DE102024000010A1 - Electromagnetic spring-loaded brake with release - Google Patents

Abstract

A release mechanism for electromagnetically opening brake calipers (BR) in floating caliper design for engagement with a brake disc (S) is proposed.
The release mechanism is realized by release rings (12, 13, 14, 15) made of elastomeric or metallic materials, which are arranged in concentric recesses (1.2, 2.2, 9.2) in the area between the guide elements (9) and the coil carrier (1) or the armature disk (2) of the brake caliper (BR).

Description

In industrial drive technology, electromagnetically released spring-loaded brakes have become established in the field of braking systems used to slow down and hold the corresponding drives.

Electromagnetic spring-loaded brakes in the form of so-called brake calipers, which interact with large brake discs, are used particularly for drives with high torques.

In addition to being able to handle high torques, one advantage of such brake calipers is their modular concept.

This means that, depending on the required braking torque, one or more brake calipers can act on a brake disc.

The majority of these brake calipers are designed in the so-called floating caliper design, which means that the complete brake caliper, consisting of a coil carrier with armature disc and counter plate, is mounted so that it can move in a direction parallel to the axis of rotation of the brake disc.

The brake disc is mounted in such a way that it cannot move parallel to its axis of rotation.

When the brake disc is braked, it is clamped and braked by the force of spring elements between an armature disc equipped with friction linings and a counter plate also equipped with friction linings.

To open the brake caliper, the magnetic coil located in the coil carrier is supplied with electrical voltage, whereby the armature disc is attracted by the coil carrier against the force of the spring elements and the brake disc is released.

To ensure that there is no contact between the friction linings on the armature disc and the counter plate with the brake disc when the brake is released, so-called release mechanisms are used in brake calipers.

From the DE10330306A1 The applicant is aware of a friction-locking release mechanism.

This system presents a system of levers whose ends are attached to the armature disk and the coil carrier via elastic tongues. In a preferred embodiment, the axes of rotation of the levers are formed by contact points between stationary bolts and parallel sections of the levers equipped with friction linings.

As a result, after the brake caliper is closed and then opened, uniform air gaps are created between the brake disc and the friction linings of the armature disc and the counter plate.

The system presented is also able to ensure very uniform air gaps between the brake disc and the friction linings of the brake caliper, even when the friction linings are worn.

The disadvantage of the system presented here is the great technical effort required to achieve the desired functionality.

Especially for applications with vertical installation of the drive and thus vertical position of the rotation axis of the brake disc as well as vertical mobility of the floating caliper, the DE102016015242A1 known to the applicant.

According to the teaching of this patent application, the release effect is achieved by direct stops within the brake caliper, which must also be adjustable within certain limits for optimal adjustment of the desired air gap.

The main disadvantage of this system is the high adjustment effort for the stops, which often has to be done at the place where the brake is used, for example on a construction site.

The object of the present invention is therefore to provide a simple and cost-effective release mechanism for a brake caliper, which ensures a sufficient release movement over the entire service life of the brake caliper and which requires no or only very little adjustment effort.

For this purpose, it is proposed to arrange at least one annular clearance element in the area between the preferably cylindrical guide elements of the brake calliper and the complementary openings, preferably cylindrical bores of the coil carrier and/or the armature disk.

Alternatively, the guide elements and the openings of the coil carrier and/or armature disk can also have other prismatic cross-sections on which can be designed as a polygon or a polygon.

The release elements are arranged in a circumferential radial recess of the coil carrier and/or the armature disk and/or the guide element, whereby basically three variants for the geometric design of the recess within the brake are possible.

In a first variant, the recess is delimited radially by a circumferential surface and axially on a first side by an annular side surface of the corresponding component, i.e. the armature disk or the coil carrier itself.

On a second side, the recess is limited by a side surface of the adjacent component, i.e. a side surface of the armature disk or the coil carrier.

After installation, the release elements do not have to be in permanent spring contact with the guide element and the peripheral surface of the recess.

In the described first variant of the recess, it is sufficient if the permanent spring contact only exists when the armature disk is in contact with the coil carrier when the brake calliper is open and thereby clamps the release element axially between the two components.

The at least one release element can be designed as an elastomer or pressure-elastic plastic ring with a preferably round, oval, polygonal or polygonal cross-section, here preferably a rectangular cross-section, or can have a cross-section corresponding to or similar to a commercially available quad ring.

Furthermore, the release element can be formed from a metallic ring with one of the aforementioned cross-sections, which has the required elasticity in the radial and/or axial direction due to its polygonal shape over the circumference.

Due to the described design of the components, it is sufficient to simply slide the brake caliper onto the guide elements during installation and connect the solenoid coil to the power supply.

When the brake caliper is closed, the friction linings of the armature disc and the friction linings of the counter plate are in contact with the brake disc and thus produce the desired braking effect.

At the latest when the brake calliper is opened for the first time by energizing the magnetic coil, the release element is slightly clamped between the said parts after a first partial movement of the coil carrier and the armature disk, thus creating a frictional contact between the release element and the guide element on the one hand and between the release element and the circumferential surface of the coil carrier or the armature disk on the other.

During a second partial movement between the coil carrier and armature disk until they touch each other, the release element is further preloaded axially from both sides by the coil carrier and the armature disk by the same amount, each corresponding to approximately half of the second partial movement. This ultimately generates a release movement between the friction linings of the armature disk and the counterplate, as well as the brake disk. When the brake caliper is open, this creates an approximately equal air gap on both sides of the brake disk, enabling friction- and wear-free operation of the brake disk. Furthermore, the release movement reliably prevents annoying noise and unwanted energy losses.

In a second variant, the recess is delimited radially by a circumferential surface and axially on a first and a second side by an annular side surface of the corresponding component, i.e. the armature disk or the coil carrier itself, and thus forms a circumferential radial groove closed on three sides in every operating state of the brake caliper.

In the second variant, the release elements must be in permanent resilient contact with the guide element and the peripheral surface of the recess after their installation.

Due to the described design of the components according to the second variant, it is sufficient to simply push the brake caliper onto the guide elements during installation and to connect the magnetic coil to the power supply.

However, when sliding the brake caliper onto the guide elements, care should be taken to ensure that the recess for the release elements is located in the coil carrier or in the armature disc.

When placing the recess in the spool holder, the brake should be pushed onto the guide elements in such a way that the spool holder moves away from the brake disc at least shortly before reaching its end position.

When placing the recess in the armature disc, the brake should be pushed onto the guide elements in such a way that the armature disc moves towards the brake disc at least shortly before reaching its final position.

If these assembly directions cannot be ensured in practice, appropriate one-time adjustment work is required after the brake caliper has been pushed onto the guide elements.

During these adjustments, for example, the guide elements in a brake frame can be moved axially in one direction and then fixed until the system is ready for use.

