WO2014184112A1 - Disc brake with a measuring device for measuring grinding torque and a corresponding method - Google Patents

Abstract

A disc brake (1), particularly for a motor vehicle, comprises a measuring device (10) for measuring grinding torque between a brake disc (2) and at least one brake pad (3) of the disc brake (1). The measuring device (10) comprises at least one first measuring module (11) for direct measurement of the torque between the brake disc (2) and an axle flange/axle of a vehicle to be assigned to the brake disc (1). And a method for measuring a grinding torque of a disc brake (1).

Description

 Disc brake with a measuring device for grinding torque measurement and a corresponding method

The invention relates to a disc brake, in particular for a motor vehicle, having a measuring device for measuring the grinding torque according to the preamble of claim 1. The invention also relates to a corresponding method.

Vehicles and certain technical devices often use friction brakes to convert kinetic energy. Preference is given here, especially in the passenger car and commercial vehicle sector, the disc brake. In the typical design of a disc brake, this consists of the brake disc with usually two brake pads, a floating application clamping unit and a brake carrier with which the brake attached to the associated axle of a vehicle, e.g. screwed, will.

The application forces act on both brake pads on the brake disc and thus generate a braking torque. The brake disc experiences a delay of the rotational movement as a function of the magnitude of the application force. This delay is largely determined by the coefficient of friction between the brake disc and brake pad. Since the pads are structurally designed as wearing parts and the coefficients of friction are dependent on the strength, they are generally softer than the brake disc, i. the pads learn about their service life, a change in the lining thickness, they wear out. From this covering strength change, there is the necessity that a wear adjustment compensates for the change and thus sets a constant clearance. A constant air clearance is required to keep the response times of the brake small, to ensure the free movement of the brake disc and to provide a stroke reserve for limit load cases.

An example of a wear adjusting device is described in the document DE 10 2004 037 771 A1. In this case, a drive rotational movement is e.g. from a torque-limiting device, for example, with a ball ramp, via a continuously acting clutch (slip clutch) forwarded to an adjusting spindle of a threaded temple. The air play is adjusted continuously.

Due to the system arises due to the floating mounted application unit, the slidably arranged brake pads and a so-called disc impact Abrasive torque, which is also called residual grinding torque and counteracts the rotational movement of the brake disc. Depending on its size, it can result in increased fuel consumption of the associated vehicle as well as increased wear of brake pads and brake disc. The object of the present invention is to provide a disc brake with a measuring device for Schleifmomentmessung.

Another object is to provide a corresponding method. The object is achieved by a disc brake having the features of claim 1, and a method having the features of claim 18.

Disc brake is provided, which is equipped with a measuring device having at least one measuring module for a direct torque measurement between see the brake disc and one / a Achsflansch / axis of a disc brake vehicle to be assigned.

A disc brake according to the invention, in particular for a motor vehicle, has a measuring device for measuring the grinding torque between a brake disc and at least one brake pad of the disc brake. The measuring device has at least one first measuring module for a direct torque measurement between the brake disk and an axle flange / axle of a vehicle to be assigned to the disk brake. The disk brake with the measuring device results in a reliably functioning arrangement with which the residual grinding torques, which are very small relative to the braking torques that occur, can be measured by measuring under operating conditions (during normal braking). A method according to the invention for measuring an abrading torque of the disc brake described has the following method steps: (S1) determining operating states of the disc brake; (S2) detecting measured values of a torque between the disc brake disc and the associated axle or the associated axle flange when a detected operating state of the disc brake is an operating condition without a brake operation; and (S3) evaluating the measured values as the grinding torque of the disc brake.

This is advantageously achieved that under operating conditions, the relatively small residual grinding torques can be detected. Further advantageous embodiments are specified in the subclaims.

In one embodiment, the brake disc is coupled via an adapter to the / the Achsflansch / axis of the disc brake vehicle to be assigned, the brake disc and the adapter form a brake disc assembly in which the at least one first measuring module for the direct torque measurement between the brake disc and the adapter is provided. This allows a space-saving installation. In another embodiment, the adapter has a mounting portion for attachment to an axle to be assigned, a receiving portion for connection to the brake disk, and a central portion connecting the mounting portion and the receiving portion. Thus, the connections to the brake disc and the Achsflansch be split, making a simple replacement and a space-saving design possible.

It is further provided that the receiving portion of the adapter has at least one receiving profile for interaction with the at least one first measuring module and coupling profiles for coupling with disc receiving profiles of the brake disc, wherein the at least one receiving profile and the coupling profiles for receiving and / or mounting the brake disc Thus, a space-saving integration of the at least one measuring module in the power flow between the brake disc and adapter is possible. In addition, the brake disc may e.g. be mounted on or on the adapter relative to this rotatable by means of a bearing, for example, thin-ring bearings.

In a further embodiment, at least one disc receiving profile of the brake disc has a stop for interacting with the at least one first measuring module. The measuring module is fixed to the adapter, whereby the stop contacts the measuring module for the introduction of force. Of course, this arrangement is also possible vice versa.

