Multi-disk brake device for a vehicle and vehicle with the multi-disk brake device

Abstract

Multi-disk brake device (1) for a vehicle (32) with a steel plate carrier (2) and a plurality of steel plates (3), wherein the steel plates (3) are arranged on the steel plate carrier (2), and with a lining plate carrier (4) and a plurality of lining plates (5), wherein the lining plates (5) are arranged on the lining plate carrier (4), wherein the steel plates (3) and the lining plates (5) form a plate pack (8), with an actuating device (9) for generating an actuating force which axially compresses the disk pack (8) to generate a braking torque, where a cooling device (9) closed off from the plate pack (8) for cooling the steel plate carrier (2) with a coolant, wherein - the steel disc carrier (2) is designed as an internal rotor in the multi-disk brake device (1), or - the steel plate carrier (2) is designed as an inner stator and the lining plate carrier (4) is designed as an outer rotor.

Description

The invention relates to a multi-disk brake device for a vehicle having the features of claim 1.Whereas in conventional vehicles friction brakes are regularly arranged close to the wheel or assigned in a wheel-selective manner, in electric motor vehicles or hybrid vehicles new possibilities for the brake systems result due to the changes in the drive train. For example, it is known to use a centrally arranged brake in an electric drive train, which brake acts on at least two wheels of the vehicle.The document DE 10 2021 205 073 A1 discloses a passenger vehicle with an electric rear drive, having a drive system containing power electronics, an electric motor, a transmission gear and a differential gear, together forming an E-axis, and two side shafts connected to the differential gear, each of which has a rear wheel attached to their free ends, and a brake system. The brake system has a central brake which is operatively arranged within the E-axis between the E-motor and the differential gear. FR 2 820 794 A1 discloses a disk brake device having a disk carrier and a plurality of disks, wherein the disks are arranged on the disk carrier, and having a disk carrier and a plurality of disk disks, wherein the disk disks are arranged on the disk carrier, wherein the disks and the disk disks form a disk pack, and having an actuating device which presses the disk pack axially together. A cooling device with a coolant sealed off from the plate pack is present. Further prior art is disclosed in DE 10 2016 207 646 A1.It is an object of the present invention to propose a multi-disk brake device for a vehicle, which has improved functional behavior.This object is achieved by a multi-disk brake device having the features of claim 1 and by a vehicle having the features of claim 7. Preferred or advantageous embodiments of the invention are evident from the dependent claims, the following description and the attached figures.The invention relates to a multi-disk brake device which is suitable / formed for a vehicle.The vehicle is designed in particular as a hybrid vehicle or particularly preferably as a pure electric vehicle (BEV). The vehicle is implemented, for example, as a passenger car, small bus, light truck or the like. Particularly preferably, the vehicle is assigned to class M1 or N1 according to Regulation (EU) 2018 / 858. In particular, the vehicle is designed as a road vehicle and / or is permitted and / or suitable for road traffic. For example, the vehicle can reach a maximum speed of more than 80 km / h, preferably more than 120 km / h and in particular more than 140 km / h. In the most general embodiment of the invention, the vehicle may have an internal combustion engine and / or an electric drive machine for generating a traction torque and / or drive torque for the vehicle. The vehicle is particularly preferably designed as a hybrid vehicle or as a pure electric vehicle. The multi-disk brake device has in particular the function of applying a braking torque to at least one of the wheels of the vehicle.The multi-disk brake device has a steel disk carrier, wherein the steel disk carrier carries a plurality of steel disks. Particularly preferably, the steel disks are arranged displaceably in an axial direction of the disk brake device on or in the steel disk carrier. However, it is preferred that the steel plates have good thermal contact with the steel plate carrier. The steel plates carry friction surfaces, wherein the friction surfaces are preferably formed from the base material of the steel plates, namely steel. In this way, the arising brake heat at the steel plates can be dissipated particularly well and easily into the base body of the steel plates and can be passed on to the steel plate carrier via the good thermal contact.The steel disks are arranged on the steel disk carrier in a rotationally fixed manner, preferably in a rotationally fixed manner, in the circumferential direction about an axis of rotation of the disk brake device. For example, the multi-disk brake device has at least or exactly two, three or more steel disks.The multi-disk brake device has a lining disk carrier and a plurality of lining disks. The lining disks are arranged on the lining