By correctly assembling according to one of the suggested procedures or after a corresponding adjustment, the release element is preloaded in a direction parallel to the axis of rotation when the brake is closed, so that when the brake is opened, the brake caliper moves, which moves both the armature disk and the counter friction surface connected to the coil carrier away from the brake disk by the same distance.

This enables the desired friction- and wear-free running of the brake disc without disturbing noise and without unwanted energy losses.

In a third variant, the recess is introduced as a radial recess into at least one of the guide elements, wherein the recess is delimited radially by a circumferential surface and axially on a first and a second side by an annular side surface of the guide element and thus forms a circumferential radial groove closed on three sides in every operating state of the brake calliper.

In the third variant, the release elements must be in permanent resilient contact with the circumferential surface of the recess of the guide element and with the circumferential surface of the armature disk or coil carrier after their installation.

Due to the described design of the components, it is sufficient to simply slide the brake caliper onto the guide elements during installation and connect the solenoid coil to the power supply.

However, when sliding the brake caliper onto the guide elements, care should be taken to ensure that the recess on the guide elements is located in the area of the coil carrier or in the area of the armature disk.

If the recess is placed in the area of the spool holder, the brake should be pushed onto the guide elements in such a way that the spool holder moves away from the brake disc at least shortly before reaching its end position.

If the recess is placed in the area of the armature disc, the brake should be pushed onto the guide elements in such a way that the armature disc moves towards the brake disc at least shortly before reaching its final position.

If these assembly directions cannot be ensured in practice, appropriate one-time adjustment work is required after sliding the brake caliper onto the guide elements.

By correctly assembling according to one of the suggested procedures or after an appropriate adjustment, the release elements are preloaded in a direction parallel to the axis of rotation when the brake is closed, so that when the brake is opened, the brake caliper moves, which moves both the armature disk and the counter friction surface connected to the coil carrier away from the brake disk by the same distance.

This enables the desired friction- and wear-free running of the brake disc without disturbing noise and without unwanted energy losses.

Because of the very low frictional forces between the guide elements and the release elements in relation to the masses moved by the brake calliper and the braking forces generated, the movement of the brake calliper is only slightly hindered when the brake is applied.

This means that the full desired braking effect can always be achieved on both braking surfaces compared to the brake disc.

For special operating conditions such as vertical installation or high moving masses, the release system can be equipped with several release elements arranged axially one behind the other, preferably in a ring shape, or release elements with larger cross sections and/or higher axial and radial rigidity can be used.

With appropriate design and selection of optimal materials and surfaces, the presented release system, despite its simplicity and freedom from maintenance, achieves a long service life, which usually exceeds the service life of the friction linings of the brake caliper.

Further features of the release mechanism according to the invention for a brake caliper emerge from the following description of the embodiments and from the patent claims.

• 1 die perspektivische Darstellung einer erfindungsgemäßen Bremszange in Schwimmsattelbauweise, angebaut an eine Bremsscheibe.
• 2 eine Vorderansicht der erfindungsgemäßen Bremszange mit Bremsscheibe und einen Schnittverlauf X - X.
• 3 eine Schnittansicht der geschlossenen Bremszange gemäß Schnittverlauf X - X aus 2.
• 3 Detail A die Detailansicht eines lose in einer Ausnehmung der Ankerscheibe liegenden ersten Freistellelements in Form eines O-Rings und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier maximal ist.
• 3 Detail B die Detailansicht eines zweiten und eines dritten Luftspalts, die hier „Null“ sind.
• 4 eine Schnittansicht der geöffneten Bremszange entsprechend Schnittverlauf X - X aus 2
• 4 Detail C die Detailansicht des in der Ausnehmung der Ankerscheibe eingespannten ersten Freistellelements in Form eines O-Rings und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier „Null“ ist.
• 4 Detail D die Detailansicht eines zweiten und dritten Luftspalts, die hier gleich groß sind und ihre maximale Breite aufweisen.
• 5 eine Schnittansicht der geschlossenen Bremszange gemäß Schnittverlauf X - X aus 2.
• 5 Detail E die Detailansicht eines lose in einer Ausnehmung des Spulenträgers liegenden zweiten Freistellelements in Form eines Quad-Rings und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier maximal ist.
• 5 Detail F die Detailansicht eines zweiten und dritten Luftspalts, die hier „Null“ sind.
• 6 eine Schnittansicht der geöffneten Bremszange entsprechend Schnittverlauf X - X aus 2
• 6 Detail G die Detailansicht des in der Ausnehmung des Spulenträgers eingespannten zweiten Freistellelements in Form eines Quad-Rings und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier „Null“ ist.
• 6 Detail H die Detailansicht eines zweiten und dritten Luftspalts, die hier gleich groß sind und ihre maximale Breite aufweisen.
• 7 eine Schnittansicht der geöffneten Bremszange entsprechend Schnittverlauf X - X aus 2
• 7 Detail J die Detailansicht eines in der Ausnehmung der Ankerscheibe liegenden dritten Freistellelements in Form eines VierkantRings und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier „Null“ ist.
• 7 Detail K die Detailansicht eines zweiten und dritten Luftspalts, die hier gleich groß sind und ihre maximale Breite aufweisen.
• 7 Detail L die Detailansicht des in der Ausnehmung der Ankerscheibe liegenden dritten Freistellelements in Form eines VierkantRings bei geschlossener Bremszange und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier maximal ist.
• 8 eine Schnittansicht der geöffneten Bremszange entsprechend Schnittverlauf X - X aus 2
• 8 Detail M die Detailansicht eines in der Ausnehmung des Spulenträgers liegenden vierten Freistellelements in Form eines Metall-Rings mit rundem Querschnitt und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier „Null“ ist.
• 8 Detail N die Detailansicht eines zweiten und dritten Luftspalts, die hier gleich groß sind und ihre maximale Breite aufweisen.
• 8 Detail O die Detailansicht des in der Ausnehmung des Spulenträgers liegenden vierten Freistellelements in Form eines Metall-Rings mit rundem Querschnitt bei geschlossener Bremszange und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier maximal ist.
• 9 eine Schnittansicht der geöffneten Bremszange entsprechend Schnittverlauf X - X aus 2
• 9 Detail P die Detailansicht des in einer Ausnehmung des Führungselements liegenden vierten Freistellelements in Form eines Metall-Rings mit rundem Querschnitt und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier „Null“ ist.
• 9 Detail Q die Detailansicht eines zweiten und dritten Luftspalts, die hier gleich groß sind und ihre maximale Breite aufweisen.
• 9 Detail R die Detailansicht des in der Ausnehmung des Führungselements liegenden vierten Freistellelements in Form eines Metall-Rings mit rundem Querschnitt bei geschlossener Bremszange und einen ersten Luftspalt zwischen dem Spulenträger und der Ankerscheibe, der hier maximal ist.
• 10 A eine Vorderansicht des vierten Freistellelements in Form eines Metall-Rings mit rundem Querschnitt, wobei das Freistellelement über den Umfang eine polygonale Kontur in Form einer Ellipse aufweist.
• 10 B eine Vorderansicht des vierten Freistellelements in Form eines Metall-Rings mit rundem Querschnitt, wobei das Freistellelement über den Umfang eine polygonale Kontur in Form eines Sechseck-Polygons aufweist.