In yet another embodiment, the coupling profiles of the adapter and the disc receiving profiles of the brake disc are coupled with bridging elements having a previously determinable game. This allows a power transmission from the adapter to the brake disc and vice versa.

It is provided that the at least one first measuring module for the direct torque measurement for small torques in the range of grinding moments is formed and can be bridged when exceeding a pre-definable torque by means of the bridging elements. For this purpose, the previously definable game of bridging elements of advantage, within which the torque measurement can take place. As soon as larger torques, for example during braking occur, the game is bridged and the bridging elements form a bridging of the measuring module in such a way that the force flow no longer passes through the measuring modules. An impairment, eg due to overload, the sensor is thus prevented.

In yet another embodiment, the receiving portion of the adapter is received in a disc bore of the brake disc, resulting in a compact design.

In one embodiment, the at least one first measuring module has a housing with a measuring sensor, a spring assembly and a fastening element. The spring assembly preferably has disc springs. Sensor and spring assembly are axially displaceable in the housing and are assembled and held under pretension.

Furthermore, it is provided that the sensor has a force introduction element which projects out of the housing. Thus, it is advantageously possible that the sensor is displaceable into the housing against the force of the spring assembly when exceeding a previously determinable force with which the force introduction element is acted upon. In this way, the power flow of small forces due to grinding moments, ie small torques, passes through the measuring sensor of the measuring module. Larger torques produce larger forces, in which the force introduction element is sunk in the housing. Then the power flow passes through the housing and of course through the bridging elements whose play is bridged. In one embodiment, the sensor is a load cell. This is a component that is cost-effectively available in the market in high quality.

In a still further embodiment, the housing has a fastening element for fastening the at least one first measuring module. This can e.g. a screw or a threaded bolt, whereby a simple fixation is possible.

In addition, it is provided that the measuring device has at least one second measuring module for indirect torque measurement in a brake pad and / or a brake pad carrier. This puts a second measuring system indirectly in the braking covering, with which tangential forces can be measured, which are available as redundant measured values.

Here, the at least one second measuring module is arranged in the brake pad carrier and cooperates with a brake carrier of the disc brake. In this case, the at least one second measuring module has a structure as the at least one first measuring module. A fastener is not necessary because the second measuring module can be inserted into a matching bore whose bottom forms an axial stop. For protection, e.g. a grub screw can be used.

In one embodiment of the method, measured values of at least three measuring modules are detected in method step (S2) by detecting measured values of a torque. It is preferred that three measuring modules are used. Thus, a measurement accuracy can be increased.

In a further embodiment, in method step (S2), acquisition of measured values of a torque results in the acquisition of measured values of a tangential force between at least one brake pad and / or brake pad carrier and the brake carrier of the disc brake. Thus, a redundant measurement becomes possible, whereby the accuracy and reliability is further increased.

For a further increase in reliability, it is provided that, in method step (S2), acquisition of measured values of a torque, detection of signal values of distance sensors between brake pad carrier and a reaction-side saddle back of a brake caliper and / or between brake pad carrier and thrust pieces or thread tamping on the application side of Disc brake is done.

In one embodiment of the method, it is provided that in method step (S3) evaluation of the measured values as grinding torque on the basis of the evaluation, an indication and / or forwarding of data for initiating measures for reducing and stopping the measured grinding torque to a brake control unit. After, for example, measures have been taken by the brake control unit to stop the grinding torque, the results can be checked with the measuring device, wherein the measures can be applied repeatedly. In this way, grinding torques can be completely eliminated. The disc brake forms a reliable arrangement with the measuring device for grinding torque measurement, the following advantages can be achieved:

Recording of the actually occurring residual grinding torques

 Measurement under operating conditions / service braking

 Direct comparison of remedial measures

 Redundancy measurements of the reaction forces in the brake lining

The invention will now be described by way of example with reference to the accompanying drawings. Hereby show:

Fig. 1 is a schematic partial sectional view of an inventive

 Disc brake with a measuring device according to the invention; FIG. 2 is a schematic perspective view of an exemplary embodiment of a measuring module; FIG.

FIG. 3 is a schematic sectional view of the measuring module according to FIG. 2; FIG. 4 is a schematic perspective view of a brake disk;

Fig. 5 is a schematic perspective view of an adapter;

6 shows a schematic perspective view of a brake disk assembly with the brake disk according to FIG. 4 and the adapter according to FIG. 5;

FIG. 7 shows a schematic side view of the brake disk arrangement according to FIG. 6; FIG.

Fig. 8 is a schematic partial sectional view of the brake disk assembly of Fig. 6;

Fig. 9 is a schematic, enlarged side view of the mark

 IX of the brake disk assembly of Fig. 7;

Fig. 10 is a schematic perspective view of a brake pad; and Fig. 1 1 is a schematic flow diagram of a method according to the invention.

