutment surface 241 does not yet abut against the abutment surface 243 and thus the second clutch claw 24 "and the B gearwheel 28 remain. As soon as the A gearwheel 27 and the clutch claw 24 'have rotated so far that the abutment surface 241 abuts the stop surface 243 is present, the B gear 28 is taken via the clutch claw 24 "during further rotation and also from the in FIG. 5 shown position rotated clockwise. If the A gear 27 is then rotated counterclockwise, then the clutch claw 24 ′ is also rotated counterclockwise, the stop face 242 not yet resting against the stop face 244, and thus the second clutch claw 24 ″ and the B gear 28 stand still. As soon as the A gearwheel 27 and the clutch claw 24 'have rotated so far, namely by the first angular play, that the abutment surface 242 bears against the abutment surface 244, the B gearwheel 28 is carried along with a further rotation and also rotated counterclockwise. The operation when driving the B gear 28 is reversed accordingly.

The second clutch 25 ( FIG. 8th ) comprises a first clutch claw 25 'with a first and second stop surface 251 ( FIG. 2 ), 252 ( FIG. 2 . 5 ) and a second clutch claw 25 "with a third and fourth stop surface 253, 254. The first clutch claw 25 'is attached to the C gear 29 and the second clutch claw 25" to the top of the D gear 30. The operation of the second clutch 25 corresponds to that of the first clutch 24.

FIG. 9 is a bottom view of the cam 20 from FIG. 4 with an exemplary embodiment of curve 202. Curve 202 is self-contained and has a first section 202A with a constant first radius, a second section 202B with a constant second radius smaller than the first radius, a third section 202C, which is shown in FIG FIG. 9 connects lower ends of sections 202A, 202B and has a variable radius, and a fourth section 202D, which the in FIG. 9 connects upper ends of sections 202A, 202B and has a variable radius; the radii relate to the input hub 201. Curve 202 thus offers a variable translation.

The mode of operation of the cam mechanism forming the variable transmission means is as follows: The starting point is, for example, that in FIG. 3 to 6 Shown A basic position, in which the cam disc 20 in FIG. 9 shown position, which corresponds to a fifth angular position α5 = 0 °, scanner 21 sits in section 202A ( FIG. 3 . 4 ), Abutment surface 242 abuts abutment surface 244 and consequently abutment surface 241 is removed by the complete first angular play from abutment surface 243, abutment surface 252 abuts the abutment surface 254 and consequently abutment surface 251 is removed by the complete second angular play from abutment surface 253, the storage element 17 is relaxed and the pawl 261 is latched to latch 263 and pawl 262 is notched. The end point will be a B-basic position, in which the cam disc 20 assumes a fourth angular position α4 = 180 °, scanner 21 is located in section 202B, stop surface 241 rests against stop surface 243, and consequently stop surface 242 is removed from the stop surface 244 by the complete first angular play, Stop surface 251 abuts stop surface 253 and consequently stop surface 252 is removed from stop surface 254 by the complete second angular play is, memory element 17 is relaxed and pawl 262 latched on latch 264 and pawl 261 is released.

When the motor 11 rotates the cam 20 via the output shaft 12 and the input hub 201 from this A basic position, that is to say from the fifth angular position a5, in a first direction R1 into a first angular position α1, the scanner 21 first moves in section 202A toward section 202C and then into section 202C. Since in section 202A the radius of the curve 202 is constant, the drive gear 22 is not moved, which corresponds to an infinite transmission ratio of the cam mechanism. As a result, the transmission blocks an undesired rotation of the output gear 23 driven by the drive shaft 14. In section 202C, the radius initially decreases rapidly, which corresponds to a small transmission ratio. As a result, the drive gear 22 and A gear 27 are rotated rapidly until the first in the angular position α1 Angular play is used up, so that stop surface 241 now lies against stop surface 243 and thus stop surface 242 is now removed from the stop surface 244 by the complete first angular play. Consequently, during this rotation from angular position α5 to angular position α1, B gear 28 and the subsequent gear train are not driven, so that storage element 17 is not tensioned and output hub 231 is stationary.