They show:

• 1 the perspective view of a brake caliper according to the invention in floating caliper design, mounted on a brake disc.
• 2 a front view of the brake caliper according to the invention with brake disc and a section X - X.
• 3 a sectional view of the closed brake caliper according to section line X - X from 2 .
• 3 Detail A shows the detailed view of a first release element in the form of an O-ring lying loosely in a recess of the armature disk and a first air gap between the coil carrier and the armature disk, which is at its maximum here.
• 3 Detail B shows the detailed view of a second and a third air gap, which are “zero” here.
• 4 a sectional view of the opened brake caliper according to section line X - X 2
• 4 Detail C shows the detailed view of the first release element in the form of an O-ring clamped in the recess of the armature disk and a first air gap between the coil carrier and the armature disk, which is “zero” here.
• 4 Detail D shows the detailed view of a second and third air gap, which are the same size here and show their maximum width.
• 5 a sectional view of the closed brake calliper according to section line X - X from 2 .
• 5 Detail E shows a detailed view of a second release element in the form of a quad ring lying loosely in a recess of the coil carrier and a first air gap between the coil carrier and the armature disk, which is at its maximum here.
• 5 Detail F shows the detailed view of a second and third air gap, which are “zero” here.
• 6 a sectional view of the opened brake caliper according to section line X - X 2
• 6 Detail G shows the detailed view of the second release element in the form of a quad ring clamped in the recess of the coil carrier and a first air gap between the coil carrier and the armature disk, which is “zero” here.
• 6 Detail H shows the detailed view of a second and third air gap, which are the same size here and show their maximum width.
• 7 a sectional view of the opened brake caliper according to section line X - X 2
• 7 Detail J shows the detailed view of a third release element in the form of a square ring located in the recess of the armature disk and a first air gap between the coil carrier and the armature disk, which is “zero” here.
• 7 Detail K shows the detailed view of a second and third air gap, which are the same size here and show their maximum width.
• 7 Detail L shows the detailed view of the third release element in the form of a square ring located in the recess of the armature disk with the brake caliper closed and a first air gap between the coil carrier and the armature disk, which is at its maximum here.
• 8 a sectional view of the opened brake caliper according to section line X - X 2
• 8 Detail M shows the detailed view of a fourth release element in the recess of the coil carrier in the form of a metal ring with a round cross-section and a first air gap between the coil carrier and the armature disk, which is “zero” here.
• 8 Detail N shows the detailed view of a second and third air gap, which are the same size here and show their maximum width.
• 8 Detail O the detailed view of the fourth release element in the recess of the coil carrier in the form of a metal ring with a round cross-section with the brake calliper closed and a first air gap between the coil carrier and the armature disk, which is maximum here.
• 9 a sectional view of the opened brake caliper according to section line X - X 2
• 9 Detail P shows the detailed view of the fourth release element in the form of a metal ring with a round cross-section, located in a recess of the guide element, and a first air gap between the coil carrier and the armature disk, which is “zero” here.
• 9 Detail Q shows the detailed view of a second and third air gap, which are the same size here and show their maximum width.
• 9 Detail R shows the detailed view of the fourth release element in the recess of the guide element in the form of a metal ring with a round cross-section when the brake caliper is closed and a first air gap between the coil carrier and the armature disk, which is at its maximum here.
• 10 A a front view of the fourth clipping element in the form of a metal ring with a round cross-section, wherein the clipping element has a polygonal contour in the form of an ellipse over the circumference.
• 10 B a front view of the fourth clipping element in the form of a metal ring with a round cross-section, wherein the clipping element has a polygonal contour in the form of a hexagonal polygon over the circumference.

Out of 1 the basic structure of the brake caliper (BR) according to the invention, its attachment to a stationary machine wall and its assignment to a brake disc (S) are shown.

The brake caliper (BR) essentially consists of a coil carrier (1) and a counterplate (3) connected to the coil carrier (1) via spacer bushings (4) and second fastening elements (5). It is also conceivable to construct the coil carrier (1) and the counterplate (3) as a single piece.

An armature disk (2) which is movable parallel to the rotational axis (R) of the brake disk (S) is assigned to the coil carrier (1), which armature disk is displaced towards the brake disk (S) via spring elements (6) (not shown) located in bores of the coil carrier (1).

Furthermore, the brake caliper (BR) has a brake frame (7) which is connected to a stationary machine wall (not shown) via first fastening elements (8).

Guide elements (9) are fixed in openings in the brake frame (7), on which the coil carrier (1), the armature disk (2) and the counter plate (3) are mounted so as to be displaceable parallel to the axis of rotation (R) of the brake disk (S).

At the 1 In the advantageous embodiment described, the brake frame (7) is arranged approximately in the same plane as the brake disc (S) and radially outside the same.

The guide elements (9) can advantageously protrude beyond the side surfaces of the brake frame (7) on both sides. This allows the components arranged one behind the other in the direction of the rotation axis (R) to be arranged in the following advantageous sequence: coil carrier (1) - armature disk (2) - brake frame (7) with brake disk (S) - counterplate (3).

All components that experience an axial movement parallel to the rotation axis (R) relative to the brake frame (7) and the guide elements (9) can be equipped with suitable bearing elements in the form of plain bearings or rolling bearings in contact areas with the guide elements (9).

Within the coil carrier (1) there is an electromagnetic coil (1.1), not shown, by the energization of which the armature disk (2) is attracted against the force of the spring elements (6) towards the coil carrier (1), whereby the brake calliper (BR) opens.

In the event of a failure of the electrical power supply, the brake calliper (BR) can be manually released, i.e. opened, in an emergency by operating the illustrated manual release lever (10) using a mechanism not described in detail here.

The switching state of the brake caliper (BR), i.e. whether the brake caliper is in an open or closed state, is monitored by detecting the relative position of the coil carrier (1) and armature disk (2) via one or more switches (13).

2 shows a front view of the brake caliper (BR) with associated brake disc (S).

The brake frame (7) is connected to a stationary machine wall (not shown) via first fastening elements (8).

The coil carrier (1), the armature disc (2) and the counter plate (3) connected to the coil carrier (1) by means of spacer bushes (4) and second fastening elements (5) are mounted on the guide elements (9) of the brake frame (7) so as to be displaceable parallel to the axis of rotation (R) of the brake disc (S).