1 shows a schematic partial sectional view of a disc brake 1 according to the invention with a measuring device 10 according to the invention.

The disk brake 1 has a brake disk 2 with a brake disk axis 2 a. The brake disk 2 is overlapped by a, designed here as a floating caliper 4 caliper. The caliper 4 is slidably mounted on a brake carrier 4a. On both sides of the brake disk 2, a brake lining 3 is arranged, each with a brake pad carrier 3a. The disc brake 1 is here designed as a two-part brake with two spindle units 5 and 5 ', each with a threaded stem 6, 6'. The right side in FIG. 1 side of the disc brake 1 is called Zuspannseite A and the left side is referred to as lining shaft side B.

The application-side brake pad carrier 3a is connected to the spindle units 5, 5 'at the ends of the thread tamps 6, 6' via pressure pieces 6a, 6'a in connection. The other brake pad carrier 3a is also called the reaction-side brake pad carrier 3a and is fixed on the other side of the brake disk 2 in the brake caliper 4. The threaded dies 6, 6 'are each arranged rotatable in threads in a traverse 7.

The traverse 7 and thus the threaded pistons 6, 6 'are actuated by an application device, in this case an unspecified brake rotary lever with a pivot axis perpendicular to the brake disk axis 2 a and thus adjustable in the direction of the brake disk axis 2 a. A movement on the brake disc 2 is referred to as Zuspannbewegung, and a movement in the opposite direction is called release movement. A not further explained return spring is received in the middle of the traverse 7 in a corresponding recess on the lining side of the cross member 7 and is supported on the brake caliper 4 from. By means of the return spring, the traverse 7 is adjusted in the release movement in the position shown in Fig. 1 dissolved position of the disc brake 1.

A distance between the brake pads 6 and the brake disc 2 in the released position is referred to as a clearance. As a result of lining and disc wear this clearance is larger.

In this example, an adjusting device 8, which is coupled to a driver 8 'by means of a synchronization unit, for wear adjustment of a before specified clearance, which is referred to as nominal clearance, provided. The predetermined clearance is determined by the geometry of the disc brake 1 and has a so-called constructive clearance, in other words, the wear adjusting device 30 reduces an existing clearance when this is related to a previously set clearance is too big.

The adjusting device 8 is arranged on the one spindle unit 5 coaxial therewith. In the example shown, the adjusting device 8 is inserted into the threaded spindle 6. The description of such an adjustment device 8 is e.g. to refer to the document DE 10 2004 037 771 A1.

The driver 8 'is coaxial with the other spindle unit 5' arranged in the threaded spindle 6 ', with which the driver 8' is in operative connection. The adjusting device 8 is connected via an unspecified drive with the brake rotary lever in cooperation. A Verstelldrehbewegung the adjusting device 8 is transmitted via the synchronization unit 9 on the driver 8 '. In this example, the synchronization unit 9 is equipped with a chain transmission. Of course, other transmissions can be used.

The disc brake 1 may have different power drives. The brake rotary lever is here shown e.g. pneumatically operated. For construction and function of a pneumatic disc brake 1 with further detailed description, reference is made to the document DE 40 32 886 A1.

Depending on the system, a grinding torque can be generated by the floatingly mounted caliper 4 with tensioning unit, by the displaceably mounted brake linings 3 and also by a so-called disk impact of the brake disk 2. It is e.g. a brake pad 3 or a part of a brake pad 3 still on the brake disc 2 and can as a grinding torque, which is also referred to as residual grinding torque produce. The residual grinding torque counteracts the rotational movement of the brake disk 2 about the brake disk axis 2a. In Fig. 1, a main direction of rotation of the brake disc 2 is indicated by an arrow, which prevails, for example, when driving forwards a vehicle that is equipped with the disc brake 1 Tet. This arrow points in the so-called expiring direction.

In order to detect such an abrading torque, the disc brake 1 has the measuring device 10. The measuring device 10 for grinding torque measurement comprises at least a first measuring module 1 1, a transmission unit 12 and an evaluation unit 13.

The first measuring module 1 1, which will be described in detail below, is arranged in this embodiment between the brake disc 2 and one / a Achsflansch / axle, not shown, of a vehicle having the disc brake 1. The measuring module 1 1 detects a torque in the power flow between the brake disk 2 and the connection of the brake disk 2 to the axle flange, not shown here, to which the disk brake 1 is attached. The measured values of the torque detected by the measuring module 1 1 are processed by the measuring module 1 1 and transmitted as measuring signals to the transmission unit 12. For this purpose, the measuring module 1 1 corresponding measuring amplifier, pulse shaper, etc. have. For example, For example, the measuring module 1 1 can digitize the measuring signals and then transmit them, which ensures high interference immunity. The transmission unit 12 transmits supply energy e.g. in the form of electrical energy to the measuring module 1 1 and receives the prepared by the measuring module 1 1 and sent measuring signals. The measuring module 1 1 can be used e.g. be designed in the manner of an RFID unit. Of course, it is also conceivable that the measuring module 1 1 receives 12 electrical energy for supply by other wireless transmission from the transmission unit.

