DE102019118503A1 - Braking device for a wheel hub drive arrangement - Google Patents

Abstract

There is a braking device (2) for a wheel hub drive arrangement (1), with a housing section (3) for arranging the braking device (2) on the wheel hub drive arrangement (1), with a disk carrier (12) for supporting a disk disc (11), wherein the Disc carrier (12) defines a main axis (H), with one or more lining carriers (13a, b) for carrying a brake lining (14a, b), the lining carrier (13a, b) being operatively connected to the housing section (3), and wherein a braking force (F) can be introduced via the brake lining (14a, b) into the disk (11) for braking the disk carrier (12), with a hydraulic device (6) for generating the braking force (F), the braking force (F) A pressure pot (16) to which at least one lining carrier (13a, b) is transferred and / or can be transferred is proposed, the disk carrier (12) being designed as an inner disk carrier (12). Furthermore, a wheel hub drive arrangement (1) with said braking device (2) is proposed.

Description

The invention relates to a braking device for a wheel hub drive arrangement according to the preamble of patent claim 1. The invention also relates to a wheel hub drive arrangement with a braking device.

In a vehicle, in particular a vehicle with an electric wheel hub drive, a so-called e-wheel drive, brakes with lamellas are often used to brake the vehicle.

For example, describes the DE 10 2012 200 668 A1 a wheel drive on a vehicle axle, with a driven wheel hub rotatably mounted on a wheel hub carrier and with at least one hydraulically actuated multi-disc brake for braking the wheel hub. As a rotating part of the multi-disk brake, an outer disk is arranged on the wheel hub in a rotationally fixed and axially displaceable manner.

The invention is based on the object of proposing a braking device which saves space and is better integrated into a wheel hub drive arrangement.

This object is achieved by a braking device for a wheel hub drive arrangement with the features of claim 1 and by a wheel hub drive arrangement with the braking device according to claim 7. Preferred or advantageous embodiments of the invention emerge from the dependent claims, the following description and / or the attached figures.

According to the invention, a braking device for a wheel hub drive arrangement, in particular for a vehicle with an electric wheel hub drive, is proposed. The wheel hub drive arrangement preferably has an electric motor for driving a vehicle wheel, the braking device being designed to brake the vehicle wheel. In particular, the braking device is designed as a multi-disc brake.

The braking device has a housing section for arranging the braking device on the wheel hub drive arrangement. In particular, the housing section is non-positively connected to a wheel hub drive housing and / or integrated in the wheel hub drive housing. In particular, the housing section forms an installation space in the wheel hub drive arrangement in which the braking device is formed. Alternatively or optionally in addition, the housing section is designed to close off an installation space of the wheel hub drive arrangement, for example the installation space for the electric motor.

The braking device has a disk carrier for supporting a disk disk, in particular a brake disk. The disk carrier defines a main axis, the disk carrier with the disk disk preferably being designed to be rotationally symmetrical about the main axis. The lamellar carrier preferably has a toothing for supporting the lamellar disk, the toothing being designed for a positive connection with the lamellar disk. Alternatively or optionally in addition, the disk carrier engages in the disk disk via a wave spring.

In particular, the lamellar disc has two friction surfaces, the friction surfaces preferably being formed annularly in the radial direction with respect to the main axis, and the two friction surfaces being arranged on the lamellar disc facing away from one another. The lamellar disk is preferably made of metal, for example steel.

The braking device has one or more pad carriers for supporting a brake pad. In particular, the brake lining is materially connected to the lining carrier, for example via an adhesive connection. The lining carrier is preferably designed as an annular carrier, the brake lining preferably being formed circumferentially on the lining carrier and being arranged on a radial side surface of the lining carrier. The brake lining preferably has a mixed composition, for example a metal-graphite composition.

The at least one lining carrier is operatively connected to the housing section. The lining carrier is preferably supported on the housing section in at least one axial direction in relation to the main axis.