Furthermore, a section X - X is shown, which intersects one of the guide elements (9) centrally and which forms the basis of the following illustrations in 3 until 9 represents.

In 3 is a side view of the brake calliper (BR) including the associated brake disc (S) as a sectional view according to section line X - X from 2 shown in the braked state.

The central element of the brake calliper (BR) is the brake frame (7), which is connected via not shown first connecting elements (8) are connected to a stationary machine wall, not shown.

Guide elements (9) are fixed in openings in the brake frame (7), on which the coil carrier (1), the counter plate (3) connected to the coil carrier (1) and the armature disk (2) are mounted on guide bushes (9.1) so as to be displaceable axially parallel to the guide axis (F) of the guide pin (9) and to the rotation axis (R) of the brake disk (S).

In the recesses of the coil carrier (1) which are open towards the armature disk (2), there are spring elements (6) which apply force to the armature disk (2) towards the brake disk (S), the brake disk (S) being mounted so as to be rotatable about the axis of rotation (R) relative to the stationary machine wall.

The brake caliper (BR) in 3 is shown in the braked state, with the brake disc (S) clamped between the friction linings (2.1) of the armature disc (2) and the friction linings (3.1) of the counterplate (3) by the force of the spring elements (6). According to detail B, the second air gap (L2) and the third air gap (L3) are zero.

At the same time, the first air gap (L1) shown in detail A between the coil carrier (1) and the armature disk (2) reaches its maximum value.

Detail A also shows a first release element in the form of an O-ring (12) concentric with the guide axis (F), which is located in a circumferential armature recess (2.2) of the armature disk (2) and can, but does not have to, be in contact with the circumferential surface (9.3) of the guide element (9) and/or the circumferential surface (2.3) of the armature recess (2.2).

In the axial direction parallel to the guide axis (F), the O-ring (12) has no preload. The release element can be formed as a closed, circumferential O-ring (12) or from individual ring segments.

The brake caliper (BR) in 4 is shown in the unbraked, i.e. open, state, ie the armature disk (2) is pulled towards the coil carrier (1) by the energized magnetic coil (1.1) against the force of the spring elements (6) and the friction linings (2.1, 3.1) of the armature disk (2) and counter plate (3) are not in contact with the brake disk (S), which can therefore rotate freely around the rotation axis (R).

According to detail D, the second air gap (L2) and the third air gap (L3) between the friction linings (2.1, 3.1) and the brake disc (S) assume their respective maximum values, which are ideally equal when the release mechanism is functioning optimally.

Accordingly, when the brake caliper (BR) is open, the first air gap (L1) between the coil carrier (1) and the armature disk (2) assumes its minimum value, which has the value "zero" in the illustration in detail C. The O-ring (12), also shown in detail C, is axially clamped between the side surface (2.4) of the armature recess (2.2) and the side surface (1.4) of the coil carrier (1) when the brake caliper (BR) is open and is therefore in radial contact with the circumferential surface (9.3) of the guide element (9) and the circumferential surface (2.3) of the armature recess (2.2).

• - Beim Bestromen der Magnetspule (1.1) des Spulenträgers (1) vollführt die Ankerscheibe (2) zunächst eine kurze erste Hubbewegung zum Spulenträger (1) hin, bis der O-Ring (12) leicht zwischen der Seitenfläche (2.4) der Ankerausnehmung (2.2) und der Seitenfläche (1.4) des Spulenträgers (1) axial eingespannt ist und dadurch radial in Kontakt zur Umfangsfläche (9.3) des Führungselements (9) und zur Umfangsfläche (2.3) der Ankerausnehmung (2.2) kommt.
• - Unmittelbar anschließend vollführt die Ankerscheibe (2) eine weitere zweite Hubbewegung zum Spulenträger (1) hin, bis die Ankerscheibe (2) am Spulenträger (1) zur Anlage kommt und somit der Luftspalt (L1) „null“ wird.
• - Während dieser zweiten Hubbewegung wird der O-Ring (12) weiter axial verformt, wobei sich diese axiale Verformung auf eine erste elastische Verformung an der Seitenfläche (2.4) der Ankerausnehmung (2.2) und eine gleich große zweite elastische Verformung an der Seitenfläche (1.4) des Spulenträgers (1) aufteilt.
• - Die genannte erste elastische Verformung führt dazu, dass sich der Reibbelag (2.1) der Ankerscheibe (2) um den dritten Luftspalt (L3) von der Bremsscheibe (S) entfernt.
• - Die genannte zweite elastische Verformung führt dazu, dass sich der Reibbelag (3.1) der mit dem Spulenträger (1) verbundenen Gegenplatte (3) um den zweiten Luftspalt (L2) von der Bremsscheibe (S) entfernt.
• - Dadurch, dass die beschriebene erste und zweite elastische Verformung des O-Rings (12) gleich groß sind, ergeben sich bei geöffneter Bremszange (BR) gleich große Luftspalte (L2, L3).

The release movement of the brake calliper (BR) thus takes place at the transition between the 3 shown closed position and the one in 4 shown open position of the brake caliper (BR) and proceeds as follows:

• - When the magnetic coil (1.1) of the coil carrier (1) is energized, the armature disk (2) initially performs a short first stroke movement towards the coil carrier (1) until the O-ring (12) is slightly axially clamped between the side surface (2.4) of the armature recess (2.2) and the side surface (1.4) of the coil carrier (1) and thereby comes into radial contact with the circumferential surface (9.3) of the guide element (9) and the circumferential surface (2.3) of the armature recess (2.2).
• - Immediately afterwards, the armature disk (2) performs a further second stroke movement towards the coil carrier (1) until the armature disk (2) comes into contact with the coil carrier (1) and thus the air gap (L1) becomes “zero”.
• - During this second stroke movement, the O-ring (12) is further axially deformed, this axial deformation being divided into a first elastic deformation on the side surface (2.4) of the armature recess (2.2) and a second elastic deformation of the same size on the side surface (1.4) of the coil carrier (1).
• - The first elastic deformation mentioned above causes the friction lining (2.1) of the armature disc (2) to move away from the brake disc (S) by the third air gap (L3).
• - The said second elastic deformation causes the friction lining (3.1) of the counter plate (3) connected to the coil carrier (1) to move away from the brake disc (S) by the second air gap (L2).
• - Due to the fact that the described first and second elastic deformation of the O-ring (12) are equal, the air gaps (L2, L3) are equal when the brake caliper (BR) is open.

In 5 is a side view of the brake calliper (BR) including the associated brake disc (S) as a sectional view according to section line X - X from 2 shown in the braked state.