The measurement signals 12, which are received by the transmission unit 12, are further processed by the transmission unit 12 for transmission to the evaluation unit 13.

The evaluation unit 13 processes the measurement signals thus obtained for output to a display for a driver of the vehicle, which is equipped with the disc brake 1. The evaluation unit 13 can also be connected to a brake control unit, not shown here, of the disc brake 1 and forward the evaluated measured signals to the brake control unit for further processing. The brake control unit can thus initiate appropriate measures for stopping a sliding brake pad 3 on the brake disc 2, such as an automatic tensioning and releasing the disc brake 1 at standstill of the vehicle. In this embodiment, the brake disc 2 is part of a brake disc assembly 20, which will be explained in more detail below in connection with FIGS. 6 and 7. In this case, the brake disk 2 is coupled to the axle flange, not shown, via an adapter 21. Here are preferably three first measuring modules 1 1 in the Brake disc assembly 20 disposed between the brake disc 2 and the adapter 21.

Fig. 1 also shows a second measuring module 1 1 ', which is shown here in the application-side brake pad 3 is arranged. Another second measuring module 1 1 'may be arranged in the reaction-side brake pad 3. The second measuring module 1 1 'detects a reaction force between the brake lining 3 or brake lining carrier 3 a and the brake carrier 4 a, on which the brake lining 3 or brake lining carrier 3 is supported expiring. This reaction force is created not only during braking but also in the case of an existing grinding torque due to a reaction torque. In this case, the dragging brake pad 3 is taken along by the friction forces occurring in the tangential direction of the brake disk 2 and pressed against the brake carrier 4a. The reaction force generated thereby can be detected with the further / further measuring module / measuring modules 1 1 '. Thus, the measuring device 10 is designed as a redundant measuring system. The first measuring modules 1 1 detect in direct measurement grinding moments on the brake disc 2 and in indirect measurement grinding moments as reaction moments between the / the brake pad / brake pads 3 and the brake carrier 4a. All measuring modules 1 1, 1 1 'are in cooperation with the transmission unit 12. From the respective measurement signals in the evaluation unit 13, the current grinding torque is evaluated.

In both cases, the basic measuring system with the measuring module 1 1 is designed so that by means of e.g. small forces can be detected corresponding force load cells, it comes with a crossing of the maximum measuring range of these load cells to a mechanical bypass of the power flow, thereby larger forces can be transmitted without overloading the load cells or damaging.

2 shows a schematic perspective view of an exemplary embodiment of a measuring module 11. 3 shows a schematic sectional view of the measuring module 1 1 according to FIG. 2. The basic measuring module or measuring module 1 1 comprises a cylindrical housing 14, a measuring sensor 15, a spring assembly 17 and a fastening element 18.

A longitudinal axis of the measuring module 1 1 is provided with the reference numeral 1 1 a. The circular cylindrical housing 14 has a circular cylindrical interior 14a with a front opening 14b and a mounting opening 14c in a rear wall 14d opposite the front opening 14b. In addition, the wall of the housing 14, starting from the front opening 14b in the direction of the longitudinal axis 1 1 a with an unmarked slot-shaped recess is broken, which extends approximately over half the length of the housing 14.

In the circular cylindrical interior 14a of the housing 14, the fastening element 18, here a threaded bolt with a head portion 18a and a threaded portion 18b, is used. In this case, an outer diameter of the head portion 18a is greater than the attachment opening 14c, so that the head portion 18a of the fastening element 18 rests against the rear wall 14d of the housing 14 in the inner space 14a and the threaded portion 18b of the fastening element 18 through the attachment opening 14c in the direction of the longitudinal axis 1 1 a extends to the outside. The fastener 18 is axially held and secured in the housing 14 by means of a nut 19 applied to the threaded portion 18b. The nut 19 may e.g. a locknut or / and be combined with corresponding security elements against loosening. By means of the threaded section 18b of the fastening element 18, the measuring module 11 can be fixed in a measuring setup, which will be described in detail below (FIG. 9). Starting from the head portion 18a of the fastening element 18, the spring assembly 17 and the sensor 15 are adjacent to each other and contacting each other under axial bias, which will be explained below, arranged in the interior 14a of the housing 14. The spring assembly 17 is formed here with disc springs. Between the sensor 15 and the Federpaket17 an intermediate ring 17a is arranged. Also, an intermediate ring 17 b is provided between the spring assembly 17 and the head portion 18 a of the fastening element 18. The sensor 15 is here designed as a load cell in miniature construction and has a, which protrudes from a front side 15 b of the sensor 15. A rear side 15c of the sensor 15 is in contact with the intermediate ring 17a of the spring assembly 17. A connection 15d of the sensor 15 shown only schematically protrudes radially from the wall of the sensor 15 and extends radially through the slot-shaped recess (FIG. 2) of the wall of the housing 14.