The brake lining is designed to introduce a braking force into the disk to brake the disk carrier. The braking force is preferably to be understood as the force which leads to the braking of the disk carrier. The braking force can preferably be understood as a tensioning force of the brake lining against the lamellar disk, with kinetic energy being converted into heat by friction, for example, for braking. The braking force can preferably be introduced in the axial direction with respect to the main axis via the brake lining into the flap disk, the braking force preferably being introduced into at least one of the two annular friction surfaces of the flap disk via the circumferential brake lining.

The braking device has a hydraulic device for generating the braking force. The hydraulic device generates the braking force preferably via a pressure difference of a fluid, in particular oil. The braking device for the wheel hub drive arrangement is preferably designed as a hydraulically actuated multi-disc brake. For example, the braking device can be actuated by hydraulic actuation, for example a brake pedal.

The braking force generated by the hydraulic device can be transmitted and / or is transmitted to the at least one lining carrier via a pressure pot. The pressure pot is preferably plate-shaped and arranged coaxially and / or concentrically with respect to the main axis. The pressure pot preferably has an inner and an outer diameter, the lining carrier being arranged adjacent to the outer circumference of the pressure pot and the hydraulic device being arranged adjacent to the inner diameter of the pressure pot. The pressure pot preferably transmits the braking force in the axial direction with respect to the main axis from the hydraulic device to the lining carrier. In particular, the pressure pot is designed as a resilient disk, the braking force being transmitted from the pressure pot to the lining carrier and / or being transferable. For example, the pressure pot presses on a radial rear side surface of the lining carrier, with the brake lining being able to be pressed onto the one friction surface of the disk disc on the radial side surface facing away.

According to the invention, the disk carrier is designed as an inner disk carrier. In particular, the inner disk carrier is designed as a rotating part of the braking device. The inner disk carrier preferably rotates together with the disk disk around the main axis, the at least one lining carrier preferably being designed as a stationary part of the braking device. The inner disk carrier is preferably arranged inside the disk disk, the inner disk carrier preferably being plate-shaped and engaging in a radial inner diameter of the disk disk.

It is advantageous that a space-saving design of the braking device is created by the inner disk carrier. The compact design of the brake device enables improved integration into a wheel hub drive arrangement, so that the brake device with the wheel hub drive arrangement can be accommodated within a vehicle wheel thanks to a compact construction, in particular in an axial dimension. It is also advantageous that the braking device reduces the rotating parts, so that an inexpensive and low-maintenance braking device with sufficient braking power is created.

In a preferred embodiment, the lamellar disk is non-rotatably connected to the inner disk carrier. The lamellar disk is arranged such that it can be displaced in the axial direction with respect to the main axis between a first lining carrier and a second lining carrier. In particular, a position of the disk disc on the inner disk carrier can be changed in the axial direction in relation to the main axis. The non-rotatable connection and the variable axial position of the lamellar disk on the inner lamella carrier are preferably formed by the toothing and / or the wave spring. For example, the toothing has axially extending teeth, the teeth being arranged around the inner disk carrier. For example, the teeth of the inner disk carrier engage in a mating contour of the disk disk and fasten the disk disk to the inner disk carrier in a rotationally fixed manner.

The first lining carrier can be pressed against the disk disk in the axial direction in order to introduce the braking force. In particular, the pressure pot presses the first lining carrier against the disk, the brake lining of the first carrier introducing the braking force into the disk.

The second lining carrier is arranged on the housing section in a supporting manner against the braking force. In particular, the second lining carrier is supported in the axial direction on the housing section. The second lining carrier is preferably connected to the housing section with a force fit. In particular, the second lining carrier is arranged in a fixed position on the housing section.

In particular, the first pad carrier presses in the axial direction with respect to the main axis against the lamellar disc, the lamellar disc being displaceable against the fixed second lining carrier, the lamellar disc being clamped and / or able to be clamped between the brake linings of the first and second lining carriers.

It is advantageous in this embodiment that the lamellar disk can detach itself from the second lining carrier in the axial direction, for example when it is free running, so that the lamellar disk can be rotated without friction.

In a preferred constructive implementation of the invention, the hydraulic device has at least one piston and a pressure chamber, the piston being received in the pressure chamber such that it can be disengaged. The pressure chamber is preferably designed as a hydraulic cylinder for receiving a column of fluid, in particular oil. In particular, the fluid column can be displaced into the pressure chamber via a pressure connection. The piston is disengageably received in the pressure chamber, the piston preferably being supported and / or running against the pressure chamber when it is disengaged. The hydraulic device preferably has a seal, the seal being arranged on the piston and / or the pressure chamber for sealing.