disk carrier. In particular, the lining plates are arranged on the lining plate carrier so as to be displaceable in the axial direction. The lining disks are arranged on the lining disk carrier in a rotationally fixed manner, in particular in a rotationally fixed manner in a positive-locking manner, in the circumferential direction. The lining plates preferably each have a base body on which a friction lining is formed. Alternatively, the lining plates are made of a base material which forms the friction lining with its surface.The steel plates and the lining plates form a plate pack. In particular, the steel plates and the lining plates are arranged alternately in the plate pack. In this way, friction areas are produced between the steel plates and the lining plates, wherein a friction lining can press from the lining plates onto the surface, in particular steel surface, of the steel plates.The disk brake device has an actuating device for generating an actuating force, wherein the actuating force is generated such that the disk pack is axially compressed in order to generate a braking torque. The actuating device can be designed as an electrical, electromechanical, pneumatic or particularly preferably hydraulic actuating device. The actuating force is provided in particular in the axial direction.Within the scope of the invention, it is proposed that the disk brake device has a cooling device for cooling the steel disk carrier with a coolant, in particular a liquid coolant. The cooling device is arranged on the steel plate carrier or integrated in the steel plate carrier. In particular, the steel plate carrier forms the cooling device. The coolant is in particular a liquid coolant which is guided in a flow through the cooling device in order to cool the steel disk carrier and thus the disk brake device. The cooling device is fluidically closed off with respect to the plate pack, so that the coolant cannot pass from the cooling device to the plate pack. In particular, the lamination stack is arranged outside a wet region of the cooling device and / or in a coolant-insulated manner.It is a consideration of the invention that the use of a disk brake device increases the number of friction regions and thus the diameter of the individual disks can be kept small. However, as the number of fins increases, the removal of the heat energy introduced by the braking turns out to be difficult. In order that the disks do not overheat during operation, a cooling device is provided, through which the coolant flows and which nevertheless in principle enables a dry brake system. By using the steel plates, a particularly good and efficient heat transport from the friction regions to the cooling device can take place. A disk brake device which is improved in its functional behavior can thus be formed.In a preferred embodiment of the invention, the steel plate carrier is designed as an inner plate carrier. The lining disk carrier, on the other hand, is designed as an outer disk carrier. In this embodiment, the cooling device is arranged radially inside the disk pack.According to an alternative of the invention, the steel disk carrier is designed as an inner rotor in the disk brake device. It is thus provided that the steel disk carrier rotates in the disk brake device, whereas the lining disk carrier is preferably arranged stationary. Preferably, the cooling device is integrated in the steel plate carrier, so that the cooling device also rotates completely or at least partially.For example, the steel plate carrier, in particular the inner rotor, can be designed as a hub, wherein the hub has receptacles for the steel plates on the radial outer side and the cooling device radially on the inside.It is particularly preferred that the multi-disk brake device has a rotary feedthrough for supplying the coolant via the inner rotor and / or the hub. In this way, the coolant can be introduced into the rotating inner rotor or the rotating hub. For example, an axially extending bore is formed in the inner rotor or in the hub, which bore is supplied via a stationary section of the rotary feedthrough for supplying the coolant. In this way, the coolant can be supplied in a simple manner in a process-safe manner.It is preferred that the inner rotor has a circular ring groove for guiding the coolant in the inner rotor, wherein the circular ring groove has a circular ring-shaped axial opening. The circular ring groove and / or the circular ring-shaped axial opening is or are arranged coaxially to the axis of rotation of the multi-disk brake device.Furthermore, the multi-disk brake device has a covering device, wherein the covering device is arranged in a stationary manner. For example, the covering device is arranged on a brake housing of the multi-disk brake device. The covering device is designed to seal the annular axial opening and to form a return for the coolant. For example, the covering device has one or more axial passages via which the coolant can be returned. The brake housing preferably has at least or exactly one return opening, which is formed in a manner complementary to the passage and via which the coolant can be returned. The circular ring groove with the covering device forms