When the motor 11 rotates the cam 20 from the angular position α1 further in the direction R1 to a second angular position α2, the scanner 21 moves further in section 202C to section 202B. However, since the radius now decreases more slowly than before in section 202C, this corresponds to a larger transmission ratio. As a result, the drive gear 22 and A gear 27 are rotated more slowly. The B clutch 28, C gear 29 and crank 18 are now also rotated via the first clutch 24 and thus the storage element 17 is tensioned until the storage element 17 is tensioned to its top dead center in the angular position α2 and the second angular play is used up, so that now The abutment surface 251 bears against the abutment surface 253 and the abutment surface 252 is now removed from the abutment surface 254 by the complete second angular play. Consequently, during this rotation from the angular position α1 to the angular position α2, the D gear 30 and the subsequent gear train are not driven, so that the output hub 231 is stationary. B gear 28 moves release bolts 31 'up to the stop of the first pawl 261.

When the motor 11 rotates the cam 20 from the angular position α2 further in the direction R1 to a third angular position α3, then the scanner 21 moves further in section 202C to section 202B. Consequently, release pin 31 'is countered by B gear 28 Pawl 261 pressed and this released by latch 263. At the same time, crank 18 pushes memory element 17 past top dead center, so that memory element 17 relaxes and output gear 23 comes out of the position in FIG FIG. 2 to 6 shown first angular position ω1 rotates into a second angular position ω2. In the angular position ω1, flywheel 232 lies with its in FIG. 6 right end at one in FIG. 6 front stop block, which is fastened to the underside of the lower frame plate 19 ". In angular position ω2, flywheel 232 lies with its in FIG. 6 left end at one in FIG. 6 rear stop block, which is attached to the underside of the lower frame plate 19 ", pawl 262 is latched to latch 264 and pawl 261 is unlatched.

When motor 11 rotates cam 20 from angular position α3 further in direction R1 to fourth angular position a4, which corresponds to the B basic position, scanner 21 moves into section 202B. Since the radius of curve 202 is constant in section 202B, drive gear 22 is not moved, which corresponds to an infinite transmission ratio of the cam mechanism. As a result, the transmission blocks an undesired rotation of the driven gear 23 driven by the drive shaft 14.

• sowohl bei der zuvor erläuterten Drehung der Eingangsnabe 201 in der ersten Richtung R1 aus Winkelstellung α5 in Winkelstellung α4 als auch bei einer weiteren Drehung der Eingangsnabe 201 in einer entgegengesetzten, zweiten Richtung R2 aus Winkelstellung α4 zurück in Winkelstellung a5, die jeweiligen Bewegungen des Antriebszahnrades 22 spiegelbildlich zueinander verlaufen; und
• sowohl bei der zuvor erläuterten Drehung der Eingangsnabe 201 in Richtung R1 aus Winkelstellung α5 in Winkelstellung α4 als auch bei einer Drehung der Eingangsnabe 201 weiter in Richtung R1 aus Winkelstellung α4 um denselben Differenzwinkel, der hier beispielhaft α4-α5=180° beträgt, die jeweiligen Bewegungen des Antriebszahnrades 22 spiegelbildlich zu zueinander verlaufen.

The curve 202 is designed, for example, in such a way that

• Both the rotation of the input hub 201 in the first direction R1 from the angular position α5 to the angular position α4 and the further rotation of the input hub 201 in an opposite, second direction R2 from the angular position α4 back to the angular position a5, the respective movements of the drive gear 22 run in mirror image to each other; and
• Both in the case of the previously explained rotation of the input hub 201 in the direction R1 from the angular position α5 in the angular position α4 and also in the case of a rotation of the input hub 201 further in the direction R1 from the angular position α4 by the same difference angle, which in this example is α4-α5 = 180 °, the respective Movements of the drive gear 22 are mirror images of each other.