The braking force can be actuated by a stroke movement of the piston against the pressure pot in the axial direction with respect to the main axis. The pressure chamber is preferably open on one side for performing the lifting movement. In particular, when moving out of the pressure chamber, the piston presses in the axial direction against at least one inner diameter section of the pressure pot. In particular, the hydraulic device has a second piston and a second pressure chamber, the second piston being movable against a second inner diameter section of the pressure pot. Preferably, the first and the second piston are axially symmetrical with respect to the main axis, a uniform stroke movement of the first and the second piston against the pressure pot in the axial direction with respect to the main axis can be exerted.

In a preferred embodiment of the invention, the braking device has a preload device for preloading the pressure pot. The preload device preferably has one or spring elements for generating and / or storing a pretensioning force, the spring elements preferably being supported on the pressure pot. The pretensioning device counteracts the stroke movement of the piston in the axial direction with respect to the main axis. For example, when the piston is disengaged from the pressure chamber, the spring element is tensioned by axially displacing the pressure pot, and when the braking device is released, the pressure pot pushes the piston back into the pressure chamber due to the stored preloading force of the spring element.

In this preferred embodiment, the braking device has an external driver ring for receiving the at least one lining carrier. The outer driver ring is preferably designed coaxially and / or concentrically to the main axis, the outer driver ring preferably being arranged around the inner disk carrier in the radial direction with respect to the main axis. The outer driver ring preferably forms a non-rotatable counterpart to the inner disk carrier, the at least one lining carrier being arranged on the outer driver ring. The first and the second lining carrier are preferably arranged on the outer driver ring, the first lining carrier being arranged on the outer driver ring such that it can be displaced in the axial direction. The second lining carrier is preferably arranged in a fixed position on the outer driver rim and faces the first lining carrier in the axial direction, the lamellar disk being arranged between the two lining carriers so as to be rotatable about the main axis. The second lining carrier is preferably supported in the radial direction on the outer driver rim, the outer driver rim preferably being connected to the housing section by a force-fit connection, for example a screw connection. For example, when the disk disc is braked, the second lining carrier is supported on the outer driver ring in the radial and axial directions, the outer driver ring being arranged on the housing section to transmit torque.

In a preferred embodiment of the invention, the braking device has a wheel carrier. The wheel carrier is preferably designed to axially close off the braking device and / or the housing section in the shape of a disk and / or plate. The wheel carrier is preferably connected to the housing section in a non-positive and / or positive manner, the wheel carrier being designed to accommodate the vehicle wheel.

The outer drive rim has several fastening elements and the wheel carrier has several centering contours. The fastening elements and the centering contours are designed for frictional connection of the outer driver rim to the wheel carrier. The fastening elements are preferably designed as radially designed screw-on lugs, the centering contours preferably being designed as centering domes in the axial direction, whereby the screw-on lugs can preferably be positioned between the centering domes, with a non-positive connection means, e.g. a screw, connecting the outer driver rim to the wheel carrier.

In an alternative embodiment of the invention, the braking device has a spring device for generating a restoring force of the at least one lining carrier. The spring device preferably has a leaf spring or a wave spring for generating the restoring force, the restoring force preferably acting on the first lining carrier.

The at least one lining carrier is operatively connected to the housing section via the spring device. In particular, the first lining carrier is arranged on the housing section in a supporting manner via the spring device, the first lining carrier preferably being axially displaceable.

The restoring force of the spring device counteracts the braking force for releasing the brake lining from the flap disc. The spring device is preferably tensioned when the lamellar disc is braked, the restoring force being built up becomes. The spring device preferably has a plurality of leaf springs or wave springs, the leaf springs or wave springs being arranged around the main axis. The leaf or wave springs are preferably arranged uniformly on the housing section around the main axis. For example, two leaf or wave springs are arranged offset by 180 degrees, in particular three by 120 degrees, about the main axis. It is advantageous that the plurality of leaf or wave springs of the spring device transmits the restoring force uniformly and enables the brake lining to be released evenly from the lamellar disk.