the cooling device in the inner rotor.In a preferred structural embodiment of the invention, the covering device is designed as a circular ring disk. For example, the covering device can be designed as a plastic part or as a sheet metal part. An inner sealing collar is arranged on the inner periphery, wherein the inner sealing collar extends in the axial direction. The inner rotor has an inner groove which is designed to receive the inner sealing collar. The inner groove and the inner sealing collar together form an inner labyrinth seal, so that the circular ring groove is sealed radially inward. Alternatively or additionally, an outer sealing collar is arranged on the outer periphery of the covering device, which collar likewise extends in the axial direction. The inner rotor has an outer groove for receiving the outer sealing collar. The outer groove and the outer sealing collar together form an outer labyrinth seal, so that the circular ring groove is sealed radially outwards. The passage can be introduced into the circular ring disk, which represents the return for the coolant.According to a further alternative of the invention, the steel disk carrier is designed as an inner stator, while the lining disk carrier is realized as an outer rotor. In this embodiment, the lining disk carrier is connected to the hub of a feed shaft or to the feed shaft in a rotationally fixed manner. This embodiment has the advantage that the steel plate carrier can be cooled particularly easily with the cooling device, since the rotary feedthrough can be dispensed with.In another embodiment of the invention, it is provided that the steel plate carrier is designed as an outer stator and the lining plate carrier is realized as an inner rotor. This embodiment can be implemented particularly easily in that the steel disk carrier and the cooling device together form the brake housing for the disk brake device. On the other hand, it is advantageous to arrange the lining plate carrier with the lining plates radially inward; this arrangement would have the advantage that the lining plates are on the smallest possible diameter, which can bring an advantage with a view to a risk of the lining plates bursting in the event of overloading.The multi-disk brake device preferably has the brake housing, wherein the disk pack is encapsulated in the brake housing in particular in a dust-tight manner, so that fine dust emission of brake abrasion is prevented.A further subject matter of the invention relates to a vehicle having the multi-disk brake device as described above or according to one of the preceding claims.A further, optional subject matter of the invention relates to a drive arrangement for a or the vehicle. The drive arrangement has a functional assembly with a housing and the multi-disk brake device as described above, wherein the multi-disk brake device is preferably fixed to the housing as a self-holding module. In particular, the brake housing can be flanged to the housing of the functional assembly.Particularly preferably, the functional assembly is connected and / or connectable to a coolant circuit, wherein the multi-disk brake device is indirectly fluidically connectable and / or connected to the coolant circuit via the functional assembly. This further development enables the multi-disk brake device not to require its own connection construction for the coolant circuit, but to be supplied with it by the functional assembly.The functional assembly is particularly preferably designed as a differential or as an electric axle.In the event that the functional assembly is designed as a differential, the multi-disk brake device can be operatively connected to an input of the differential. In this case, both outputs of the differential can be braked via a single disk brake device. Alternatively, the drive arrangement has two of the multi-disk brake devices, wherein each output is assigned a multi-disk brake device. In this configuration, the outputs can be acted upon by different braking torques, so that the multi-disk brake devices brake actuators for torque vectoring, i.e. a controlled distribution of the driving torque and / or the braking torque to the wheels operatively connected to the outputs, can be implemented. The activation is effected, for example, by a corresponding control device.In the event that the functional assembly is designed as an electric axle, the electric axle can have an electric machine and optionally additionally a transmission, wherein the transmission is arranged in a drive torque path behind the electric machine. The transmission is designed in particular to reduce the rotational speed and / or to translate the deceleration from the speed. In particular, it is a reduction gear. The multi-disk brake device can be connected and / or connectable in a rotationally fixed manner to the rotor shaft of the electric machine, for example, so that the rotational speed of the rotor shaft and of the brake drum is the same in the connected state. This has the advantage that the rotational speeds are comparatively high, so that only low braking torques have to be used. Alternatively and with the same advantage, the multi-disk brake device can be operatively connected to