DE102017003166A1 - BRAKE CALIPER OF A DISC BRAKE WITH ELECTROMECHANICAL ACTUATION WITH AN ELASTIC PROTECTION ELEMENT - Google Patents

Abstract

A disc brake caliper (4) comprising a caliper body (6) including a spindle / spindle nut type mechanism (8) provided with a spindle (12) operatively connected to motor means for pivotal movement about an axis of rotation (Fig. XX), and with a spindle nut (16) engaged with said spindle (12), said spindle nut (16) being positively coupled to a thrust piston (20) for pushing a lining (24) so as to engage said axis of rotation (XX) can be axially displaced but can not be rotated, said pushing piston (20) having a head (28) adapted to attach to a lining and in a forward direction (F) towards the pad (24) and in a return direction (R) from the pad (24) moves. Advantageously, the spindle (12) is axially translationally bonded to the caliper body (6) so that it can rotate but not translate with respect to the axis of rotation (XX), the caliper (4) comprising elastic means (48) suitable thereto are to dampen a reaction force on the spindle nut (16) upon reaching a stroke end shoulder (52) of the thrust piston (20) at its axial return from the assignable lining (24).

Description

FIELD OF USE

The present invention relates to a caliper of a disc brake with electromechanical actuation, which is provided with an elastic protective element.

STATE OF THE ART

In the field of brake calipers for disc brakes with electromechanical actuation, it is common, especially in brake systems of the type BBW (brake by wire), to provide safety devices capable of achieving a stroke mechanical end at the return of those intended to actuate the pads Brake piston to reduce mechanical and / or electrical overload of the system.

In fact, when the brake piston returns, when it reaches the end of its stroke and abuts axially against the corresponding support surface on the caliper body, a shock is generated which is transmitted to the screw and which can cause damage to some components extending between the Screw and the caliper body.

The position of the mechanical stroke end does not appear during normal use of the disc brake caliper, but is achieved only under some operating conditions, such as: when the worn pad and the worn disc change, when the system is restarted or in the event of an electrical failure.

Therefore, it is necessary in the return of the brake piston, in the case of a stop, to avoid the occurrence of possible damage to the saddle, although this does not occur frequently in normal use of the caliper of the disc brake.

PRESENTATION OF THE PRESENT INVENTION

In order to solve the mentioned problems, some technical solutions have heretofore been used in the prior art.

For example, from the document WO 201142280 A1 known that a spring between an axial bearing and the caliper body along the thrust spindle axis of the piston can be used; however, such a spring has the function of relating the displacement of the screw to the value of the force applied to the disc when the stiffness of the spring is known. In the document WO 201142280 A1 , In the phase of the withdrawal of the braking force, when the piston has struck the stop element (ie, a complete return has been completed) also the use of a position sensor is provided which reads the displacement of the screw due to the compression of another spring between the caliper body and the screw is arranged to ensure a more damped displacement of the screw in the final phase of the approach. The control of the electric motor is then defined as a function of the displacement read by the sensor.

This solution in the document WO 201142280 A1 But does not quite solve the technical problem of avoiding mechanical damage when reaching the stroke end in the return of the brake piston.

It also requires the document WO 201142280 A1 described solution, the use of an additional hub sensor, which increases the cost and complexity in the production and in the control of the system.

Furthermore, from the document US 2012/0090418 A1 a solution is known, which provides a ball screw having a spindle nut with a mechanical lock, which is arranged in the direction of rotation, and a receiving plate, which has a locking tooth. The mechanical stroke end is realized via the (circumferential) contact between the abutment surface on the spindle nut and the locking tooth on the receiving plate of the spindle. In the position of the stroke end, an axial clearance is obtained between the spindle nut and the receiving plate, which enables prevention of possible damage caused by a blockage of the spindle and spindle nut within the caliper.

However, this technical solution has the technical disadvantage that it does not ensure a reliable correlation between the rotation of the shaft of the electric motor and the translation of the piston; in fact, with this type of brake system actuators, for the purpose of software control, it is necessary to ensure the correlation between the rotational angle of the electric motor shaft and the translation or stroke of the thrust piston under each condition of use (temperature, speed, etc.) ,

The technical solution from the document US2012 / 0090418 A1 causes the spindle, the spindle nut and the piston, after reaching the position at the mechanical stroke end, if the electric motor would be kept started would rotate integrally within the brake caliper without translation, with concomitant loss of correlation between motor rotation and spindle translation.