In the normal case, the storage element 17 relaxes so quickly and with such a force that the C gear 29 rotates so fast that it rotates the B gear 28 faster than the drive gear 22 and the A gear 27. As a result, the abutment surface 241 is removed from stop surface 243, so that clutch 24 runs freely again. In order that in the event that the storage element 17 cannot rotate the driven gear 23 quickly enough, the motor 11 can press the driven gear 23 as soon as possible, the radius now decreases again faster in section 202C, which means a smaller transmission ratio and faster Rotation of drive gear 22 and Output gear 23 means. Consequently, in this case, the gearbox can turn the output gear 23 from the angular position ω1 or from an intermediate angular position, which lies between the angular position ω1 and the angular position ω2, to the angular position ω2 either together with the storage element 17 or even instead of the storage element 17.

In FIG. 10 A second embodiment of the locking mechanism 26 is shown schematically. This embodiment is similar to the first embodiment, so that the differences are explained in more detail below. Locking lug 264 is designed analogously to locking lug 263 and is not shown.

In this embodiment, the first latching lug 263 has an intermediate latching surface 32 between its latching surface and its opposite end on its contact surface, which the pawl 261 engages with its pawl claw when the output gear 23 reaches a corresponding intermediate angular position when the angular position ω1 is rotated into the angular position ω2 lies between these angular positions ω1, ω2. Consequently, the locking mechanism 26 prevents the driven gear 23 from being able to leave this intermediate angular position in the direction of its first angular position ω1.

In this embodiment, the locking mechanism 26 comprises a first spring plate 265 assigned to the latching lug 263, a second spring plate (not shown) assigned to the latching lug 264 and two guide pins 266, 267 assigned to the pawls 261, 262. The first spring plate 265 has a fixed end ( left in FIG. 10 ) attached radially within its locking lug 263 to the underside of the lower frame plate 19 "and presses with its other free end (right in FIG. 10 ) radially outwards against the connecting edge between the contact surface and the locking surface. The fixed end lies in the area of the intermediate latching surface 32. Each guide pin 266, 267 is fastened on the top of the pawl claw of its associated pawl 261, 262. When the pawl 261 is latched, the guide pin 266 in FIG. 10 from left to right into the space between spring plate 265 and detent 263 until the driven gear 23 in FIG. 10 has reached the second angular position shown ω2, in which the pawl 261 is latched and the guide pin 266 has left the space. When notching, the guide pin 266 is moved radially inward past the free end of the spring plate 265 and slides along the output gear 23 further in the direction of the first angular position ω1 along the side of the spring plate 265 facing away from the detent 263 in FIG. 10 from right to left and prevents the pawl 261 with its pawl claw from gripping the intermediate latching surface 32. As a result, the locking mechanism prevents 26 when the driven gear 23 rotates from the angular position ω2 to the angular position ω1, so that the driven gear 23 can stand or get caught or get stuck in this intermediate angular position.

In FIG. 11 A third embodiment of the locking mechanism 26 is shown schematically. This embodiment is similar to the second embodiment, so that the differences are explained in more detail below. Locking lug 264 is designed analogously to locking lug 263 and is not shown.

In this embodiment, the locking mechanism 26 instead of the spring plates 265, 266 comprises a first cover part 268 assigned to the locking lug 263 and a second cover part assigned to the locking lug 264 (not shown). In comparison to the second embodiment, the intermediate latching surface 32 is closer to the latching surface and cannot be seen since it is covered by the cover part 268. The cover part 268 is supported by a biasing spring, which is supported on the radially outer surface of the latch 263, with its in FIG. 11 right end biased radially outward against the connecting edge between the ramp surface and the locking surface. The cover member 268 lies with its other one, in FIG. 11 left end at a distance from the latch 263. When the pawl 261 is latched, the guide pin 266 in FIG. 11 from left to right into the space between cover 268 and locking lug 263 until the output gear 23 in FIG. 11 has reached the second angular position shown ω2, in which the pawl 261 is latched and the guide pin 266 has left the space. When notching, the guide pin 266 is moved radially inward past the free end of the cover part 268 and slides along the output gear 23 in the direction of the first angular position ω1 on the side of the cover part 268 facing away from the detent 263 in FIG FIG. 11 from right to left and prevents the pawl 261 with its pawl claw from gripping the intermediate latching surface 32. Consequently, when the driven gear 23 rotates from the angular position ω2 into the angular position ω1, the locking mechanism 26 prevents the driven gear 23 from standing or getting caught or stuck in this intermediate angular position.