an input of the transmission. It is also possible that the multi-disk brake device is arranged between the transmission and the differential and acts on the output of the transmission or the input of the differential.A further subject matter of the invention relates to a vehicle as described above, wherein the vehicle has at least one multi-disk brake device as described above. The multi-disk brake device can be arranged, for example, in a wheel-selective or axle-selective manner. Thus, the individual wheels, in particular the driven wheels and / or the non-driven wheels, can each be assigned a multi-disk brake device of this type. It can also be provided that a vehicle axle is assigned in its entirety a corresponding multi-disk brake device which acts on both wheels of the vehicle axle. The vehicle axle can be designed as a driven or as a passive vehicle axle.In a preferred development of the invention, the vehicle has the drive arrangement, wherein the multi-disk brake device in the drive arrangement is designed as a central brake. In particular, the multi-disk brake device acts on all wheels of the vehicle, which are driven and / or can be driven by the drive arrangement. In particular, the central brake acts on at least or exactly two driven wheels of the vehicle, wherein the at least or exactly two driven wheels of the vehicle are distributed in particular on two longitudinal sides of the vehicle. The brake device preferably rotates at the rotor speed.The multi-disk brake device is designed in particular as a dynamic multi-disk brake device and / or as a multi-disk brake device for actuation during the driving operation of the vehicle. In particular, the multi-disk brake device is not designed as a parking brake or at least not as a pure parking brake.Starting from the multi-disk brake device, a braking torque path runs to the at least one driven wheel. The brake torque is thus generated by the multi-disk brake device and conducted via the brake torque path to the at least one driven wheel.The multi-disk brake device is preferably arranged coaxially to the rotor axis of the electric axis. The vehicle preferably has a service brake, wherein the multi-disk brake device is designed as a complementary brake to the service brake and / or a supplementary multi-disk brake device to the service brake. A particularly advantageous application of the drive arrangement is thus proposed:The service brake in the vehicle is preferably designed as a friction brake, in particular as a dry friction brake, in particular as a disk and / or drum brake.In decelerations which are customary in urban road traffic, the predominant part of the braking task is taken over by the friction brake or the recuperation brake. Shortly before the vehicle is at a standstill, the use of the recuperation brake is not technically expedient; here, the friction brake supplies either the main part or the complete proportion of the required braking power.The vehicle with the electric drive machine lacks the laminating noise of the internal combustion engine; in hybrid vehicles, the internal combustion engine is optionally deactivated. Previously not relevant operating noises of the vehicle are perceived by the driver and can be perceived as annoying. Thus, reduction in noise emission leads to improvement in operating characteristics.The regulations (for example the UNDECE 13H for the vehicle class M1) also result in stringent safety requirements for the service brake with regard to hazardous braking, hot braking action and failsafety. In the future, further requirements are to be expected; here, the restriction of the permissible emission of fine dust particles of the brakes is to be emphasized.A conflict of goals can be derived from this voltage field: the friction brake must be both able to meet the safety requirements, have a significant acoustic behavior and at the same time the emission of fine dust particles must be reduced. In the case of emergency braking, on the other hand, brake noises are negligible. Here, the focus is merely on avoiding accidents, i.e. damage to the person or things.This conflict of goals is alleviated by the vehicle having the drive arrangement comprising the multi-disk brake device: the multi-disk brake device acts as a complementary brake and / or redundant multi-disk brake device, for example, in the urban environment, since the friction brake can no longer resolve the conflict of goals and / or the recuperation brake can no longer be used. In this case, it is emission-free and / or has a positive acoustic behavior.Since the multi-disk brake device as a complementary brake and / or supplementary multi-disk brake device still requires a conventional service brake (for example, embodied as a disk brake or drum brake), the safety-relevant requirements remain with the service brake, in particular with the friction brake. The operating properties of the drive arrangement and / or of the vehicle are thus improved taking into account the safety requirements and / or the environmental requirements.Towards the end of the deceleration process, the main brake deceleration may be generated by the service brake. This must be designed both for safe, controlled risk braking from