The leaf or wave springs are preferably designed to transmit torque from the first lining carrier to the housing section. The leaf or wave springs are preferably arranged around the circumference in such a way that a torque is absorbed when the disk is braked, in particular independently of a direction of rotation of the disk. For example, the leaf or wave springs are alternately arranged on the housing section, oriented according to a direction of rotation. It is advantageous that the leaf or wave springs are not damaged when the direction of rotation of the lamellar disc is reversed, e.g. when the vehicle is reversing, e.g. by kinking the leaf spring, as the alternately arranged leaf or wave springs support each other.

According to the invention, a wheel hub drive arrangement has the braking device described. The wheel hub drive arrangement is preferably designed as an electric wheel hub drive for a vehicle, in particular for an electric vehicle, the wheel hub drive arrangement being arranged on one or all of the wheels, preferably on four wheels, of the vehicle to drive the vehicle. The wheel hub drive arrangement preferably has an electric motor for generating a drive torque. The wheel hub drive arrangement is preferably installed within the wheel, in particular within a wheel rim, of the vehicle.

The wheel hub drive arrangement preferably has a wheel bearing carrier for receiving one or more wheel bearing devices. The wheel bearing carrier is preferably connected to the wheel carrier in a force-fitting and / or form-fitting manner. The wheel bearing carrier preferably defines the main axis.

In a preferred embodiment of the invention, the wheel hub drive arrangement has a sun gear section for engaging in a planetary gear, and the braking device has a coupling section. The planetary gear preferably comprises a ring gear and a planet carrier for supporting several planet gears, with the sun gear section preferably being engageable with the several planet gears and with the sun gear section being operatively connected to the planet carrier and the ring gear for torque transmission.

The sun gear section is preferably coupled to the electric motor, the sun gear section preferably forming a drive axis for the electric motor. The sun gear section is operatively connected to a wheel of the wheel hub drive arrangement. The sun gear section preferably drives the planetary gear, an output of the planetary gear, in particular the planet carrier, being operatively connected to the wheel for driving the vehicle. The sun gear section is preferably designed coaxially and / or concentrically to the main axis. In particular, the sun gear portion is positioned in the axial direction with respect to the main axis on a drive side of the wheel hub drive arrangement with the electric motor and the planetary gear, the coupling portion being positioned in the axially opposite direction with respect to the main axis on a brake side of the wheel hub drive arrangement with the braking device.

The coupling section is connected to the inner disk carrier for transmitting a braking torque. The coupling section is preferably connected to the inner disk carrier in a force-locking manner, in particular by a screw connection. The coupling section is preferably designed coaxially and / or concentrically to the main axis, the coupling section preferably forming an input and / or output for the braking device for transmitting the braking torque.

The sun gear section is materially connected to the coupling section for introducing the braking torque into the wheel. In particular, the sun gear section with the coupling section is designed as a hollow shaft, the hollow shaft preferably being connected to the inner disk carrier for braking and the electric motor for driving the wheel and engaging with a toothing in the planetary gear for torque transmission. The sun gear section and the coupling section are preferably made of metal, in particular aluminum, and in particular are materially connected by a one-piece design.

In a preferred embodiment of the invention, the coupling section with the sun gear section are designed concentrically and / or coaxially to the main axis. The coupling section and the sun gear section are preferably rotatably received in the wheel hub drive arrangement. The coupling section is, in particular rotatable, on the housing section via a roller bearing device in the radial direction with respect to FIG supports the main axis. The roller bearing device is designed, for example, as a deep groove ball bearing and / or angular contact ball bearing and / or roller bearing, the roller bearing device preferably bearing the coupling section and the sun gear section. For example, the rolling element device forms a common bearing for the coupling section with the inner disk carrier and for the sun gear section of the planetary gear.