In the recesses of the coil carrier (1) which are open towards the armature disk (2), there are spring elements (6) which apply force to the armature disk (2) towards the brake disk (S), the brake disk (S) being mounted so as to be rotatable about the axis of rotation (R) relative to the stationary machine wall.

The brake caliper (BR) in 5 is shown in the braked state, with the brake disc (S) clamped between the friction linings (2.1) of the armature disc (2) and the friction linings (3.1) of the counterplate (3) by the force of the spring elements (6). According to detail F, the second air gap (L2) and the third air gap (L3) are zero.

At the same time, the first air gap (L1) shown in detail E between the coil carrier (1) and the armature disk (2) reaches its maximum value.

Detail E also shows a second release element in the form of a quad ring (13) concentric with the guide axis (F), which lies in a circumferential coil carrier recess (1.2) of the coil carrier (1) and can, but does not have to, have contact with the circumferential surface (9.3) of the guide element (9) and/or the circumferential surface (1.3) of the coil carrier recess (1.2).

In the axial direction parallel to the guide axis (F), the quad ring (13) has no preload.

Here too, the release element can be formed as a closed, circumferential quad ring (13) or from individual ring segments with a cross-section corresponding to the quad ring (13).

The brake caliper (BR) in 6 is shown in the unbraked, i.e. open, state, ie the armature disk (2) is pulled towards the coil carrier (1) by the energized magnetic coil (1.1) against the force of the spring elements (6) and the friction linings (2.1, 3.1) of the armature disk (2) and counter plate (3) are not in contact with the brake disk (S), which can therefore rotate freely around the rotation axis (R).

According to detail H, the second air gap (L2) and the third air gap (L3) between the friction linings (2.1, 3.1) and the brake disc (S) assume their respective maximum values, which are ideally equal when the release mechanism is functioning optimally.

Accordingly, when the brake caliper (BR) is open, the first air gap (L1) between the coil carrier (1) and the armature disk (2) assumes its minimum value, which has the value "zero" in the illustration in detail G. The quad ring (13), also shown in detail G, is axially clamped between the side surface (1.4) of the coil carrier recess (1.2) and the side surface (2.4) of the armature disk (2) when the brake caliper (BR) is open and is therefore in radial contact with the circumferential surface (9.3) of the guide element (9) and the circumferential surface (1.3) of the coil carrier recess (1.2).

• - Beim Bestromen der Magnetspule (1.1) des Spulenträgers (1) vollführt die Ankerscheibe (2) zunächst eine kurze erste Hubbewegung zum Spulenträger (1) hin, bis der Quad-Ring (13) leicht zwischen der Seitenfläche (1.4) der Spulenträgerausnehmung (1.2) und der Seitenfläche (2.4) der Ankerscheibe (2) axial eingespannt ist und dadurch radial in Kontakt zur Umfangsfläche (9.3) des Führungselements (9) und zur Umfangsfläche (1.3) der Spulenträgerausnehmung (1.2) kommt.
• - Unmittelbar anschließend vollführt die Ankerscheibe (2) eine weitere zweite Hubbewegung zum Spulenträger (1) hin, bis die Ankerscheibe (2) am Spulenträger (1) anliegt und somit der Luftspalt (L1) „null“ wird.
• - Während dieser zweiten Hubbewegung wird der Quad-Ring (13) weiter axial verformt, wobei sich diese axiale Verformung auf eine erste elastische Verformung an der Seitenfläche (1.4) der Spulenträgerausnehmung (1.2) und eine gleich große zweite elastische Verformung an der Seitenfläche (2.4) der Ankerscheibe (2) aufteilt.
• - Die genannte erste elastische Verformung führt dazu, dass sich der Reibbelag (3.1) der mit dem Spulenträger (1) verbundenen Gegenplatte (3) um den zweiten Luftspalt (L2) von der Bremsscheibe (S) entfernt.
• - Die genannte zweite elastische Verformung führt dazu, dass sich der Reibbelag (2.1) der Ankerscheibe (2) um den dritten Luftspalt (L3) von der Bremsscheibe (S) entfernt.
• - Dadurch, dass die beschriebene erste und zweite elastische Verformung des Quad-Rings (13) gleich groß sind, ergeben sich bei geöffneter Bremszange (BR) gleich große Luftspalte (L2, L3).

The release movement of the brake calliper (BR) thus takes place at the transition between the 5 shown closed position and the one in 6 shown open position of the brake caliper (BR) and proceeds as follows:

• - When the magnetic coil (1.1) of the coil carrier (1) is energized, the armature disk (2) initially performs a short first stroke movement towards the coil carrier (1) until the quad ring (13) is lightly clamped axially between the side surface (1.4) of the coil carrier recess (1.2) and the side surface (2.4) of the armature disk (2) and thereby comes into radial contact with the circumferential surface (9.3) of the guide element (9) and the circumferential surface (1.3) of the coil carrier recess (1.2).
• - Immediately afterwards, the armature disk (2) performs a further second stroke movement towards the coil carrier (1) until the armature disk (2) rests against the coil carrier (1) and thus the air gap (L1) becomes “zero”.
• - During this second stroke movement, the quad ring (13) is further deformed axially, this axial deformation being divided into a first elastic deformation on the side surface (1.4) of the coil carrier recess (1.2) and a second elastic deformation of the same size on the side surface (2.4) of the armature disk (2).
• - The said first elastic deformation causes the friction lining (3.1) of the counter plate (3) connected to the coil carrier (1) to move away from the brake disc (S) by the second air gap (L2).
• - The second elastic deformation causes the friction lining (2.1) of the Armature disc (2) is moved away from the brake disc (S) by the third air gap (L3).
• - Because the described first and second elastic deformations of the quad ring (13) are of equal size, the air gaps (L2, L3) are of equal size when the brake calliper (BR) is open.

The brake caliper (BR) in 7 with detail J and detail K is shown in the unbraked, i.e. open, state, ie the armature disk (2) is pulled towards the coil carrier (1) by the energized magnetic coil (1.1) against the force of the spring elements (6) and the friction linings (2.1, 3.1) of the armature disk (2) and counter plate (3) are not in contact with the brake disk (S), which can therefore rotate freely around the rotation axis (R).

According to detail K, the second air gap (L2) and the third air gap (L3) between the friction linings (2.1, 3.1) and the brake disc (S) assume their respective maximum values, which are ideally equal when the release mechanism is functioning optimally.

Accordingly, when the brake caliper (BR) is open, the first air gap (L1) between the coil carrier (1) and the armature disk (2) assumes its minimum value, which has the value "zero" in the illustration in detail J. The third release element in the form of a square ring (14), also shown in detail J, is located in this embodiment in an armature recess (2.2) which is delimited radially by a circumferential surface (2.3) and axially by two side surfaces (2.4) and thus forms a circumferential groove closed on three sides.