high speed with a short braking distance and also not generate noise perceived as annoying by the driver in the case of braking from lower speed. Since the multi-disk brake device can replace the friction brake during brakings from lower speeds, manufacturers of friction brakes can focus on controlled dangerous brakings in their optimization efforts and obtain new action margins for the vehicle with the drive arrangement. In the case of dangerous braking, the acoustic behavior is of secondary importance in comparison with daily braking in urban traffic. Since the multi-disk brake device preferably makes no claim to a safety function - the service brake continues to be maintained and fully usable - it can be arranged in front of the transmission.In a preferred development of the invention, the vehicle has a brake management device for monitoring the service brake and the multi-disk brake device.The brake management device is preferably designed to implement an emergency braking state, wherein in the emergency braking state the service brake, in particular the friction brake, brings the vehicle to a standstill, wherein in the emergency braking state at least the main brake deceleration or the exclusive brake deceleration is implemented by the friction brake of the service brake. All safety requirements are thereby fulfilled.Alternatively or additionally, the brake management device is designed to implement a regenerative braking state, wherein at least a part of the brake deceleration is implemented by a regenerative braking of the regenerative brake. This realizes environment-aware and comfortable driving.Alternatively or additionally, the brake management device is designed to implement a comfort braking state, wherein the main braking deceleration is effected by the multi-disk brake device in order to bring the vehicle to a standstill. In particular, the brake management device is designed to implement the comfort braking state at speeds of less than 20 km / h, in particular of less than 15 km / h and / or already in a range greater than 10 km / h. In these speed states, the regenerative braking can no longer work effectively, the multi-disk brake device being used in particular instead of the friction brake. In the comfort braking state, it is achieved that the braking of the vehicle to a standstill is implemented without or only with low noise emission, since this is implemented completely or largely by the multi-disk brake device.An optional subject matter of the invention relates to a method for operating the vehicle with the drive arrangement as described above, wherein at least one of the operating states is implemented by the brake management device.The vehicle, in particular designed as an electric vehicle, optionally has a thermal management arrangement, wherein the thermal management arrangement has at least one user, wherein the thermal management arrangement is designed to supply the thermal energy from the multi-disk brake device to the user. In this configuration, the dissipated thermal energy is not simply conducted into the environment, but an attempt is made to use the thermal energy at the user in order to improve the environmental balance and efficiency of the electric vehicle. For example, the user can be configured as a heater for the passenger compartment, a pre-heating of a transmission, of a battery and / or of an engine or other vehicle components.Further features, advantages and effects are evident from the following description of preferred exemplary embodiments and from the attached figures. These show: FIG. 1 shows a schematic longitudinal section through a multi-disk brake device as an exemplary embodiment of the invention; FIG. 2 shows a schematic three-dimensional plan view of the multi-disk brake device in FIG. 1 ; FIG. 3 is a schematic block diagram of a vehicle having the multi-disk brake device at various positions; FIGS. 4 a, b, c show three different variants of the multi-disk brake device as can be used in the vehicle of FIG. 3.FIG. 1 shows a disk brake device 1 in a schematic longitudinal sectional illustration along an axis of rotation 100 of the disk brake device 1.The disk brake device 1 has a steel disk carrier 2, on which a plurality of steel disks 3 are placed. The steel plates 3 have axially aligned friction surfaces, wherein the friction surfaces are formed from the base material of the steel plates, i.e. as a steel material. The steel plates 3 are arranged on the steel plate carrier 2 so as to be displaceable in the axial direction with respect to the axis of rotation 100. As can be seen in particular from FIG. 2, which shows a schematic plan view or a cross section perpendicular to the axis of rotation 100, the steel disks 3 have a toothing 28 on the inner circumference, which engages in a positive fit in a counter toothing 29 of the steel disk carrier 2 in the circumferential direction about the axis of rotation 100. The contour of the toothing 28 and of the counter toothing 29 are formed complementary to one another, so that good heat transfer between the steel plate carrier 2 and the steel plates 3 is ensured.The disk brake device 1 has a disk carrier 4, the disk carrier 4 carrying a plurality of disk disks 