Disc brake cooling device of a motor vehicle

Abstract

Disc brake cooling device (10; 80; 90; 100) of a motor vehicle, comprising - a brake disc (14) with a brake chamber (16) and a friction ring (18) which is surrounded by outside air in an installed state, and - a wheel carrier (26) for holding a wheel-tire combination, wherein the brake disc (14) is fastened to the wheel carrier (26) with the brake chamber (16), characterized in that - the brake disc (14) has a plurality of brake disc channels (20) extending entirely inside the brake disc (14) for guiding cooling liquid (52), each having at least one inlet opening (22) and at least one outlet opening (24), wherein the inlet opening (22) and the outlet opening (24) are arranged in a central region of the brake chamber (16) on a side facing the wheel carrier (26) and are spaced apart from one another in the radial direction, - at least two separate wheel carrier channels (32, 34) extend within the wheel carrier (26), which provide fluidic connections between an end face (28) of the wheel carrier (26) and an outer circumference (30) of the wheel carrier (26), wherein in the installed state, one of the wheel carrier channels (32, 34) is in fluidic connection with the at least one inlet opening (22) and the at least one outlet opening (24), and wherein - the wheel carrier (26) has on one end face (28) two circumferentially extending, concentric, radially spaced-apart grooves of uniform depth, which in the installed state are in fluid communication on the one hand with the plurality of brake disc channels (20) and on the other hand with the at least two separate wheel carrier channels (32, 34) of the wheel carrier (26), and wherein - a sealing unit (36) has two sealing chambers (38, 40) separated from one another, wherein the sealing unit (36) is arranged in a sealing manner on the outer circumference (30) of the wheel carrier (26) at the location of the fluidic connections for fluidic separation thereof, and which has at least two fluidic connections (42, 44) for supplying and discharging the cooling liquid (52), which are each in fluidic connection with one of the sealing chambers (38, 40).

Description

[0001] The invention relates to a disc brake cooling device with a braking device comprising a brake disc with a brake chamber and a friction ring, which is surrounded by outside air in an installed state, and a wheel carrier for holding a wheel-tire combination, wherein the brake disc with the brake chamber can be fastened to the wheel carrier, with the features of the preamble of claim 1.

[0002] It is known in the art to use internal combustion engines in stationary applications to heat fluids required in process engineering. Heat exchangers are typically used to heat the fluids.

[0003] Heat sources are often required in oil fields to generate steam or thermal fracturing fluids. These include both flame and flameless heat sources, which may include an internal combustion engine.

[0004] DE 197 22 254 A1, which comes closest to the invention, relates to a device for extracting thermal energy from vehicle friction brake systems, wherein parts of the service brakes arranged in the wheel or axle area are flushed with a cooling medium. For this purpose, the brake disc or the brake drum has a channel or a channel system. The channel or the channel system is part of a heat transfer medium circuit with at least one integrated heat exchanger, or parts of the brake disc or the brake drum are equipped with cooling fins, wherein a heat transfer medium flows between a housing enclosing the cooling fin zones, passing through at least one heat exchanger and / or a filter, or wherein the heat transfer medium flows through the enclosing housing and passes through at least one heat exchanger.

[0005] CN 102 267 442 A deals with a cooling system and a cooling method for cooling brake drums.

[0006] DE 32 23 405 A1 deals with a brake disc designed as a rotating heat pipe.

[0007] EP 0 202 581 A2 deals with a device for cooling the hydraulic fluid of a brake system.

[0008] DE 10 2013 111 102 A1 discloses a viscous brake for drivetrain heating. Embodiments for heating a drivetrain of a vehicle are provided. An exemplary method for a vehicle includes heating a fluid with vehicle kinetic energy in response to a vehicle braking request and directing the fluid to a drivetrain component. In this way, the vehicle kinetic energy can be used to heat a drivetrain component during a vehicle braking event.

[0009] For example, US 7 614 367 B1 describes a system and method for flameless heating, concentrating or vaporizing a fluid by converting rotational kinetic energy into heat by heating the fluid in a heating subsystem with a rotating heating device such as a water brake dynamometer, and then vaporizing all or part of the fluid in an evaporation subsystem and / or concentrating the fluid in a concentration subsystem.