• 1 in einer schematischen Schnittdarstellung eine Bremsvorrichtung für eine Radnabenantriebsanordnung als ein Ausführungsbeispiel der Erfindung;
• 2a einen Außenmitnehmerkranz der Bremsvorrichtung aus 1 als ein alternatives Ausführungsbeispiel;
• 2b einen Radträger der Bremsvorrichtung aus 1 als ein alternatives Ausführungsbeispiel;
• 3 die Bremsvorrichtung aus 1 in einer perspektivischen Schnittdarstellung als ein weiteres Ausführungsbeispiel der Erfindung.

Further features, advantages and effects of the invention emerge from the following description of preferred exemplary embodiments of the invention. Show:

• 1 in a schematic sectional view a braking device for a wheel hub drive arrangement as an embodiment of the invention;
• 2a an outer drive ring of the braking device 1 as an alternative embodiment;
• 2 B a wheel carrier of the braking device 1 as an alternative embodiment;
• 3 the braking device off 1 in a perspective sectional view as a further embodiment of the invention.

Corresponding or identical parts are provided with the same reference numerals in the figures.

1 shows a braking device in a schematic sectional view 2 for wheel hub drive arrangement 1 of a vehicle as an embodiment of the invention. For example, the vehicle is designed as an electromobile or an electric car. The wheel hub drive assembly 1 serves to drive and brake a vehicle wheel. For example, the vehicle has at least two, preferably exactly four, vehicle wheels which can be driven or braked via a separate wheel hub drive arrangement.

The braking device 2 has a housing section 3 to accommodate the braking device 2 and for carrying the braking device 2 on the wheel hub drive assembly 1 on. The housing section 3 is plate- and / or cup-shaped and around a main axis H educated. For example, the housing section 3 rotationally symmetrical around the main axis H formed with the main axis H is defined for example by a drive shaft (not shown) for the vehicle wheel. The housing section 3 is for flange-mounting the braking device 2 to the wheel drive assembly 1 educated. The housing section 3 is open on one of its radial sides, with a wheel carrier 4th closes the opened page.

The wheel carrier 4th is designed to carry the vehicle wheel (not shown). The wheel carrier 4th is plate-shaped and / or in the radial direction with respect to the main axis H educated. For example, the wheel carrier 4th rotationally symmetrical around the main axis H educated. A wheel bearing bracket is used to carry the vehicle wheel 5 with the wheel carrier 4th connected, the wheel bearing carrier 5 in the axial direction on the main axis H extends and perpendicular to the wheel carrier 4th is flanged and / or arranged. The wheel bearing carrier 5 is designed to accommodate wheel bearings (not shown) hollow and concentric and / or coaxial to the main axis H educated. The drive shaft (not shown) runs through the wheel bearing carrier to drive the vehicle wheel 5 , wherein the drive shaft extends at least in the radial direction over the wheel bearings on the wheel bearing carrier 5 supports.

The braking device 2 has a hydraulic device 6th to generate a braking force F. for braking the vehicle wheel. The hydraulic device 6th has a pressure space 7th and a piston 8th on, with the piston 8th in the pressure room 7th is added and in the axial direction with respect to the main axis H from the one-sided open pressure chamber 7th is displaceable, the piston 8th to the pressure room 7th when disengaging. The disengagement can be understood as a lifting movement and acts in the same direction as the braking force F. .

The printing room 7th has a pressure connection 9 on, the pressure connection 9 for moving a column of fluid, for example oil, from a master cylinder (not shown) with the pressure chamber 7th connected is. The printing room 7th is on the wheel carrier 4th arranged, the pressure chamber 7th during the stroke movement of the piston 8th in the axial direction on the wheel carrier 4th supports. The hydraulic device 6th exhibits a seal 10 on, taking the seal 10 on the piston 8th is arranged, the seal 10 when the piston is disengaged 8th at the pressure room 7th starts up and seals. Alternatively and / or optionally, the seal is a supplement 10 at the pressure room 7th arranged and runs on the piston 8th at. In the 1 has the braking device 2 two hydraulic device 6th on, the two hydraulic devices 6th offset by 180 degrees to the main axis H on the wheel carrier 4th are arranged.