There is thus a need to remedy the aforementioned disadvantages and limitations of the solutions with respect to saddle of disc brakes with electromechanical actuation according to the prior art.

In other words, there is a need in the art on the one hand to ensure the safe and precise correlation between the rotation of the shaft of the electric motor and the translation of the piston (to have reliability, precision, calibration and repeatability in braking) and, on the other hand, the need To prevent the occurrence at the stroke end at the return, of excessive mechanical loads that could damage the mechanism for moving the piston.

These needs are met by a caliper of a disc brake according to claim 1.

• – einen Mechanismus der Art Spindel/Spindelmutter, der mit einer Schraube bzw. Spindel ausgestattet ist, die operativ bzw. funktionell mit Motorenmitteln verbunden ist, sodass sie um eine Rotationsachse X-X dreht, und mit einer Spindelmutter, die mit der genannten Spindel im Eingriff steht.
• – wobei die Spindelmutter formschlüssig mit einem Schubkolben zum Schub eines Belags gekoppelt ist, sodass sie bezüglich der genannten Rotationsachse X-X axial verschoben aber nicht gedreht werden kann, wobei der Schubkolben einen Kopf aufweist, der angepasst ist, um sich mit einem Belag des genanten Sattels der Scheibenbremse zu verbinden, und wobei er sich in eine Vorwärts-Richtung F hin zum Belag und in eine Rücklauf-Richtung R vom Belag bewegt. dadurch gekennzeichnet, dass
• – die Spindel ist axial translatorisch an den Sattelkörper gebunden, sodass sie bezüglich der Rotationsachse X-X drehen aber nicht verschoben werden kann,
• – der Sattel elastische Mittel umfasst, die dazu geeignet sind, eine Reaktionskraft auf die Spindelmutter bei Erreichung einer Schulter am Hub-Ende des Kolbens bei seinem axialen Rücklauf vom zuordenbaren Belag zu dämpfen.

In particular, this need is met by a caliper of a disc brake comprising:

• A spindle / spindle nut type mechanism provided with a screw operatively connected to motor means so as to rotate about a rotation axis XX and a spindle nut engaged with said spindle ,
• - Wherein the spindle nut is positively coupled to a thrust piston for pushing a lining, so that they can be axially displaced with respect to the said axis of rotation XX but not rotated, wherein the thrust piston has a head which is adapted to contact a lining of the said saddle To connect disc brake, and wherein it moves in a forward direction F towards the pad and in a return direction R of the pad. characterized in that
• - The spindle is axially translationally bonded to the caliper body, so that they rotate with respect to the rotation axis XX but can not be moved,
• - The saddle comprises elastic means which are adapted to dampen a reaction force on the spindle nut upon reaching a shoulder at the stroke end of the piston at its axial return from the assignable lining.

According to a possible embodiment of the said positive connection between the spindle nut and the thrust piston is prismatic type.

According to a possible embodiment of the positive connection between the spindle nut and the thrust piston is realized by means of interposition of a thrust ring which is received within the thrust piston.

According to a possible embodiment, the spindle is axially translationally by means of a slewing gear (Italian: ralla) bound to the caliper body, which realizes an axial binding of the spindle in the return direction R, and a snap ring, the axial binding of the spindle in the forward direction F realized the spindle which has the freedom to rotate about the rotation axis XX, being moved by the motor means.

According to a possible embodiment, the caliper body comprises an inner wall defining a hole which is traversed by a shaft of the spindle, said inner wall being arranged between the slewing gear and the circlip.

According to a possible embodiment, wherein the elastic means are positioned so as to prevent a collision between the spindle nut and said shoulder at the stroke end.

According to a possible embodiment, the elastic means are arranged on the side which is axially opposite to the thrust piston head, so that they work on reaching the said shoulder at the stroke end of the returning thrust piston under pressure load.