[0010] The procedure includes the following steps: Providing a prime mover, such as an internal combustion engine, adapted to generate rotational kinetic energy and thermal energy; coupling a dynamometer to the prime mover such that rotational kinetic energy is transferred to the dynamometer; circulating a first fluid through the dynamometer to impart thermal energy to the fluid; circulating the first fluid through at least one heat exchanger adapted to transfer thermal energy of the prime mover to the fluid; circulating the fluid through at least one second heat exchanger; passing a second fluid through the at least second heat exchanger to transfer thermal energy from the first fluid to the second fluid, thereby heating the second fluid; separating the second fluid into its vapor and liquid phases; providing a receiving tank adapted to receive the liquid and vapor phases of the second fluid;Providing a fluid-to-air condenser in fluid communication with the tank for condensing a portion of the second fluid vapor by passing air through the condenser to transfer heat energy from the vapor to the air; and providing an evaporation chamber in fluid communication with the tank for evaporating a portion of the second fluid with the heated air.

[0011] It is also known from the prior art to reduce the fuel consumption of internal combustion engines, such as combustion engines, particularly during cold starts, by bringing the engine and other components of a drive train to their respective operating temperatures as quickly as possible, or even before start-up. Solutions have been proposed for this purpose, both that utilize waste heat generated by the engine itself and solutions that supply additional energy from outside. The rapid or premature heating of operating fluids and lubricants in the drive train leads to lower friction losses and / or increased efficiency of the internal combustion engine.

[0012] The solutions proposed in the state of the art are adapted to the respective design of the internal combustion engine.

[0013] For example, US 2012 / 0 125 278 A1 describes a stationary method for heating engine and / or transmission oil of a hybrid vehicle with an internal combustion engine and an electric motor, wherein the engine and / or transmission oil is heated using the waste heat of a charger for at least one battery and / or the waste heat of the at least one battery. During charging of the battery, waste heat is generated at the charger and the battery. The waste heat at the charger is in the range of a few hundred watts to several kW, depending on how quickly the battery is charged. An intermediate fluid circuit can be thermally coupled to the charger and the battery as heat sources by means of a heat exchanger. This allows the waste heat from the charger and the battery to be transferred to the coolant of the intermediate fluid circuit.

[0014] A fluid circuit containing engine oil can be connected to an M heat exchanger. The fluid circuit containing the engine oil is circulated by a circulation pump. This allows the heat in the coolant of the intermediate fluid circuit to be transferred to the engine oil via the M heat exchanger. Similarly, the intermediate fluid circuit can also be connected to a G heat exchanger. Another fluid circuit containing transmission oil, circulated by a circulation pump, can thus flow through the G heat exchanger. At the G heat exchanger, heat can thus be transferred from the coolant of the intermediate fluid circuit to the transmission oil, heating the transmission oil.

[0015] DE 103 32 497 A1 provides a method for shortening the warm-up phase of a motor vehicle with an internal combustion engine, at least one transmission, and associated oil circuits, as well as an on-board electrical system consisting of a starter motor, generator, and storage unit. In this method, the oil circuits are heated using electrical energy extracted from the on-board electrical system.

[0016] For example, the electrical energy for heating can be drawn from the vehicle's electrical system only during the vehicle's coasting or braking phase. This has the advantage of preventing additional energy from being drawn from the vehicle's electrical system, which would then have to be compensated for by increasing engine power. The same advantage can be achieved if the electrical energy for heating is only drawn when the battery is full or "overcharged."

[0017] Debbie Sniderman's May 29, 2012, paper "Using Waste Engine Heat in Automobile Engines" (available at https: / / www.asme.org / topics-resources / content / usingwaste-engine-heat-in-automobile-engines) describes how drive oils in an internal combustion engine can be quickly heated and operated at a slightly higher temperature without additional hydraulic power. It was found that, with optimal control, the utilization of waste heat delivers consistently higher oil temperatures and significantly shorter warm-up times. This resulted in fuel savings of nearly 4% compared to conventional thermal management strategies. The greatest efficiency gains occur in heating oil after a cold start, and approximately half of the improvement comes from the powertrain and transmission side.

[0018] Furthermore, US Pat. No. 7,077,776 B2 discloses a heat exchanger integrated into the transmission oil pan, which transfers heat from exhaust gases downstream of the catalytic converter to the transmission oil. Inlet and outlet channels direct the exhaust gas between the heat exchanger and an exhaust pipe located downstream of the catalytic converter. The exhaust pipe contains a control valve that redirects the exhaust flow to the heat exchanger during the warm-up phase or to the exhaust pipe during steady-state operation. A control function is provided to monitor the transmission oil temperature and engine operating conditions and to control the valve actuation. The main input parameter for the control function is the transmission oil temperature.