The sensor 15 and the spring assembly 17 with the intermediate rings 17a, b are arranged axially displaceably in the inner space 14a of the housing 14. It is the sensor 15 when installed in the interior 14a of the housing 14 against the axial force of the spring assembly 17 pressed by a locking ring 16 under axial bias. By means of the fastening element 18 and the nut 19, the bias can still be varied. The securing ring 16 is inserted in the region of the front opening 14b of the housing 14 into a groove formed in the wall of the inner space 14a and contacts the front side 15b of the measuring sensor 15. The pin-shaped force introduction element 15a is in the axial direction of the longitudinal axis 11a by a specific axial Length from the front opening 14b forth, which is particularly evident in Fig. 3 clearly. In the test setup described in more detail below, the measuring module 1 1 is fixed. A force is introduced into the measuring module 1 1 via the force introduction element 15a in the sensor 15 in the direction of the longitudinal axis 1 1 a. A force-introducing surface, for example, the brake disc 2 (stop 22c in Fig. 9), which contacts the force introduction element 15a is greater than the front opening 14b of the housing 14. In this case, the sensor 15 is axially displaced with increasing force against the spring pact 17 until the maximum force measuring range of the sensor 15 is achieved. In this point, the force introduction element 15a is axially displaced into the inner space 14a of the housing 14 so that the force sensing front contact surface of the force introduction element 15 is flush with the front of the housing 14 at the front opening 14b and the force introducing surface at the edge of the front opening 14b of the housing 14th comes to the edition. The flow of force through the adjacent components is guided so that a Kraftflussüberbrückung of the sensor 15 takes place. The spring assembly 17 must be matched to the measuring range of the sensor 15.

In the following, the measurement setup with the first measurement module 1 1 will be explained. 4 shows a schematic perspective view of the brake disk 2. FIG. 5 shows a schematic perspective view of an adapter 21. FIG. 6 shows a schematic perspective view of a brake disk assembly 20 with the brake disk 2 according to FIG. 4 and the adapter 21 Fig. 5 is shown. FIG. 7 shows a schematic side view of the brake disk arrangement 20 according to FIG. 6.

In this measuring setup for the direct measurement of the grinding torque of the brake disk 2 with the measuring device 10, the measuring structure has the brake disk assembly 20 (FIG. 6). The brake disk assembly 20 includes the here two parts brake disk 2 with an adapter 21st The brake disk 2 has in its disk bore 2b a disk receiving profile 22 which communicates with a receiving profile 24 of the adapter 21 as a counterpart. In Fig. 4, the brake disc 2 is shown with the disc receiving profile 22, wherein a plurality of Circumference of the inner bore 2b distributed disc receiving profiles 22 are arranged, each having two tooth portions 22a. Between the tooth portions 22a, an arc portion 22b is arranged, which connects the tooth portions 22a at their feet. The adapter 21 shown in Fig. 5 has a flange as a fixing portion 21 for attachment to the Achsflansch the associated vehicle. An attachment portion 21 opposite to the receiving portion 21 a is connected by a cylindrical central portion 21 c with the attachment portion 21. The receiving portion 21 b is formed at its periphery with radially outwardly extending receiving profiles 24 and coupling profiles 24 a. Here, three receiving profiles 24 are provided with measuring module receptacles 23.

The receiving profiles 24 and the coupling profiles 24a have a same outer diameter. Their tops all have the same outer diameter and are provided to the central portion 21 c out, each with a radially outwardly extending web. The coupling profiles 24a are each provided in their middle with a cavity which is open towards the top and to the outside of the receiving portion 21b facing in the radial direction and has an approximately semicircular cross-section. In contrast to the coupling profiles 24a, the receiving profiles are about half as long in axial length as the coupling profiles 24a, with the rear sides facing the middle section 21c being aligned with those of the coupling profiles 24a. The pointing to the outside of the receiving portion 21 b sides of the receiving profiles 24 are axially offset from the edge of the receiving portion 21 b to the central portion 21 c to about half the axial length of the coupling portions 24a, so that from the edge of the receiving portion 21 b to the receiving profiles 24th gives a free space in which a measuring module 1 1 is arranged (see FIGS. 7 and 9).

The measuring module receptacle 23 is designed as a web, which extends here in Fig. 5 at the left edge of a receiving profile 24 from the edge region of the receiving portion 21 b along the space defined for the measuring module 1 1 free space axially to the receiving profile 24 and is connected thereto. The measuring module receptacle 23 has a bore for attachment of the measuring module 1 1 (see FIGS. 8 and 9), wherein the measuring module 1 1 is arranged tangentially to the receiving portion 21 b.