REFERENCE NUMBERS

10

OLTC

11

engine

12

output shaft

13

diverter switch

14

drive shaft

15

energy storage

16

voter

17

elastic storage element

18

crank

19 '/ 19 "

upper / lower frame plate

20

cam

201/202

Input hub / curve of 20

202A / B / C / D

first / second / third / fourth section of 202

21

sampler

22

drive gear

221

Swivel axis from 22

23

output gear

231/232

Output hub / flywheel from 23

24

first clutch

24 '/ 24'

first / second clutch claw of 24

241/242

first / second stop surface of 24

243/244

third / fourth stop surface of 24

25

second clutch

25 '/ 25'

first / second clutch claw of 25

251/252

first / second stop surface of 25

253/254

third / fourth stop surface of 25

26

locking mechanism

261/262

first / second jack of 26

263/264

first / second latch from 26

265

first spring plate from 26

266/267

first / second guide pin of 26

27

A gear

28

B Gear

29

C-Gear

30

D-gear

31 '/ 31'

first / second release bolts

32

Intermediate rest area of 263, 264

R1 / R2

first / second direction of rotation of 20

α1 ... α5

Angular positions of 20 and 201

ω1, ω2

Angular positions of 23 and 231

Claims (13)

1. An energy accumulator (15) for an on-load tap changer (10) that comprises a motor (11) with an output shaft (12) and a load diverter switch (13) with an input shaft (14), the energy accumulator (15) comprising

   - an elastic storage element (17);

   - a gear that is coupled to the storage element (17) and comprises

   • an input hub (201) that can be non-rotatably connected to the output shaft (12);

   • an output hub (231) that can be non-rotatably connected to the input shaft (14); and

   • a variable transmission means (20, 21) that is interposed between the input hub (201) and the storage element (17); characterised by

   • a first coupling (24) with a specified first angular backlash, which first coupling (24) is interposed between the input hub (201) and the storage element (17);

   • a second coupling (25) with a specified second angular backlash, which second coupling (25) is interposed between the storage element (17) and the output hub (231).
2. The energy accumulator (15) according to one of the previous claims, comprising

   - a tensioning element (18) that is formed such that it engages at the storage element (17) for tensioning and then tensions the storage element (17) upon rotation of the input hub (201);

   - a relaxing element (18) that is formed such that it engages at the storage element (17) for driving the output hub (231) and then drives the output hub (231) upon relaxation of the storage element (17);
   wherein

   - the gear is formed such that it

   • follows up the tensioning element (18) to the relaxing element (18) at a specified velocity upon relaxation; and/or

   • re-presses the relaxing element (18) upon relaxation.
3. The energy accumulator (15) according to one of the previous claims, wherein

   - the gear is formed such that it

   • tensions the storage element (17) upon rotation of the input hub (201) in a first direction (R1) from a specified first angular position into a specified second angular position, and the output hub (231) meanwhile stands still;

   - the storage element (17) is formed such that it

   • relaxes upon rotation of the input hub (201) in said direction (R1) from the second angular position into a specified third angular position, and the output hub (231) meanwhile rotates from a first angular position into a second angular position.
4. The energy accumulator (15) according to claim 3, wherein

   - the gear is formed such that

   • the transmission of the transmission means (20, 21) upon rotation of the input hub (201) in said direction (R1) from the second into the third angular position is smaller than during tensioning.
5. The energy accumulator (15) according to claim 3, wherein

   - the gear is formed such that

   • the transmission of the transmission means (20, 21) upon rotation of the input hub (201) in said direction (R1) from the first into the second angular position is greater than a specified threshold value;