5. The lining disks 5 each have a base body 6, which positively engages via a toothing 30 in a counter toothing 31 of the lining disk carrier 4 in the circumferential direction. Friction linings 7 are arranged on the base body 6, which can come into frictional contact with the friction surfaces of the steel plates 3. The lining plates 5 and the steel plates 3 together form a plate pack 8.The disk brake device 1 has an actuating device 9, wherein the actuating device 9 is designed to exert an axial actuating force on the disk pack 8, so that a braking torque is generated. The lining disk carrier 5 forms a stationary brake partner which can be connected to a section fixed to the vehicle, and the steel disk carrier forms a rotating brake partner which can be connected or is connected to a shaft.A cooling device 10 is integrated in the steel disk carrier 2, which is designed as an inner rotor and / or as an inner disk carrier in FIG. 1, wherein a liquid coolant can flow through the cooling device 10 in order to cool the steel disk carrier 2 and thus the disk brake device 1.Viewed from the constructional point of view, the steel disk carrier 2 is designed as a hub which carries a spline 11 for coupling to the shaft, not shown. Alternatively, the shaft, not shown, can be connected integrally and / or in one material with the hub and form or form the steel disk carrier 2.The steel plate carrier 2 has an axially but eccentrically extending bore 12 which is a component of a rotary feedthrough, not shown in detail, wherein the coolant can be supplied to the cooling device 10 via the rotary feedthrough with the bore 12.The steel plate carrier 2 has a circular ring groove 13, wherein the circular ring groove 13 is opened in an axial direction. In the longitudinal section shown, the circular ring groove 13 has a rectangular cross section and extends in the axial direction over a major part, in particular more than 90%, of the axial extent of the steel disk carrier 2 in the region of the circular ring groove 13.The bore 12 of the rotary feedthrough is connected in terms of flow to the circular ring groove 13 via a transverse bore 14, so that the coolant can flow from the bore 12 via the transverse bore 14 into the circular ring groove 13 and from there cool it out of the steel plate carrier 2.The circular ring groove 13 has an axially aligned circular ring-shaped axial opening 15 which is sealingly covered by a covering device 16.The disk brake device 1 has a brake housing 17, wherein the brake housing 17 forms a brake chamber 18, wherein the disk pack 8 is arranged in the brake chamber 18. The brake chamber 18 can be encapsulated, for example, with a cover, not shown, in particular in a dust-tight manner. Alternatively, the brake chamber 18 is open to the environment. The brake chamber 18 with the disk pack 8 is designed as a dry brake chamber 18, i.e. without coolant.The cover device 16 is fixed stationary in the brake housing 17, in particular fixed stationary on a back plate of the brake housing 17. The further part of the brake housing 17 can be formed by the lining disk carrier 4.The cover device 16 is designed as a circular ring disk, wherein an inner sealing collar 19 is arranged on the inner circumference, which engages in an inner groove 20 of the steel disk carrier 2 to form a labyrinth seal 21. On the radial outer side, the cover device 16 has an outer sealing collar 22, which engages in an outer groove 23 of the steel disk carrier 2 and forms with the latter an outer labyrinth seal 24. The circular ring groove 13 is thus sealingly closed in the axial direction.The sealing device 16 has a passage 25 which is formed corresponding to a passage opening 26 in the brake housing 17 and, viewed more precisely, in the rear plate and enables the coolant to be returned from the circular ring groove 13. The circular ring groove 13 with the sealing device 16 and the feed via the bore 12 and the discharge via the passage 25 and the passage opening 26 thus forms the cooling device 10, which is integrated in the steel disk carrier 2.FIG. 2 shows a schematic top view or sectional view through the brake disk device 1 in FIG. 1, and from the representation, the counter toothing 31 of the lining disk carrier 4, in which the toothing 30 of the lining disks 5 engage and the toothing 28 of the steel disks 3, can be seen from the outside to the inside.FIG. 3 shows a schematic block diagram of a vehicle 32 having a drive arrangement 33. in this exemplary embodiment, the drive arrangement 33 comprises an electric machine 34 and a transmission gear 35 which is operatively connected to the electric machine 24. The transmission 35 converts the rotational speed of the electric machine 34 from "fast to slow" or is designed as a reduction gear. From there, the torque is passed on to a differential 36 which distributes the drive torque to two wheels 37 a, bof a common axle 38 of the vehicle 32.It can be provided that the electric machine 34 and the transmission 35 together form an electric axis 38. Optionally, the differential 37 is also a component of the electric axle 39.The electric axle 38 has a housing 39, wherein the electric machine 34, the transmission 35 and optionally additionally