The braking device 2 has a lamellar disc 11 on, with the flap disc 11 rotationally symmetrical around the main axis H is designed and rotatable about the main axis H on a lamella carrier 12 is arranged. The flap disc 11 is non-rotatable with the lamella carrier 12 connected, with the flap disc 11 axially movable from the lamella carrier 12 is recorded. The flap disc 11 is a friction partner for one or more brake pads 14a , b trained. The lamellar carrier 12 is with a coupling section 31 non-rotatably connected. The coupling section 31 is coaxial and / or concentric to the main axis H formed and forms with the plate carrier 12 and the flap disc 11 the rotatable components of the braking device 2 . The coupling section 31 is supported by a roller bearing device when rotating in the radial direction 32 on the housing section 3 from.

The brake pads 14a , b are from a lining carrier 13a , b worn and are firmly bonded to the lining carrier 13a , b, for example by means of an adhesive bond. The brake pads 14a , b are on radial friction surfaces 15a , b of the flap disc 11 arranged to the braking force F. into the flap disc 11 initiate. The lining carrier 13a , b and the brake pads 14a , b are for the circumferential introduction of the braking force F. into the flap disc 11 ring-shaped and coaxial and / or concentric within the housing section 3 arranged.

The first pad carrier 13a is in the axial direction between the first friction surface 15a and a pressure pot 16 arranged. The pressure pot 16 is for transmitting the braking force F. with the first pad carrier 13a and the hydraulic device 6th effectively connected. The pressure pot 16 is plate-shaped and coaxial and / or concentric to the main axis H arranged. The first pad carrier 13a lies with the first brake pad 14a on the flap disc 11 on, with the pressure pot 16 the braking force F. over a rear surface of the first lining carrier 13a transmits in the axial direction. In other words, pushes the pressure pot 16 the first pad carrier 13a on the flap disc 11 , the first brake pad 14a on the first friction surface 15a can be pressed on to the braking force F. into the flap disc 11 to initiate braking of the vehicle wheel.

In the embodiment in 1 is the lamella carrier 12 as an inner disc carrier 12 educated. The inner disc carrier 12 carries the flap disc 11 on an inner diameter of the flap disc 11 , with the flap disc 11 non-rotatably with the inner disc carrier 12 connected is. The flap disc 11 and the inner disc carrier 12 have a toothing, the toothing for the positive connection of the flap disc 11 with the inner disc carrier 12 is trained. The flap disc 11 is axially displaceable on the inner disc carrier 12 delegated so that the friction surfaces 15a , b when rotating the flap disc 11 from the brake pads 14a , b are detachable and / or can run freely.

The embodiment shows the braking device 2 with an outer drive ring 17th to carry the two lining carriers 13a , b. The outer drive ring 17th is with the housing section 3 positively and non-positively, for example by a screw connection and a receiving contour. The second pad carrier 13b supports itself when braking the flap disc 11 via the outer drive ring 17th on the housing section 3 in the radial and axial directions. For example, the second lining carrier is 13b fixed in position between a radial section of the outer drive ring 17th and the flap disc 11 arranged. The outer drive ring 17th supports the two lining carriers 13a , b when braking the flap disc 11 from, with a moment from the outer drive rim 17th is transferable and on the housing section 3 works.

In the embodiment in 1 has the braking device 2 a preload device 18th for pretensioning the pressure pot 16 on. The pretensioner 18th has several spring elements 19th , for example compression springs, with the spring elements 19th to the main axis H distributed, are arranged circumferentially. The spring elements 19th are designed to build up and store a preload force in the axial direction, the preload force being the stroke movement of the piston 8th counteracts. The pressure pot 16 lies with its inner diameter between the piston 8th and the spring elements 19th on, the stroke movement of the piston 8th the pressure pot 16 axially shifts and the opposing spring elements 19th tense. For example, he pushes the pressure pot 16 the piston 8th back into the pressure chamber through the applied pre-tensioning force 7th back.

The 2a shows the outer drive ring 17th in an alternative embodiment, wherein the outer driver rim 17th as a substantially annular ring with a receiving toothing 20th to hold the two lining carriers 13a , b is formed. The outer drive ring 17th has several fasteners 21st on, with the fasteners 21st extend in the radial direction and have a through opening 22nd for frictional connection, for example by a screw connection. The fastening elements have a lateral support contour 23 around the through opening 22nd on, with the support contours 23 are wedge-shaped and / or trapezoidal in the radial direction.