According to a possible embodiment, the elastic means are arranged between an axial end of the spindle nut, which is opposite the assignable lining, and a cover of the thrust piston, said cover axially integrating the spindle nut and the thrust piston, the elastic means being a collision between the spindle nut and prevent lids.

According to a possible embodiment, said cover is associated with the thrust piston by means of interposition of a retaining ring.

According to a possible embodiment, said cover is a washer inserted between the elastic means and a retaining ring.

According to a possible embodiment said elastic means are inserted between a lid of the piston, which is arranged in the region of a portion which is axially opposite the piston head, and the shoulder at the stroke end, wherein the lid is separated from the spindle nut by axial play.

According to a possible embodiment, said shoulder at the stroke end is associated with a force sensor which is adapted to measure the axial thrust under compression pressure which is transmitted at the stop of the thrust piston, said force sensor with a control unit (centralina di comando) is operatively connected to the engine means programmed to deactivate the engine means upon reaching a limit value of the axial thrust under compression pressure.

According to a possible embodiment, said elastic means comprise an elastic ring.

According to a possible embodiment, said elastic means comprise a cup spring (molla a tazza) or a helical spring.

According to a possible embodiment, said elastic means are sized and / or calibrated so that axial play between the spindle nut and the thrust piston is canceled.

According to one possible embodiment, said spindle / spindle nut mechanism comprises a ball screw, the spindle being operatively connected to said motor means, the spindle nut being coupled to the push piston, and a plurality of balls being interposed between the spindle nut and the spindle.

DESCRIPTION OF THE DRAWINGS

Further features and advantages of the present invention will become more apparent from the following description, which is given below together with preferred and non-limiting embodiments, wherein:

the 1 a sectional view of a saddle of a disc brake according to the invention represents;

the 2 the enlarged section II 1 according to an embodiment of the present invention;

the 3 Figure 12 is a schematic graph of the time course of the supply current of the electric motor of a caliper of a disc brake of a prior art solution compared to a caliper of a disc brake according to the invention;

the 4 the enlarged section II 1 according to another embodiment of the present invention;

the 5 FIG. 4 is a sectional view of a caliper of a disc brake according to another embodiment of the present invention; FIG.

the 6 the enlarged section VI 5 represents.

The common elements or parts of elements of the embodiments described below are identified by the same reference numerals.

DETAILED DESCRIPTION

With reference to said figures, the entirety of a saddle of a disc brake with 4 designated.

More particularly, the present invention relates to a caliper of a disc brake of electromechanical type, which provides an electrical actuation, a reduction system and a system for the transformation of a rotational movement into a translatory movement, as will be described in more detail below.

Therefore, the present invention is not tied to a specific type of brake caliper of a disc brake, but includes both fixed caliper and floating caliper.

The caliper 4 a disc brake comprises a caliper or caliper body 6 , that a mechanism of the kind spindle / spindle nut 8th picks up with a screw or spindle 12 is equipped, which is functionally connected to not shown motor means, so that it rotates about a rotation axis XX, and with a spindle nut 16 that with the mentioned spindle 12 is engaged.

The engine means are preferably electric motors.

The spindle nut 16 is form-fitting with a push piston 20 to the thrust of at least one covering 24 coupled, so that they can be axially displaced with respect to said rotation axis XX but not rotated.

For example, the said positive connection between the spindle nut 16 and the thrust piston 20 prismatic type.

For example, the positive connection between the spindle nut 16 and the thrust piston 20 by interposition of a thrust ring 26 realized within the thrust piston 20 is recorded.

The thrust piston 20 has a head 28 which is designed to with said coating 24 of the disc brake caliper 4 co.

The thrust piston 20 is preferably axially symmetrical with respect to said rotation axis XX; the thrust piston 20 is hollow, so he has a recording volume 32 limited. This axial symmetry is in the area of the interface with the thrust ring 26 not present, in which said prismatic positive connection is realized.

Preferably, said receiving volume is 32 even with respect to said rotation axis XX axisymmetric; this axial symmetry is in the area of the interface with the thrust ring 26 unavailable.

The caliper body 6 also includes an anti-rotation pin 33 in a hollow 35 engages on the thrust piston 20 is won; by inserting the anti-rotation pin 33 into the cavity 35 can the thrust piston 20 with respect to said rotation axis XX only shifted, not rotated. Of course, the mentioned cavity 35 elongated or buttonhole shaped, causing them the displacement of the thrust piston 20 allowed along its actuation hub. The anti-rotation pin 33 is appropriate on the caliper body 6 attached.