The receiving portion 21 b is used to attach the adapter 21 in the brake disc 2, which Fig. 6 and 7 represent. The receiving portion 21b is inserted in the disc bore 2b of the brake disc 2 so that the disc receiving profiles 22 of the brake disc 2 in the spaces between the recording profiles 24 and coupling profiles 24a of the receiving portion 21 b of the adapter 21 are arranged. In this case, three measuring modules 1 1 are regularly distributed on the circumference of the receiving portion 21 b of the adapter 21 and the disc bore 2 b of the brake disc 2, as shown in FIG. 7. The three measuring modules 1 1 are arranged in the brake disk assembly 20 so that there is a three-point bearing and the torques of the brake disc 2 are transmitted tangentially to the measuring modules 1 1.

8 shows a schematic partial sectional view of the brake disk assembly 30 according to FIG. 6, and FIG. 9 shows a schematic, enlarged side view of the mark IX of the brake disk assembly 20 according to FIG. 7.

The brake disk 2 is rotatably mounted on the receiving profiles 24 and coupling profiles 24a of the adapter 21 by means of a thin-film bearing 25 and thereby rotationally movable relative to the adapter 21, as can be seen in Fig. 8. The thin-ring bearing 25 is arranged on the outer diameter or the surfaces of the receiving profiles 24 and coupling profiles 24a of the adapter 21 between the respective webs and a shoulder in the disk bore 2b of the brake disk 2. In addition, the brake disk 2 is held secured on the adapter 21 axially by an axial securing element 26, which is arranged in a groove on the circumference of the receiving portion 21 b of the adapter 21.

In Fig. 8, moreover, the axial, i. Detecting parallel to the brake disc axis 2a extending measuring module receptacle 23, in which the measuring module 1 1 is fastened with its fastening element 18. This is shown enlarged in a side view in FIG. The threaded portion 18b of the fastener 18 of the measuring module 1 1 extends with its free end through the bore of the Meßmodulaufnahme 23 and is fixed on both sides with nuts 19a and 19b. With these nuts 19a, 19b and an axial position of the measuring module 1 1 in its longitudinal axis 1 1 a is adjustable. It can be used for a position adjustment of the measuring module 1 1 in the longitudinal axis 1 1 a and spacer sleeves and / or discs use.

Fig. 8 further shows that the force introduction element 15a interacts with a stop 22c. The stopper 22c is connected to a toothed portion 22a of the associated disk receiving profile 22 of the brake disk 2 and extends axially in the direction of the brake disk axis 2a. The contact surface of the stopper 22 c, which cooperates with the force introduction element 15 a of the measuring module 1 1, runs parallel to the measuring module receptacle 23 of the adapter 21. The rotatory movement possibility of the brake disk 2 on the adapter 21 by means of the thin-film bearing 25 is limited by a corresponding play in bridging elements 27 (FIG. 9). The bridging elements 27 transmit the corresponding braking torque from the disc receiving profiles 22 of the brake disc 2 to the coupling profiles 24a of the adapter 21 and thus to the axis of the associated vehicle. The bridging elements 27 have, on the one hand, a profile matching the disc receiving profiles 22 of the brake disc 2 and, on the other hand, a profile communicating with the coupling profiles 24a of the adapter 21. In addition, these profiles of the bridging elements 27 are formed with a certain play in the tangential direction of the brake disc 2, which is set so that small torques of the brake disc 2, ie moments in the order of grinding moments, on the stops 22c in the force application elements 15a of the sensor 15 of the measuring modules 1 1 must be initiated and work against the spring assemblies 17. From a certain torque, the sensor 15 of the measuring modules 1 1 are sunk in their housings 14 as described above, the game of bridging elements 27 is bridged, and the moments of the brake disc 2 are transmitted via the disc receiving profiles 22 on the coupling profiles 24 a of the adapter 21. The specific play of the transmission elements 27 must be adapted to the characteristic of the spring assemblies 17. In this case, the measuring ranges of the measuring sensors 15 of the measuring modules 11 are also to be taken into account.

In Fig. 10 is a schematic perspective view of a brake pad 3 is shown.

The brake pad 3 is here equipped with second measuring modules 1 1 '. In this example of a second measuring system for the measuring device 10 for the indirect detection of an grinding torque, two second measuring modules 11 'are inserted in the brake lining carrier 3a of the brake lining 3 in the region of one side of the brake lining carrier 3a. This side of the brake pad carrier 3a is the one with which the brake pad carrier 3a is supported in the brake carrier 4a in order to derive the braking torques into the vehicle body. As described above, the force introduction elements 15a are arranged protruding from the housings 14 of the measuring modules 11 'and contact a so-called brake carrier horn of the brake carrier 4a of the disc brake 1. Within the scope of the respective spring package characteristic curves, these second measuring modules 1 1 'can detect tangential forces on the brake pad 3 or brake pad carrier 3 a, which are generated by grinding moments. After exceeding a maximum force of the tangential forces, for example during a braking operation, the brake lining carrier 3a bears against the brake carrier 4a, the force introduction elements 15a having previously been sunk in the housings 14 of the second measuring modules 11 '. Thus, then a Kraftflussüberbrückung by conditioning the side of the brake pad carrier 3a on the brake carrier 4a.