the differential 36 are thus arranged in the housing 39, wherein the multi-disk brake device 1 is flanged onto the housing 39.FIG. 3 shows the disk brake device 1 arranged coaxially with respect to the electric machine 34, wherein the steel disk carrier 2 is connected in a rotationally fixed manner to the rotor shaft of the electric machine 34 via a transmission shaft 40. The multi-disk brake device 1 is thus operated at the rotational speed of the electric machine 34. The multi-disk brake device 1 can be supplied with the coolant via the electric axle 38.An alternative position for the multi-disk brake device 1 is provided on the side of the differential 36 either on the housing 39 of the electric axle 39 or-in the case of a separate housing 41 for the differential 36-on the housing 41. In this case, it is preferable that the rotation axis 100 is coaxially aligned with an input shaft of the differential 36.In addition, further possible positions for the multi-disk brake device 1 are drawn in FIG. 3. It is thus possible, for example, for the multi-disk brake device 1 to act in the transmission range between the electric machine 34 and the transmission gear 35. It is also possible for the multi-disk brake device 1 to be arranged so as to act at the output of the transmission 35 and / or the electric axle 38, in particular in front of the differential 36. Alternatively, the multi-disk brake device 1 is positioned at the entrance of the differential 36. A further possibility for positioning the multi-disk brake device 1 is at the outputs of the differential 36.In the latter positions of the multi-disk brake device 1, a torque path branch is formed in each case.Optionally, the drive arrangement 33 and / or the vehicle 32 can have a thermal management device, wherein the thermal management device is designed to supply the braking heat arising in the multi-disk brake apparatus 1 to a consumer in the vehicle 32. The brake heat can be dissipated in particular via the coolant and supplied to various tasks.As can be seen from FIG. 3, the multi-disk brake device 1 is arranged in most cases such that it acts on at least two wheels of the vehicle 2 and is thereby designed as a central brake. It can be provided that the vehicle 2 has a service brake, wherein the multi-disk brake device 1 is used as a complementary brake to the service brake.FIGS. 4 a, b, c show three possible embodiments for the multi-disk brake device 1 in a highly styled representation. The illustrated disc brake devices 1 can be disposed at the respective positions in FIG. 3.FIG. 4 ashows the multi-disk brake device 1, as is also shown in FIGS. 1 and 2. The steel plate carrier 2 can be seen, which is designed as an inner rotor and / or as an inner plate carrier and which carries the steel plates 3. The steel disk carrier 2 forms a hub and can be rotated. The cooling device 9 is integrated in the steel plate carrier 2. The lining disk carrier 4 with the lining disks 5, on the other hand, is arranged stationary.FIG. 4 bshows the disk brake device 1, wherein the steel disk carrier 2 is designed as an inner stator and / or as an inner disk carrier which carries the steel disks 3. The lining disk carrier 4 with the lining disks 5, on the other hand, is designed as an outer rotor and / or an outer disk carrier. The cooling device 9 is integrated in the steel plate carrier 2. Because the steel plate carrier 2 is realized as an inner stator, the supply of coolant for the cooling device 9 can be carried out much more easily.FIG. 4 cshows a disk brake device 1, wherein the steel disk carrier 2 is designed as an outer stator and / or as an outer disk carrier which carries the steel disks 3. The lining plate carrier 4 with the lining plates 5, on the other hand, is designed as an inner rotor and / or as an inner plate carrier. The cooling device 9 is integrated in the steel disk carrier 2, which can be configured at the same time as the brake housing 17. In this position, too, the coolant can be supplied to the cooling device 9 in a simple manner.In other words, the multi-disk brake device 1 with internally cooled disks can be seen in FIG. 1. A hub with internal toothing formed as a plug toothing 11 serves as a connection to the drive axle. Via this connection, the cooling liquid as coolant is also transported into the interior of the hub via a rotary feedthrough with the bore 12 and 14. The hub rotates at the input speed. The space for the cooling liquid as the circular ring groove 13 is closed by a cover device 16 which is connected to a carrier of the brake housing 17 and does not rotate. At the transition between the cover device 16 and the hub there is the geometry of a labyrinth seal 21, 24 in order to prevent the cooling liquid from leaking out. The steel plates 3 are connected to the hub in a rotationally fixed manner and preferably have a good heat transfer to the hub. The lining disks 5 are fastened on lining carriers as base body 6, which have a toothing 30 to the outer disk carrier as lining disk carrier 4 and are thereby connected to the latter in a rotationally fixed manner. The actuating device 9 generates an actuating force which presses the disk pack 8 axially against one another and generates a