The square ring (14) is only preloaded radially against the circumferential surface (2.3) of the armature recess (2.2) and the circumferential surface (9.3) of the guide element (9).

The armature recess (2.2) is preferably designed such that in the region of its circumferential surface (2.3) it corresponds approximately to the width and the geometric shape of the square ring (14) and that its axial extent increases in the direction parallel to the guide axis (F) towards the guide element (9), so that the two side surfaces (2.4) are inclined to one another at an angle in a range of preferably 10° to 90° and geometrically each form part of a conical surface.

Detail L shows the same section as detail J, but in contrast, with the brake caliper closed (BR).

The brake disc (S) is clamped between the friction linings (2.1, 3.1) of the armature disc (2) and the counterplate (3), and the first air gap (L1) between the coil carrier (1) and the armature disc (2) is at its maximum. The square ring (14) shown in detail L is elastically deformed and assumes the shape of a parallelogram.

This deformation from a rectangle to a parallelogram occurs when the brake caliper (BR) transitions from the open state shown in detail J to the closed state shown in detail L. This is because the square ring (14) is preloaded so strongly against the circumferential surfaces (2.3, 9.3) of the armature disk (2) and guide element (9) that no surface sliding occurs at these contact points. Conversely, when the brake caliper (BR) is opened, a release movement occurs through the square ring (14), during which the square ring (14) moves back from its deformed state shown in detail L to its undeformed state according to detail J, thereby creating the release effect with the second air gap (L2) and third air gap (L3) of the same size.

The brake caliper (BR) in 8 with detail M and detail N is shown in the unbraked, i.e. open, state, ie the armature disk (2) is pulled towards the coil carrier (1) by the energized magnetic coil (1.1) against the force of the spring elements (6) and the friction linings (2.1, 3.1) of the armature disk (2) and the counter plate (3) are not in contact with the brake disk (S), which can therefore rotate freely around the rotation axis (R).

According to detail N, the second air gap (L2) and the third air gap (L3) between the friction linings (2.1, 3.1) and the brake disc (S) assume their respective maximum values, which are ideally equal when the release mechanism is functioning optimally.

Accordingly, when the brake caliper (BR) is open, the first air gap (L1) between the coil carrier (1) and the armature disk (2) assumes its minimum value, which in the illustration at detail M has the value “zero”.

The fourth release element, also shown in detail M, in the form of a metal ring (15) with a round wire cross-section, is located in this embodiment in a coil carrier recess (1.2) that is radially bounded by a circumferential surface (1.3) and axially by two side surfaces (1.4), thus forming a circumferential groove closed on three sides. The metal ring (15) is only radially preloaded against the circumferential surface (9.3) of the guide element (9) and the circumferential surface (1.3) of the coil carrier recess (1.2).

This pre-tensioning of the metal ring (15) is made possible by the fact that the metal ring (15) is arranged as shown in 10 A and 10 B in Circumferential direction forms a polygon with external contacts (15.1) and internal contacts (15.2) alternating in the circumferential direction, wherein the external contacts (15.1) are aligned towards the coil carrier recess (1.2) and the internal contacts (15.2) are aligned towards the guide element (9).

In the non-deformed state of the metal ring (15) in the direction parallel to the guide axis (F), as shown in detail M, the contact points between the external contacts (15.1) and the coil carrier recess (1.2) and the contact points between the internal contacts (15.2) and the guide element (9) lie in one plane.

The circumferential surface (1.3) of the coil carrier recess (1.2) preferably has the shape of a circular arc, the radius of which corresponds approximately to the radius of the wire cross-section of the metal ring (15) and thus embeds it in a form-fitting manner in the circumferential surface (1.3).

The coil carrier recess (1.2) is preferably designed such that its axial extent increases in the direction parallel to the guide axis (F) towards the guide element (9), so that the two side surfaces (1.4) are inclined to one another at an angle in a range of preferably 10° to 90° and geometrically each form part of a conical surface.

Detail O shows the same section as detail M, but in contrast, with the brake caliper closed (BR).

The brake disc (S) is clamped between the friction linings (2.1, 3.1) of the armature disc (2) and the counterplate (3), and the first air gap (L1) between the coil carrier (1) and the armature disc (2) is at its maximum. The metal ring (15) shown in detail O is elastically deformed.

During this elastic deformation, the metal ring (15) has a shape in which the plane with the contact points between the external contacts (15.1) of the metal ring (15) and the coil carrier recess (1.2) is spaced parallel from the plane with the contact points between the internal contacts (15.2) of the metal ring (15) and the guide element (9).

This distance between the two levels is created during the transition of the brake calliper (BR) from the open state shown in detail M to the closed state shown in detail O by the metal ring (15) being so strongly pre-tensioned against the circumferential surfaces (1.3, 9.3) of the coil carrier (1) and guide element (9) or being embedded there in a form-fitting manner that no superficial sliding takes place at these contact points.

Conversely, when the brake calliper (BR) is opened, a release movement takes place through the metal ring (15), in which the metal ring (15) moves back from its deformed state shown in detail O to its undeformed state according to detail M, thereby creating the release effect with the second air gap (L2) and third air gap (L3) of the same size.

The brake caliper (BR) in 9 with detail P and detail Q is shown in the unbraked, i.e. open, state, ie the armature disk (2) is pulled towards the coil carrier (1) by the energized magnetic coil (1.1) against the force of the spring elements (6) and the friction linings (2.1, 3.1) of the armature disk (2) and counter plate (3) are not in contact with the brake disk (S), which can therefore rotate freely around the rotation axis (R).

According to detail Q, the second air gap (L2) and the third air gap (L3) between the friction linings (2.1, 3.1) and the brake disc (S) assume their respective maximum values, which are ideally equal when the release mechanism is functioning optimally.

Accordingly, when the brake caliper (BR) is open, the first air gap (L1) between the coil carrier (1) and the armature disk (2) assumes its minimum value, which in the illustration at detail P has the value “zero”.

The fourth release element, also shown in detail P, in the form of a metal ring (15) with a round wire cross-section, lies in this embodiment in a guide recess (9.2) of the guide element (9), which is delimited radially by a circumferential surface (9.3) and axially by two side surfaces (9.4) and thus forms a circumferential groove closed on three sides.

The metal ring (15) is only prestressed radially against the circumferential surface (9.3) of the guide element (9) and the circumferential surface (1.3) of the coil carrier (1).

This pre-tensioning of the metal ring (15) is made possible by the fact that the metal ring (15) is arranged as shown in 10 A and 10 B forms a polygon in the circumferential direction with external contacts (15.1) and internal contacts (15.2) alternating in the circumferential direction, wherein the external contacts (15.1) are aligned towards the circumferential surface (1.3) of the coil carrier (1) and the internal contacts (15.2) are aligned towards the circumferential surface (9.3) of the guide element (9).