The 2 B shows the wheel carrier 4th in one embodiment, wherein the wheel carrier 4th several centering contours 24 having. The centering contours 24 are on a radial side of the wheel carrier 4th arranged in the area of the outer circumference, the centering contours 24 cohesively with the wheel bearing carrier 4th are connected. The wheel carrier 4th has a receiving opening 25th to record the Wheel bearing carrier 5 and two communication ports 26th for attaching two hydraulic devices 6th on. The receiving opening 25th is centered in the wheel carrier 4th introduced, with the major axis H through the through opening 25th is flowable.

The connection openings 26th are around the main axis H arranged mirrored. The pressure rooms 7th are at the connection openings 26th can be arranged, the pressure connections 9 through the connection openings 26th are extendable.

The centering contours 24 and the fasteners 21st are for the form-fitting connection of the outer drive ring 17th with the wheel carrier 4th educated. The support contours 23 the fasteners 21st grip into the centering contours 24 and center the outer drive ring 17th on the wheel carrier 4th . For example, each fastener is supported 21st on two centering contours 24 in the radial direction, with a screw connection through the through openings 22nd can be positioned and the outer drive ring 17th non-positively attached to the wheel carrier.

In this exemplary embodiment, the torque when braking is via the outer drive ring 17th in the wheel carrier 4th guided, for example the wheel carrier 4th is connected to the vehicle and / or vehicle body.

The 3 shows the braking device 2 in a perspective sectional view as a further embodiment, wherein the braking device 2 a spring device 27 for generating a restoring force of the first lining carrier 13a having. The spring device 27 has several leaf springs 28 on, with the leaf springs 28 on the first pad carrier 13a and the housing section 3 are arranged. For example, there are several spring devices 27 around the main axis H running with the first pad carrier 13a connected.

Several leaf springs 28 are flatly connected to each other, with the leaf springs 28 can be tensioned in the axial direction. When applying the braking force F. is the first pad carrier 13a with the first brake pad 14a on the flap disc 11 can be pressed on, the restoring force being provided by the spring device 27 can be built up, the restoring force of the braking force F. acts in the opposite direction, the first brake lining 14a from the flap disc 11 is solvable.

The 3 shows the braking device 2 with the second pad carrier 13b , the second pad carrier 13b directly on the housing section 3 is arranged. The second pad carrier 13b is supported on the housing section at least in an axial direction and in a radial direction 3 from. In the other axial direction, the flap disc prevents 11 the axial shifting of the second lining carrier 13b . When braking, for example, the flap disc 11 on the second brake pad 14b pressed and clamps the second pad carrier 13b between housing section 3 and lamellar disc 11 a.

The wheel hub drive assembly 1 has a hollow shaft 29 on, the hollow shaft 29 coaxial and / or concentric to the main axis H arranged and around the wheel bearing carrier 5 is designed to be rotatable. The hollow shaft 29 has a sun gear section 30th on, the sun gear section 30th engages in a planetary gear (not shown) for torque transmission. The braking device 2 has the coupling section 31 for fastening the inner disc carrier 12 on. The coupling section 31 and the sun gear section 30th are than the hollow shaft 29 formed, the coupling portion 31 and the sun gear section 30th materially connected to one another than the one-piece hollow shaft 29 are trained. The hollow shaft 29 can be coupled to an electric motor (not shown), the hollow shaft 29 can be driven by the electric motor. The hollow shaft 29 can also be understood as a drive shaft of the electric motor, the braking device 2 to brake the hollow shaft 29 is trained. An output of the wheel hub drive arrangement 1 can for example be realized via a planet carrier (not shown) of the planetary gear, the planet carrier being operatively connected to the vehicle wheel for driving or braking.