The structure of the second measuring modules 1 1 'corresponds to the structure of the measuring modules 1 1 except for the fastening element 18. The second measuring modules 1 1' can be fixed in various other ways in receiving bores of the brake pad carrier 3 a.

Furthermore, Fig. 10 shows two distance sensors 28 which are inserted in the back of the brake pad carrier 3a. With the aid of these distance sensors 28, the distance to the saddle back in the reaction-side brake pad carrier 3a or to the pressure pieces 6a, 6'a on the application side can be detected.

Finally, FIG. 11 shows a schematic flow diagram of a method according to the invention.

The method for measuring a grinding torque of a disc brake has a first method step S1, in which an operating state of the disc brake 1 is detected. Thereby, e.g. Signals and data of a brake control device of the disc brake and vehicle data such. Driving condition come to the evaluation.

In a second method step S2, a torque is measured directly between the brake disk 2 of the disk brake 1 and the associated axle or the associated axle flange when an operating condition exists without a brake application. In this case, the measurement setup described above with the brake disk assembly 20 with the adapter 21 is used. There are three measurement signals from each one measuring module 1 1 detected. In addition, when a maximum value of the torque is exceeded, a Kraftflussüberbrückung the torque detection is made.

In one variant, tangential forces between at least one brake lining carrier 3a and the brake carrier 4a of the disc brake 1 are detected for indirectly measuring the grinding torque. In addition, signal values of distance sensors 28 between the brake pad carrier 3a and the reaction-side saddle back of the caliper 4 and / or between brake pad carrier 3a and the pressure pieces 6a, 6'a and the thread tamps 6, 6 'on the application side of the disc brake 1 can be detected. Evaluation of the measurement signals as the grinding torque of the disc brake takes place in a third method step S3. One measurement signal or several measurement signals of the direct measurement can be evaluated. In addition, it is possible to determine the current grinding torque from the tangential forces as well as from the measuring signals of the distance sensors 28 on the basis of the measured signals of the indirect measured values or to indicate a measured value of the current grinding torque of the disk brake 1 with high accuracy.

In addition, in the third method step S3, the detected measured value of the current grinding torque can be used for further measures. Further measures are, for example, displaying the grinding torque for a driver of the vehicle with the disc brake 1 and / or initiating braking during a standstill of the vehicle and the like. In addition, it can be determined by such measures by means of the method, whether these measures have reduced the grinding torque or turned off.

The measuring device 10 is designed for measuring an grinding torque of a pneumatically applied disc brakes in the commercial vehicle sector, but can also be used in all other applications where detection and measurement of a grinding torque of a brake is necessary.

The embodiments described above do not limit the invention, which is modifiable within the scope of the appended claims.

So it is e.g. possible that the attachment of the measuring module (1 1) is provided on a disc receiving profile 22 of the brake disc 2, in which case the stop 22 c is arranged on the receiving profile 24 of the adapter 21 for cooperation with the force introduction element 15 a of the measuring sensor 15.

Thus, it is also conceivable that each measuring module 1 1, 1 1 'cooperates with its own transmission unit 12.

The transmission unit (s) can also be designed together with the evaluation unit or form alone or together with the evaluation unit a component of a brake control unit.

It is possible that the measuring sensor 15 is designed with its own measuring amplifier and its own measuring data processing unit. The terminal 15d of the sensor 15 may be connected to another separate rotating transmission unit wirelessly or otherwise connected to the stationary transmission unit 12.