In the non-deformed state of the metal ring (15) in the direction parallel to the guide axis (F), as shown in detail P, the con contact points between the external contacts (15.1) and the circumferential surface (1.3) of the coil carrier (1) and the contact points between the internal contacts (15.2) and the circumferential surface (9.3) of the guide element (9) in one plane.

The circumferential surface (9.3) of the guide recess (9.2) preferably has the shape of a circular arc, the radius of which corresponds approximately to the radius of the wire cross-section of the metal ring (15) and thus embeds it in a form-fitting manner in the circumferential surface (9.3).

The guide recess (9.2) is preferably designed such that its axial extent increases in the direction parallel to the guide axis (F) towards the circumferential surface (1.3) of the coil carrier (1), so that the two side surfaces (9.4) are inclined to one another at an angle in a range of preferably 10° to 90° and geometrically each form part of a conical surface.

Detail R shows the same section as detail P, but in contrast, with the brake caliper closed (BR).

The brake disc (S) is clamped between the friction linings (2.1, 3.1) of the armature disc (2) and the counterplate (3), and the first air gap (L1) between the coil carrier (1) and the armature disc (2) is at its maximum. The metal ring (15), shown in detail R, is elastically deformed. During this elastic deformation, the metal ring (15) has a shape in which the plane with the contact points between the outer contacts (15.1) of the metal ring (15) and the circumferential surface (1.3) of the coil carrier (1) is spaced parallel to the plane with the contact points between the inner contacts (15.2) of the metal ring (15) and the circumferential surface (9.3) of the guide element (9).

This distance between the two planes is created during the transition of the brake calliper (BR) from the open state shown in detail P to the closed state shown in detail R by the metal ring (15) being so strongly pre-tensioned against the circumferential surfaces (1.3, 9.3) of the coil carrier (1) and guide element (9) or being positively embedded there that no superficial sliding takes place at these contact points.

Conversely, when the brake calliper (BR) is opened, a release movement takes place through the metal ring (15), in which the metal ring (15) moves back from its deformed state shown in detail R to its undeformed state according to detail P, thereby creating the release effect with the second air gap (L2) and third air gap (L3) of the same size.

10 A shows a first advantageous embodiment of the metal ring (15), which has a polygonal shape over the circumference, which in the present example corresponds to an ellipse.

The metal ring (15) has alternating outer contacts (15.1) and inner contacts (15.2) around its circumference, which are located on an enveloping circle (15.4) and an inner circle (15.5) respectively.

The external contacts (15.1) are intended to come into contact with a circumferential surface (1.3, 2.3) of the coil carrier (1) or the armature disk (2) and the internal contacts (15.2) are intended to come into contact with a circumferential surface (9.3) of the guide element (9).

To achieve increased flexibility and to enable easy assembly, the metal ring (15) has an interruption (15.3) which can be located either in the area of an external contact (15.1) or in the area of an internal contact (15.2) or in an intermediate area.

10 B shows a second advantageous embodiment of the metal ring (15), which has a polygonal shape over the circumference, which in the present example corresponds to a hexagonal polygon.

The metal ring (15) has alternating outer contacts (15.1) and inner contacts (15.2) over its circumference, which are located correspondingly on an enveloping circle (15.4) and an inner circle (15.5) and which are intended to come into contact with a peripheral surface (1.3, 2.3) of the coil carrier (1) or the armature disk (2) or into contact with a peripheral surface (9.3) of the guide element (9).

The metal ring (15) made of 10 B has an interruption (15.3) for the reasons mentioned above, which in the example in 10 B is placed on an internal contact (15.2).

In contrast to the embodiments shown, the metal ring (15) can be designed as a polygon with "N" radially outward-facing corners, whereby the variable "N" can practically assume a value between 2 and 20, with a value "N" of 2 to 6 being considered very advantageous. Unequal or equal distances between external contacts (15.1) and internal contacts (15.2) are possible over the circumference of the metal ring (15).

The cross-section of the metal ring (15) can be round, polygonal or polygonal, with versions with round, elliptical and square cross-sections being considered particularly advantageous.

The metal ring (15) can be made of all conceivable metal alloys which have sufficient elasticity and rigidity and which, in contact with the circumferential surface (1.3, 2.3) of the coil carrier (1) or the armature disk (2) and in contact with the circumferential surface (9.3) of the guide element (9), have the required tribological properties with low wear rates.

List of reference symbols:

1

coil carrier

1.1

magnetic coil

1.2

Coil carrier recess

1.3

circumferential area

1.4

side surface

2

Anchor disc

2.1

Friction lining

2.2

Anchor recess

2.3

circumferential area

2.4

side surface

3

Counter plate

3.1

Friction lining

4

spacer bushing

5

Second fastening element

6

spring element

7

brake frame

8

First fastener

9

Guide element

9.1

guide bushing

9.2

Guide recess

9.3

circumferential area

9.4

side surface

10

Manual release lever

11

Switch

12

O-ring

13

Quad ring

14

Square edge

15

metal ring

15.1

External contact

15.2

Internal contact

15.3

interruption

15.4

Enveloping circle

15.5

inner circle

BR

brake caliper

F

Guide axis

L1

First air gap

L2

Second air gap

L3

Third air gap

R

axis of rotation

S

brake disc

QUOTES CONTAINED IN THE DESCRIPTION

This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 10330306A1 [0010]
• DE 102016015242A1 [0015]

Claims (19)