Preferably, the mechanism of the type comprises spindle / spindle nut 8th a ball screw, in which the spindle 12 is functionally connected to said motor means, and wherein the spindle nut 16 with the thrust piston 20 coupled and being between the spindle nut 16 and the spindle 12 a variety of balls 36 is arranged.

Of course, in a known way, both the spindle 12 as well as the spindle nut 16 each on an outer side surface 38 the spindle 12 and on an inner side surface 40 the spindle nut 16 helical runways or seats 44 on, which are suitable, at least partially, said balls 36 take.

Advantageously, the spindle 12 axially translational to the caliper body 6 tied so that they rotate with respect to the rotation axis XX but can not be moved.

For example, the axial rotational binding of the spindle 12 through the interposition of a circlip 45 made in a circumferential groove 46 engages on a shaft 47 the same spindle 12 is won. This circlip 45 may represent an axial lateral bond, ie in a single translational direction of the spindle.

In other words, the circlip is 45 axially on the shaft 47 the spindle 12 for example, bound by positive engagement, and is abutting on an inner wall 49 set in the caliper body 6 is won, so for the spindle 12 at least one axial bond in a forward direction F is created.

That way, the spindle becomes 12 about the rotational axis XX of the motor means in rotation without being axially displaced, ie parallel to said rotation axis XX. In this way, the spindle nut 16 , in turn, by the above-mentioned positive connection to the thrust piston 20 is bound, can only be moved parallel to the rotation axis XX, wherein they are in the phase of the braking process to the assignable surface 24 (corresponding to a forward direction F), or being in the phase of brake deceleration, release, or brake completion from said mating deck 24 removed (corresponding to a return direction R).

In other words, the anti-rotation pin prevents 33 the rotation of the thrust piston 20 because he is in the cavity 35 the thrust piston itself is inserted.

The piston can thus be moved with respect to said rotation axis XX but not rotated. The thrust ring 26 has a positive connection with the thrust piston 20 so it can not be turned against it. The thrust ring 26 is between the thrust piston 20 and the spindle nut 16 arranged and prevents the spindle nut 16 to turn it, allowing only one translation. It follows that the spindle 12 rotates and the spindle nut can perform only one translation.

Advantageously, the disc brake caliper comprises 4 elastic means 48 that are capable of applying a reaction force to the spindle nut 16 on reaching a stroke end shoulder 52 of the thrust piston 20 to attenuate, with an axial return of the assignable deposit 24 ,

The stroke end shoulder 52 is located at a position that is the head 28 of the thrust piston 20 axially opposite.

According to one possible embodiment is between the stroke end-shoulder 52 and the spindle 12 a lathe (Italian: ralla) 56 inserted leading to the spindle 12 is arranged coaxially.

The turntable 56 has the function of a guide or a bearing for the spindle 12 ,

The turntable 56 is designed such that it is against an undercut 58 the spindle 12 in a coverable area 24 stripping away direction.

Preferably, the said slewing form 56 an axial binding of the spindle 12 in return direction R. This is how the slewing gear works 56 with the circlip 45 together to make a bilateral axial bond in both directions of the spindle 12 forward and backward, which is free to rotate about the rotation axis XX, being driven by motor means.

For example, the inner wall limits 49 a hole 50 from the shaft 47 the spindle 12 is crossed. The inner wall 49 is preferably between the slewing gear 56 and the maritime ring 45 ,

Preferably, the elastic means 48 positioned so that it collides between the spindle nut 16 and the shoulder mentioned 52 at the stroke end. In this way, as described in more detail below, mechanical loads on the spindle nut 16 and thus the whole mechanism 8th the type spindle / spindle nut significantly reduced, especially when reaching the stroke end during the return of the thrust piston 20 ,

According to a possible embodiment, the elastic means 48 arranged on one side, the head 28 of the thrust piston 20 axially opposite so that they reach the said shoulder when reaching 52 at the stroke end of the return thrust piston 20 work under pressure.