List of reference symbols

1

Wheel hub drive assembly

2

Braking device

3

Housing section

4th

Wheel carrier

5

Wheel bearing carrier

6th

Hydraulic equipment

7th

Printing room

8th

piston

9

Pressure connection

10

poetry

11

Flap disc

12

Lamella carrier

13a

first pad carrier

13b

second pad carrier

14a

first brake pad

14b

second brake pad

15a

first friction surface

15b

second friction surface

16

Pressure pot

17th

Outer drive ring

18th

Pretensioning device

19th

Spring element

20th

Receiving gear

21st

Fastener

22nd

Through opening

23

Support contour

24

Centering contour

25th

Receiving opening

26th

Connection opening

27

Spring device

28

Leaf spring

29

Hollow shaft

30th

Sun gear section

31

Coupling section

32

Rolling bearing device

F.

Braking force

H

Main axis

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was 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.

Patent literature cited

• DE 102012200668 A1 [0003]

Claims (9)

Braking device (2) for a wheel hub drive arrangement (1), with a housing section (3) for arranging the braking device (2) on the wheel hub drive arrangement (1), with a disk carrier (12) for carrying a disk disc (11), the disk carrier (12 ) defines a main axis (H), with one or more pad carriers (13a, b) for supporting a brake pad (14a, b), the pad carrier (13a, b) being operatively connected to the housing section (3), and wherein a braking force (F) can be introduced via the brake lining (14a, b) into the disk disc (11) for braking the disk carrier (12), with a hydraulic device (6) for generating the braking force (F), the braking force (F) via a pressure pot (16) to which at least one facing carrier (13a, b) is transferred and / or can be transferred, characterized in that the disk carrier (12) is designed as an inner disk carrier (12). Braking device (2) after Claim 1 , characterized in that the lamellar disc (11) is rotatably connected to the inner disc carrier (12), the lamellar disc (11) in the axial direction in relation to the main axis (H) between a first lining carrier (13a) and a second lining carrier (13b ) is arranged displaceably, and wherein at least the first pad carrier (13a) for introducing the braking force (F) can be pressed against the lamellar disc (11) in the axial direction, the second pad carrier (13b on the housing section (3) against the braking force (F ) is arranged in a supporting manner. Braking device (2) after Claim 1 or 2 , characterized in that the hydraulic device (6) has at least one piston (8) and a pressure chamber (7), the piston (8) being received in the pressure chamber (7) such that it can be disengaged, the braking force (F) being generated by a stroke movement of the piston (8) can be actuated against the pressure pot (16) in the axial direction with respect to the main axis (H). Braking device (2) after Claim 3 , characterized in that the braking device (2) has a preload device (18) for preloading the pressure pot (16), the preloading device (18) counteracting the stroke movement of the piston (8) in the axial direction with respect to the main axis (H), and wherein the braking device (2) has an outer driver rim (17) for receiving the at least one lining carrier (13a, b). Braking device (2) after Claim 4 , characterized in that the braking device (2) has a wheel carrier (4), wherein the outer driver ring (17) has several fastening elements (21) and the wheel carrier (4) has several centering contours (24) for frictional and / or positive connection of the outer driver ring (17) ) with the wheel carrier (4). Braking device (2) after Claims 1 to 3 , characterized in that the braking device (2) has a spring device (27) for generating a restoring force of the at least one lining carrier (13a, b), wherein the at least one lining carrier (13a, b) with the housing section (3) via the spring device ( 27) is operatively connected, the restoring force of the spring device (27) counteracting the braking force for releasing the brake lining (14a, b) from the flap disc (11). Wheel hub drive arrangement (1) characterized in that the wheel hub drive arrangement (1) the braking device (2) according to the Claims 1 to 6th having. Wheel hub drive assembly (1) according to Claim 7 , characterized in that the wheel hub drive arrangement (1) has a sun gear section (30) for engaging a planetary gear and the braking device (2) has a coupling section (31), the coupling section (31) being connected to the inner disk carrier (12) for transmitting a braking torque and wherein the sun gear section (30) is operatively connected to a wheel of the wheel hub drive arrangement (1), the sun gear section (30) being materially connected to the coupling section (31) for introducing the braking torque into the wheel. Wheel hub drive assembly (1) according to Claim 8 , characterized in that the coupling section (31) with the sun gear section (30) are concentric and / or coaxial with the main axis (H), at least the coupling section (31) being attached to the housing section (3) via a roller bearing device (32) supported in the radial direction with respect to the main axis (H).

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