   • the transmission of the transmission means (20, 21) upon rotation of the input hub (201) in said direction (R1) from the second into the third angular position is smaller than the threshold value.
6. The energy accumulator (15) according to claim 3, wherein

   - the gear is formed such that it

   • blocks the output hub upon rotation of the input hub (201) in said direction (R1) from the third angular position into a specified fourth angular position.
7. The energy accumulator (15) according to claim 6, wherein

   - the gear is formed such that it

   • does not tension the storage element (17) upon rotation of the input hub (201) in said direction (R1) from a specified fifth angular position, which is located before the first angular position, into the first angular position, and the output hub meanwhile stands still.
8. The energy accumulator (15) according to claim 3, wherein

   - the gear and the storage element (17) are formed such that together they

   • rotate or can rotate the output hub (231) from its first angular position or from an intermediate angular position, which is located between its first and second angular position, into its second angular position upon rotation of the input hub (201) in said direction (R1) from the second angular position into the third angular position;

   - and/or the gear is formed such that

   • instead of the storage element (17), the gear rotates or can rotate the output hub from its first angular position or from an intermediate angular position, which is located between its first and second angular position, into its second angular position upon rotation of the input hub (201) in said direction (R1) from the second into the third angular position.
9. The energy accumulator (15) according to claim 3, wherein

   - the gear is formed such that it

   • prevents the output hub (231) from being able to depart from its second angular position by more than a specified deviation angle upon rotation of the input hub (201) in said direction (R1) and between the second and third angular position.
10. The energy accumulator (15) according to claim 3, wherein

    - the gear comprises

    • a locking mechanism (26) that is coupled to the output hub (231);

    - the locking mechanism (26) is formed such that it

    • prevents the output hub (231) from being able to depart from its second angular position by more than the deviation angle and/or toward its first angular position upon rotation of the input hub (201) in said direction (R1) and between the second and third angular position;

    • prevents the output hub (231) from being able to depart from its second angular position toward its first angular position when the output hub (231) is in the second angular position;

    • prevents the output hub (231) from being able to depart from an intermediate angular position toward its first angular position when the output hub (231) is in said intermediate position, which is located between its first and second angular position;

    • prevents the output hub (231) from remaining in its intermediate angular position upon rotation of the output hub (231) from its second into its first angular position.
11. The energy accumulator (15) according to claim 3, wherein

    - the gear comprises

    • a release mechanism ;

    - the release mechanism is formed such that it

    • releases the locking mechanism (26) upon rotation of the input hub (201) in said direction (R1) and in the second angular position or between the second and third angular position.
12. The energy accumulator (15) according to claim 7, wherein

    - the gear comprises

    • a cam disk (20) that comprises a cam (202) and the input hub (201);

    • a cam follower (21) that follows the cam (202);

    - the cam (202) is formed such that each of the particular movements of the cam follower (21) run mirror-invertedly to each other upon rotation of the input hub (201) in the first direction (R1) from the fifth into the fourth angular position and upon rotation of the input hub (201) in an opposite, second direction (R2) from the fourth into the fifth angular position; and/or

    - the cam (202) is formed such that each of the particular movements of the cam follower (21) run mirror-invertedly to each other upon rotation of the input hub (201) in the first direction (R1) by a differential angle from the fifth into the fourth angular position and upon rotation of the input hub (201) in the first direction (R1) by the same differential angle from the fourth angular position; and/or

    - the cam (202) is in itself closed; and/or

    - the cam (202) is formed such that the differential angle between the fourth and fifth angular position is 180° or 90° or 60° or 45° or a whole-number fraction of 180°.
13. An on-load tap changer (10) comprising

    - a motor (11) with an output shaft (12);

    - a load diverter switch (13) with an input shaft (14);

    - an energy accumulator (15) that is formed according to one of the previous claims;
    wherein

    - the input hub (201) is non-rotatably connected to the output shaft (12);

    - the output hub (231) is non-rotatably connected to the input shaft (14).

Images