According to a possible embodiment, the elastic means 48 between an axial end 60 the spindle nut 16 that the assignable surface 24 is opposite, and a lid 64 of the thrust piston 20 arranged, said lid the spindle nut 16 and the thrust piston 20 axially integrated with each other.

The elastic means 48 prevent in this way a collision between the spindle nut 16 and lid 64 even when reaching the aforementioned shoulder 52 at the stroke end of the thrust piston 20 in the return phase.

For example, the said lid 64 with the thrust piston 20 by interposing a retaining ring 68 connected.

Preferably, said lid is 64 cup-shaped ( 1 - 2 . 5 - 6 ); According to a further embodiment, the lid 64 a washer between the elastic means 48 and the retaining ring 68 ( 4 ) is set.

According to one embodiment ( 5 - 6 ) are said elastic means 48 between the lids 64 of the thrust piston 20 which is arranged in the area of a section facing the head 28 the thrust piston is axially opposite, and the stroke end shoulder 52 set, with the lid 64 through an axial play 72 from said spindle nut 16 is disconnected.

Preferably, said stroke end shoulder 52 a force sensor 76 assigned, which is suitable to measure the axial thrust under compression pressure, the stop of the thrust piston 20 is transmitted, said force sensor 76 is operatively connected to a control unit, not shown, of the engine means programmed to deactivate the engine means upon reaching an axial thrust limit under compression pressure applied by the force sensor 76 itself is measured.

There are several embodiments of said elastic means 48 possible.

For example, the elastic means comprise 48 an elastic ring; alternatively, said elastic means 48 a Cup or disc spring and / or a coil spring include.

Preferably, said elastic means 48 dimensioned and / or calibrated such that axial play between the spindle nut 16 and the thrust piston 20 be canceled.

As already stated, the thrust piston 20 hollow and limits a recording volume 32 , Preferably, said receiving volume contains the spindle 12 , the spindle nut 16 , the elastic means 48 , the turntable 56 and the lid 64 ; preferably, the caliper body limited 6 a single cavity 80 in which the thrust piston 20 and the entire mechanism of the spindle / spindle nut type 8th and also the hub-end-shoulder 52 and the force sensor 76 be recorded. Preferably, the outer diameter of the thrust piston corresponds 20 the inner diameter or the bore of said cavity 80 in which the thrust piston 20 runs axially with a certain radial clearance.

The operation of a disc brake caliper according to the invention will now be described.

As is known, the need for a user to apply braking to an electromechanically actuated disc brake caliper implies activation of the motor means that comprise the spindle 12 to rotate,

Since this last is translationally blocked axially, it can only rotate about said rotation axis XX. The rotation of the spindle 12 in turn causes the translation of the spindle nut 16 , which by the positive connection with the thrust piston 20 is rotationally blocked.

This last exerts its thrust against the surface 24 from, in turn, generates a braking torque when striking against the braking surface of a assignable brake disc.

In case of a possible return of the thrust piston 20 At the stroke end, the special design of the disc brake caliper 4 according to the invention, as explained, prevents a collision between the spindle nut 16 and the caliper body 6 ,

In fact, the spindle nut (as in the embodiments of FIGS 1 . 2 . 4 ) on the elastic means 48 at.

In the return phase of the thrust piston 20 the force sensor receives 76 from the thrust piston 20 a compression boost; upon reaching a certain threshold, the control unit deactivates the engine means.

In particular, the electric motor is controlled such that in each time interval, a certain angle of rotation of the motor shaft and thus a certain translation of the thrust piston 20 is predetermined. In the position of the mechanical stroke end, the translation of the thrust piston 20 prevented, and thus also the rotation of the motor shaft and the corresponding spindle 12 prevented. As a result, the control of the engine increases the drive torque, which also increases the exchange of forces between the inner components of the saddle.

The monitoring of the current supplied to the motor makes it possible to determine this unusual increase in the driving torque and therefore of the forces. Timing in accordance with this peak current, control is provided by interrupting the supply of the electric motor and avoiding the occurrence of mechanical stresses that could damage the mechanism and / or the motor means themselves.

In the absence of elastic means 48 For example, the increase in current, and therefore the force per unit time, is greater than that in the presence of the elastic means 48 results.