LIST OF REFERENCE NUMBERS

1 disc brake

 2 brake disc

 2a brake disc axle

2b disc bore

 3 brake pad

 3a brake pad carrier

4 caliper

 4a brake carrier

 5, 5 'spindle unit

 6, 6 'threaded bolt

 6a, 6'a pressure piece

 8 adjusting device

8 'driver

 9 synchronization unit

10 measuring device

 1 1, 1 1 'measuring module

 1 1 a longitudinal axis

 12 transmission unit

13 evaluation unit

 14 housing

 14a interior

 14b front opening

 14c mounting hole

14d back wall

 15 sensors

 15a force introduction element

15b front

 15c back

 15d connection

 16 circlip

 17 spring pack

 17a, 17b intermediate ring

 18 fastener

18a head section

 18b threaded section

19, 19a, 19b mother

 20 brake disc assembly

21 adapters 21 a attachment section

21 b receiving section

21 c middle section

 21 d Adapter hole

 22 disk mounting profile

22a tooth section

 22b bow section

 22c stop

 23 measuring module recording

24 recording profile

 24a coupling profile

 25 thin ring bearings

 26 axial securing element

27 bridging element

28 distance sensor

 S1 ... S3 process step

Claims

claims Disc brake (1), in particular for a motor vehicle, with a measuring device (10) for grinding torque measurement between a brake disc (2) and at least one brake pad (3) of the disc brake (1), wherein the measuring device (10) at least one first measuring module (1 1 ) for a direct torque measurement between the brake disc (2) and one / a Achsflansch / axis of a disc brake (1) attributable vehicle. Measuring device according to claim 1, characterized in that the brake disc (2) is coupled via an adapter (21) to the axle flange / axle of the disc brake (1) to be assigned to the vehicle, the brake disc (2) and the adapter (21). a brake disc assembly (20) form, in which the at least one first measuring module (1 1) for the direct torque measurement between the brake disc (2) and the adapter (21) is provided. Measuring device according to claim 2, characterized in that the adapter (21) has a fixing portion (21 a) for attachment to an axis to be assigned, a receiving portion (21 b) for connection to the brake disc (2) and a central portion (21 c) the attachment portion (21 a) and the receiving portion (21 b) connects. Measuring device according to claim 3, characterized in that the receiving portion (21 b) of the adapter (21) at least one receiving profile (24) for cooperation with the at least one first measuring module (1 1) and coupling profiles (24 a) for coupling with disc receiving profiles (22). the brake disc (2), wherein the at least one receiving profile (24) and the coupling profiles (24a) are provided for receiving and / or mounting the brake disc (2). Measuring device according to claim 4, characterized in that at least one disc receiving profile (22) of the brake disc (2) has a stop (22c) for cooperation with the at least one first measuring module (1 1). Measuring device according to claim 4 or 5, characterized in that the coupling profiles (24a) of the adapter (21) and the disc receiving profiles (22) the brake disc (2) are coupled with bridging elements (27) which have a previously determinable game. Measuring device according to claim 6, characterized in that the at least one first measuring module (1 1) is designed for the direct torque measurement for small torques in the range of grinding moments and when exceeding a pre-definable torque by means of the bridging elements (27) between the brake disc ( 2) and the adapter (21) can be bridged. Measuring device according to one of claims 2 to 7, characterized in that the receiving portion (21 b) of the adapter (21) in a disc bore (2b) of the brake disc (2) is accommodated. Measuring device according to one of the preceding claims, characterized in that the at least one first measuring module (1 1) comprises a housing (14) with a sensor (15), a spring assembly (17) and a fastening element (18). Measuring device according to claim 9, characterized in that the spring assembly (17) has cup springs. 1 1. Measuring device according to claim 9 or 10, characterized in that the sensor (15) has a force introduction element (15a) which protrudes from the housing (14). 12. Measuring device according to claim 1 1, characterized in that the sensor (15) is displaceable in the housing (14) against the force of the spring assembly (17) when exceeding a previously determinable force with which the force introduction element (15a) is acted upon , 13. Measuring device according to one of claims 9 to 12, characterized in that the sensor (15) is a load cell. Measuring device according to one of claims 9 to 13, characterized in that the housing (14) has a fastening element (18) for fastening the at least one first measuring module (1 1). 15. Measuring device according to one of the preceding claims, characterized in that the measuring device (10) at least a second measuring Module (1 1 ') for indirect torque measurement in a brake pad (3) o- / / and a brake pad carrier (3a). Measuring device according to claim 15, characterized in that the at least one second measuring module (1 1 ') in the brake pad carrier (3a) is arranged and with a brake carrier (4a) of the disc brake (1) cooperates. 17. Measuring device according to 15 or 16, characterized in that the at least one second measuring module (1 1 ') has a structure as the at least one first measuring module (1 1). 18. A method for measuring an grinding torque of a disc brake (1) according to claim 19, characterized by the following method steps:  (S1) determining operating states of the disc brake (1);  (S2) detecting measured values of a torque between the brake disk (2) of the disk brake (1) and the associated axle or the associated axle flange when a detected operating state of the disk brake (1) is an operating condition without brake operation; and  (S3) Evaluation of the measured values as grinding torque of the disc brake  (1 )- 19. The method according to claim 18, characterized in that in method step (S2) detecting measured values of a torque measured values of at least three measuring modules (1 1) are detected. 20. The method according to claim 18 or 19, characterized in that in the method step (S2) detecting measured values of a torque, detecting measured values of a tangential force between at least one  Brake lining (3) and / or brake pad carrier (3a) and the brake carrier (4a) of the disc brake (1). 21. Method according to one of claims 18 to 20, characterized in that in method step (S2) detecting measured values of a torque detecting signal values of distance sensors (28) between the brake pad carrier (3a) and a reaction-side saddle back of a brake caliper (4) and / or between Brake pad carrier (3a) and thrust pieces (6a, 6'a) and threaded dies (6, 6 ') on the application side of the disc brake (1). 22. Method according to claim 18, characterized in that in method step (S3) evaluating the measured values as grinding torque on the basis of the evaluation, an indication and / or a forwarding of data for initiating measures for reducing and stopping the measured grinding torque to a brake control unit.