Electromagnetically released brake calliper (BR) for braking a brake disc (S) mounted so as to be rotatable about a rotational axis (R), wherein the brake calliper (BR) has a brake frame (7) connected to a stationary machine wall and having one or more guide elements (9), wherein at least one coil carrier (1), an armature disc (2) and a counter-plate (3) are arranged on the guide elements (9) so as to be displaceable essentially parallel to the rotational axis (R) of the brake disc (S), wherein the coil carrier (1) has a magnetic coil (1.1) for attracting an armature disc (2) and spring elements (6) for pushing the armature disc (2) away, wherein the coil carrier (1) and the counter-plate (3) are connected to one another or are designed in one piece in such a way that they surround the brake disc (S) in a U-shape and that through frictional contact between the friction linings (2.1, 3.1) of the armature disc (2) and the counter-plate (3) with the A braking effect is achieved by the force of the spring elements (6) on the opposite flat surfaces of the brake disc (S), wherein the braking effect is canceled by energizing the magnetic coil (1.1) and attracting the armature disc (2) towards the coil carrier (1) against the force of the spring elements (6), and wherein the brake caliper (BR) has a release mechanism in order to prevent contact between the friction linings (2.1, 3.1) and the brake disc (S) when the brake caliper (BR) is open, characterized in that in the region of the guide of the brake caliper (BR) between the at least one guide element (9) and the at least one coil carrier (1) or the at least one armature disc (2) in at least one recess (1.2, 2.2, 9.2) concentric with a guide axis (F) of the guide element (9), at least one annular release element (12, 13, 14, 15) is arranged in a completely circumferential form or provided with at least one interruption (15.3). is. Brake caliper (BR) with a release mechanism according to Claim 1 , characterized in that at least one recess (1.2, 2.2) is made in the coil carrier (1) or in the armature disk (2), which is formed in the radial direction by a circumferential surface (1.3, 2.3) and in the axial direction by a side surface (1.4, 2.4) of the relevant component itself and by a side surface (2.4, 1.4) of the adjacent component, i.e. the armature disk (2) or the coil carrier (1). Brake caliper (BR) with a release mechanism according to Claim 2 , characterized in that the annular release element (12, 13, 14, 15) is not or only slightly prestressed in the axial and/or radial direction when the brake calliper (BR) is closed. Brake caliper (BR) with a release mechanism according to Claim 2 , characterized in that the annular release element (12, 13, 14, 15) is prestressed in the axial and radial directions by the coil carrier (1) and the armature disk (2) when the brake caliper (BR) is open. Brake caliper (BR) with a release mechanism according to Claim 2 , characterized in that the annular release element (12, 13, 14, 15), which is not preloaded when the brake calliper (BR) is closed, experiences an axial preload in a first phase when the brake calliper (BR) is opened by the coil carrier (1) and the armature disk (2) until the release element (12, 13, 14, 15) comes into frictional contact with one of the circumferential surfaces (1.3, 2.3) of the coil carrier (1) or armature disk (2) and with the circumferential surface (9.3) of the guide element (9) and that the release element (12, 13, 14, 15) experiences a further axial preload in a second phase, which is divided equally between the coil carrier (1) and the armature disk (2) and which leads to the fact that, when the brake calliper (BR) is opened, between the friction linings (2.1, 3.1) and the two sides of the brake disk (S) set equal air gaps (L2, L3). Brake caliper (BR) with a release mechanism according to Claim 1 , characterized in that at least one recess (1.2, 2.2) is made in the coil carrier (1) or in the armature disk (2), which recess is formed in the radial direction by a circumferential surface (1.3, 2.3) and in the axial direction by two side surfaces (1.4, 2.4) of the component in question itself. Brake caliper (BR) with a release mechanism according to Claim 6 , characterized in that the axial width of the recess (1.2, 2.2) in the region of the respective circumferential surface (1.3, 2.3) is adapted to the width and shape of the annular release element (12, 13, 14, 15) and that the axial width of the recess (1.2, 2.2) running parallel to a guide axis (F) increases towards the guide element (9) so that the two side surfaces are inclined towards one another and thereby enclose an angle of preferably 10° to 90°. Brake caliper (BR) with a release mechanism according to Claim 6 , characterized in that the annular release element (12, 13, 14, 15) is arranged in the radial direction between the circumferential surfaces (1.3, 2.3) of the coil carrier (1) or the armature disk (2) and the peripheral surface (9.3) of the guide element (9) are permanently prestressed. Brake caliper (BR) with a release mechanism according to Claim 6 , characterized in that the annular release element (12, 13, 14, 15) has an axial prestress parallel to the guide axis (F) between its contact area on the circumferential surface (1.3, 2.3) of the coil carrier (1) or the armature disk (2) and its contact area on the circumferential surface (9.3) of the guide element (9) when the brake calliper (BR) is closed, and that the release element (12, 13, 14, 15) changes into a state which is not prestressed in the axial direction when the brake calliper (BR) is opened, as a result of which air gaps (L2, L3) of equal size are established between the friction linings (2.1, 3.1) and the two sides of the brake disk (S) when the brake calliper (BR) is open. Brake caliper (BR) with a release mechanism according to Claim 1 , characterized in that at least one guide recess (9.2) is introduced into the guide element (9), which is formed in the radial direction by a circumferential surface (9.3) and in the axial direction by two side surfaces (9.4) of the guide recess (9.2). Brake caliper (BR) with a release mechanism according to Claim 10 , characterized in that the axial width of the guide recess (9.2) in the region of the circumferential surface (9.3) is adapted to the width and shape of the annular release element (12, 13, 14, 15) and that the axial width of the guide recess (9.2) running parallel to the guide axis (F) increases towards the coil carrier (1) and the armature disk (2), so that the two side surfaces are inclined towards one another and thereby enclose an angle of preferably 10° to 90°. Brake caliper (BR) with a release mechanism according to Claim 10 , characterized in that the annular release element (12, 13, 14, 15) is permanently prestressed in the radial direction between the circumferential surface (9.3) of the guide element (9) and the circumferential surface (1.3, 2.3) of the coil carrier (1) or the armature disk (2). Brake caliper (BR) with a release mechanism according to Claim 10 , characterized in that the annular release element (12, 13, 14, 15) has an axial preload parallel to the guide axis (F) between its contact area on the circumferential surface (9.3) of the guide element (9) and its contact area on the circumferential surface (1.3, 2.3) of the coil carrier (1) or the armature disk (2) when the brake caliper (BR) is closed, and in that the release element (12, 13, 14, 15) changes into a state which is not preloaded in the axial direction when the brake caliper (BR) is opened, as a result of which air gaps (L2, L3) of equal size are established between the friction linings (2.1, 3.1) and the two sides of the brake disk (S) when the brake caliper (BR) is open. Brake caliper (BR) with a release mechanism according to one of the preceding claims, characterized in that the release element (12, 13, 14, 15) is a ring concentric with the guide axis (F) which, in its front view, has a circumferential circular or polygonal contour. Brake caliper (BR) with a release mechanism according to one of the preceding claims, characterized in that the release element (12, 13, 14, 15) is designed as a ring with a circular cross-section or a polygonal cross-section or a multi-edged cross-section or a cross-section corresponding to a commercially available quad ring. Brake caliper (BR) with a release mechanism according to one of the preceding claims, characterized in that the release element (12, 13, 14, 15) is made of or coated with a rubber-elastic material or an elastic plastic or a metal alloy. Brake caliper (BR) with a release mechanism according to one of the preceding claims, characterized in that the release element (12, 13, 14, 15) is designed as an O-ring (12) or as a quad ring (13) or as a square ring (14) or as a metal ring (15). Brake caliper (BR) with a release mechanism according to one of the preceding claims, characterized in that the guide element (9) and the complementary openings of the coil carrier (1) and armature disk (2) have a polygonal or polygonal cross-section. Brake caliper (BR) according to one of the preceding claims, characterized in that the release mechanism has only one recess (1.2, 2.2, 9.2) with several release rings (12, 13, 14, 15) arranged axially one behind the other or has several recesses (1.2, 2.2, 9.2) each with at least one release ring (12, 13, 14, 15).

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