braking torque via the coefficient of friction of the individual contact surfaces. The return of the coolant takes place via a bore on the cover as passage 25 and on the carrier as passage opening 26.The arrangement is also conceivable in the opposite direction, as is shown in FIG. 4 a, i.e. the outer disk carrier as the lining disk carrier 4 and the lining disks 5 are connected in a rotationally fixed manner to the drive axle and the coolant chamber of the cooling device 9 is connected in a stationary manner to the brake housing 17. This arrangement has the advantage that the coolant supply and discharge can be constructed much more simply, since no rotating parts have to be sealed.Another type of arrangement would be to place the cooling space of the cooling device 9 radially outwards (relative to the plate pack 8), as shown in FIG. 4 c. In this arrangement, the friction plates as lining plates 5 would be fixed to the inner diameter in a rotationally fixed manner with the drive axle. The steel plates 3 would be fixed on the outer diameter in a rotationally fixed manner to the component which contains the coolant space. This component could also simultaneously include the function of the outer disk carrier 2 and the brake housing 17. This arrangement would have the advantage that the lining lamellae 5 are on the smallest possible diameter (advantageous because of the risk of bursting). In addition, the supply of the coolant chamber could be made relatively simple.List of reference characters1 Multi-disk brake device 2 Steel disk carrier 3 Steel disks 4 Lining disk carrier 5 Lining disks 6 Base body 7 Friction linings 8 Disk pack 9 Actuating device 10 Cooling device 11 Spline toothing 12 Bore 13 Circular ring groove 14 Transverse bore 15 Axial opening 16 Covering device 17 Brake housing 18 Brake chamber 19 Inner sealing collar 20 Inner groove 21 Inner labyrinth seal 22 Outer sealing collar 23 Outer groove 24 Outer labyrinth seal 25 Passage 26 Passage opening 28 Toothing of the steel disks 29 Counter toothing of the steel disk carrier 30 Toothing of the lining disks 31 Counter toothing of the lining disk carrier 32 Vehicle 33 Drive arrangement 34 Electric machine 35 Transmission gear 36 Differential 37 a,b Driven wheels 38 Electric axis 39 Housing 40 Transmission shaft 41 Housing of the differential 100 Axis of rotation

Claims

Multi-disk brake device (1) for a vehicle (32), having a steel disk carrier (2) and a plurality of steel disks (3), wherein the steel disks (3) are arranged on the steel disk carrier (2), and having a lining disk carrier (4) and a plurality of lining disks (5), wherein the lining disks (5) are arranged on the lining disk carrier (4), wherein the steel disks (3) and the lining disks (5) form a disk pack (8), having an actuating device (9) for generating an actuating force which axially compresses the disk pack (8) in order to generate a braking torque, wherein a cooling device (9), which is closed off from the disk pack (8), for cooling the steel disk carrier (2) with a coolant, wherein - the steel disk carrier (2) is designed as an inner rotor in the multi-disk brake device (1), or the steel plate carrier (2) is designed as an inner stator and the lining plate carrier (4) as an outer rotor.Multi-disk brake device (1) according to Claim 1, characterized in that the steel disk carrier (2) is designed as an inner disk carrier.Multi-disk brake device (1) according to Claim 1 or 2, characterized bya rotary feedthrough for supplying the coolant to the cooling device (9) via the inner rotor and / or the steel disk carrier (2).Multi-disk brake device (1) according to one of Claims 1 to 3, characterized in that the inner rotor has a circular-ring groove (13) for guiding the coolant in the inner rotor, the circular-ring groove (13) having an annular axial opening (15), and in that the multi-disk brake device (1) has a covering device (16), the covering device (16) being arranged in a stationary manner, sealing the annular axial opening (15) in order to form the cooling device (9), and having a return for the coolant.Multi-disk brake device (1) according to Claim 4, characterized in that the covering device (16) is designed as a circular ring disk, wherein an inner sealing collar (19) which extends in the axial direction is arranged on the inner periphery, wherein the inner rotor has an inner groove (20) for receiving the inner sealing collar (19), wherein the inner groove (20) and the inner sealing collar (19) form an inner labyrinth seal (21), and / or wherein an outer sealing collar (22) which extends in the axial direction is arranged on the outer periphery, wherein the inner rotor has an outer groove (23) for receiving the outer sealing collar (22), wherein the outer groove (23) and the outer sealing collar (22) form an outer labyrinth seal (24).Multi-disk brake device (1) according to one of the preceding claims, characterized bya brake housing (17), wherein the disk pack (8) is arranged encapsulated in the brake housing (17).Vehicle (32) with the multi-disc brake device (1) according to one of the preceding claims, wherein the multi-disc brake device (1) is designed as a central brake.

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