The use of elastic means 48 allows, with the same response time, the control of the engine means and before the interruption of the engine supply, the achievement of lower force values exchanged among the components than in the absence of the elastic means 48 ,

The graphic in the 3 shows the time course of the supply current of the electric motor both in the presence and in the absence of the elastic means 48 ,

Especially on the Y-axis of the graphic 3 the current of the motor means is applied, while on the x-axis the time in seconds is plotted.

The curve 11 represents the current flow in a solution according to the prior art, ie without the elastic means 48 while the curve 12 the same course in a solution according to the present invention, ie the elastic means 48 is provided.

As you can see, the two curves coincide with each other until time T1, the reaching of the stroke end at the return of the thrust piston 20 equivalent.

From this point in time T1 on the same control of the engine means at time T2 an interruption of the engine means drive is achieved.

As can be seen, the transition, namely the course of the supply current in the time interval T1-T2 in the two solutions deviates strongly: in the solution according to the prior art (I1) the course is much steeper than in the solution according to the present invention (I2), so that twice the absolute value of the current is reached. Of course, a double current value corresponds to about twice the mechanical load of the spindle / spindle nut mechanism 8th ,

In fact, the torque acting on the mechanism spindle / spindle nut 8th is transferred directly proportional to the said supply current of the motor: thus, a reduction in the current causes a reduction in the mechanical loads due to the mechanism spindle / spindle nut 8th be transmitted by yourself.

As can be understood from what has been described so far, the disc brake caliper according to the invention allows to overcome the presented disadvantages of the prior art.

In fact, thanks to the use of the elastic element in the system, which is compressed upon reaching the position at the mechanical stroke end, with the same reaction time of the control software of the motor means, a lower motor torque on the spindle and thus a lower load on the in Contact kicking members exercised.

In addition, the correlation between the rotation angle of the shaft of the electric motor and the translation or the stroke of the thrust piston under each use condition (temperature, speed, etc.) is always ensured.

In fact, the axial travel of the spindle is blocked and thus the correlation between the rotation of the motor shaft and the stroke of the piston is simply given by the gear ratio that is interposed between the motor and the spindle.

In other words, the solution according to the present invention allows on the one hand to ensure the reliable correlation between the rotation of the shaft of the electric motor and the translation of the piston (to have reliability, precision and repeatability during braking), and on the other hand the conclusion at the stroke end Rewind to prevent excessive mechanical stresses that could damage the mechanism for moving the piston.

Advantageously, the elastic element also has the function of balancing the assembly play between the spindle nut and the piston. In the absence of the elastic member, when the direction of rotation of the spindle changes to switch from a feed to a return of the push piston or vice versa, such play would cause idle translation of the spindle nut within the piston, corresponding to the present game. This idling would delay the braking action and result in less accurate control of the caliper force achieved by the caliper. The presence of the elastic element, however, ensures the uniform or solid movement of the spindle nut and piston.

One skilled in the art will be able to make numerous changes and variations to the disc brake calipers described above to meet contingent and specific needs, which are nevertheless within the scope of the present invention as defined in the claims which follow.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The 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

• WO 201142280 A1 [0007, 0007, 0008, 0009]
• US 2012/0090418 A1 [0010, 0012]

Claims (16)

Disc brake caliper ( 4 ), a saddle body ( 6 ) comprising: a mechanism of the spindle / spindle type ( 8th ), with a spindle ( 12 ) operatively connected to motor means so as to rotate about an axis of rotation (XX) and to a spindle nut ( 16 ), which are connected to said spindle ( 12 ) is engaged, - wherein the spindle nut ( 16 ) positively with a thrust piston ( 20 ) to the thrust of a deposit ( 24 ) so that it can be axially displaced with respect to said axis of rotation (XX), but can not be rotated, wherein the thrust piston ( 20 ) a head ( 28 ), which is adapted to attach to the pad, and in a forward direction (F) towards the pad ( 24 ) and in a return direction (R) from the lining ( 24 ) characterized in that - the spindle ( 12 ) axially translationally to the caliper body ( 6 ) is bound so that it can rotate with respect to the rotation axis (XX) but can not be displaced, - the saddle ( 4 ) elastic means ( 48 ), which are adapted to a reaction force on the spindle nut ( 16 ) upon reaching a stroke end shoulder ( 52 ) of the thrust piston ( 20 ) at its axial return from the assignable lining ( 24 ) to dampen. Disc brake caliper ( 4 ) according to claim 1, wherein said positive connection between the spindle nut ( 16 ) and the thrust piston ( 20 ) is prismatic type. Disc brake caliper ( 4 ) according to claim 1 or 2, wherein the positive connection between the spindle nut ( 16 ) and the thrust piston ( 20 ) by means of interposition of a thrust ring ( 26 ) realized within the thrust piston ( 20 ) is recorded. Disc brake caliper ( 4 ) according to claim 1, 2 or 3, wherein the spindle ( 12 ) axially translationally by means of a slewing gear ( 56 ) to the caliper body ( 6 ), which is an axial binding or limitation of the spindle ( 12 ) realized in a return direction (R), and a Seeger ring ( 45 ), an axial binding or limitation of the spindle in the forward direction (F) of the spindle ( 12 ), which has the freedom to rotate about the rotation axis (XX), being moved by the motor means. Disc brake caliper ( 4 ) according to claim 4, wherein the caliper body ( 6 ) an inner wall ( 49 ), which has a hole ( 50 ) of a shaft ( 47 ) of the spindle ( 12 ), said inner wall ( 49 ) between the slewing gear ( 56 ) and the Seeger ring ( 45 ) is arranged. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein the elastic means ( 48 ) are positioned so as to cause a collision between the spindle nut 16 ) and said shoulder ( 52 ) at the stroke end. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein the elastic means ( 48 ) are arranged on the side facing the head ( 28 ) of the thrust piston ( 20 ) is axially opposite, so that when the returning plunger ( 20 ) the said stroke end shoulder ( 52 ), working under pressure. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein the elastic means ( 48 ) between an axial end ( 60 ) of the spindle nut ( 16 ) that corresponds to the assignable surface ( 24 ) is opposite or opposite, and a lid ( 64 ) of the thrust piston ( 20 ) are stored, said lid ( 64 ) the spindle nut ( 16 ) and the thrust piston ( 20 ) are axially integrated with each other, wherein the elastic means ( 48 ) a collision or impact between the spindle nut ( 16 ) and lid ( 64 ) prevent. Disc brake caliper ( 4 ) according to claim 8, wherein said lid ( 64 ) the thrust piston ( 20 ) by interposition of a retaining ring ( 68 ) assigned. Disc brake caliper ( 4 ) according to claim 8, wherein said lid ( 64 ) is a washer between the elastic means ( 48 ) and a retaining ring ( 68 ) is inserted. Disc brake caliper ( 4 ) according to any one of claims 1 to 7, wherein said elastic means ( 48 ) between a lid ( 64 ) of the thrust piston ( 20 ) located in the region of a section facing the head ( 28 ) of the thrust piston ( 20 ) is axially opposite, and the stroke end shoulder (FIG. 52 ), the lid ( 64 ) by an axial play ( 72 ) of said spindle nut ( 16 ) is disconnected. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein said hub end shoulder ( 52 ) a force sensor ( 76 ), which is adapted to measure the axial thrust under compression pressure, the stop at the thrust piston ( 20 ), wherein said force sensor ( 76 ) is operatively connected to a control unit of the engine means programmed to cause the engine means to reach a threshold value of to disable axial thrust under compression pressure. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein said elastic means ( 48 ) comprise an elastic ring. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein said elastic means ( 48 ) comprise a cup spring or a coil spring. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein said elastic means ( 48 ) are dimensioned and / or calibrated or set such that axial play between the spindle nut ( 16 ) and the thrust piston ( 20 ) be canceled. Disc brake caliper ( 4 ) according to any one of the preceding claims, wherein said spindle / spindle nut mechanism ( 8th ) comprises a ball screw, wherein the spindle ( 12 ) is operatively connected to said motor means, the spindle nut ( 16 ) with the thrust piston ( 20 ) and wherein between the spindle nut ( 16 ) and the spindle ( 12 ) a plurality of balls ( 36 ) is arranged.

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