[0019] Transmission fluid can circulate in a transmission hydraulic system under the pressure generated by a hydraulic pump, flow from the housing to an external oil cooler, which removes heat from the fluid, and return from the cooler to the oil pan. The heat of the transmission fluid can be exchanged in the cooler primarily by convection with air flowing at high velocity between fins emanating from the lines that carry the fluid through the cooler and by conduction to the surrounding fluid.

[0020] US 9 174 612 B2 proposes a solution for the specific case of an oil bath brake, which includes a vehicle method comprising the following steps: heating a fluid with vehicle kinetic energy by actuating an oil bath brake (viscous brake) via a valve set by a controller with non-volatile instructions stored in a memory, without actuating friction brakes, in response to a vehicle braking demand below a threshold and a drive temperature below a threshold; actuating the vehicle friction brakes if the vehicle braking demand is greater than the threshold; and supplying the heated fluid to a drivetrain component. The oil bath brake may include a wet clutch. The wet clutch may be configured to heat drivetrain, engine, and / or transmission lubricating oil.The wet clutch may be lubricated by a fluid, and when the wet clutch is applied to reduce axle rotation, the wet clutch may shear the lubricating fluid, thereby heating the fluid. Thus, the wet clutch functions as an oil bath braking and fluid heating mechanism. The lubricating fluid heated by the wet clutch may be routed to a heat exchanger. The heat exchanger may transfer heat from the heated fluid to other driveline or powertrain components. For example, the heat exchanger may heat transmission fluid used to lubricate the transmission, differential fluid of the differential, and / or lubricating oil routed to other driveline components. In some embodiments, the fluid from the wet clutch may directly heat downstream driveline components without an intermediary heat exchanger.

[0021] In view of the state of the art shown, there is still room for improvement in the area of ​​reducing fuel consumption or energy consumption of an engine, particularly during cold starts, by heating components of the drive train.

[0022] The invention is based on the object of providing a device at least for heating at least one component of a drive train of a motor vehicle, comprising at least one engine and a transmission, which device does not require energy to be supplied from outside the motor vehicle and with which it is possible to dispense with the extraction of thermal energy from a coolant system of the engine and the extraction of electrical energy from an electrical energy storage device of the motor vehicle.

[0023] The object is achieved by a disc brake cooling device of a motor vehicle according to claim 1.

[0024] Shown is a disc brake cooling device of a motor vehicle, comprising - a brake disc with a brake chamber and a friction ring which is surrounded by outside air in an installed state, and - a wheel carrier for supporting a wheel-tire combination, wherein the brake disc is attached to the wheel carrier with the brake chamber.

[0025] According to the invention, the brake disc has a plurality of brake disc channels extending entirely within the interior of the brake disc for guiding cooling fluid, each having at least one inlet opening and at least one outlet opening, wherein the inlet opening and the outlet opening are arranged in a central region of the brake chamber on a side facing the wheel carrier and are spaced apart from one another in the radial direction, wherein at least two separate wheel carrier channels extend within the wheel carrier, which provide fluidic connections between an end face of the wheel carrier and an outer circumference of the wheel carrier, wherein, in the installed state, one of the wheel carrier channels is in fluidic connection with the at least one inlet opening and the at least one outlet opening, and wherein the wheel carrier has two circumferentially extending, concentric, radially spaced-apart grooves of uniform depth on one end face,which, in the installed state, are in fluid communication on the one hand with the plurality of brake disc channels and on the other hand with the at least two separate wheel carrier channels of the wheel carrier, and wherein a sealing unit has two separate sealing chambers, wherein the sealing unit is arranged in a sealing manner on the outer circumference of the wheel carrier at the location of the fluid connections for fluid separation thereof, and which has at least two fluid connections for supplying and discharging the cooling liquid, each of which is in fluid communication with one of the sealing chambers.

[0026] Further, particularly advantageous embodiments of the invention are disclosed in the dependent subclaims.

[0027] It should be noted that the features and measures listed individually in the following description can be combined with one another in any technically reasonable manner and demonstrate further embodiments of the invention. The description further characterizes and specifies the invention, particularly in conjunction with the figures.

[0028] The braking device of a motor vehicle includes, as already mentioned above, a brake disc with a brake chamber and a friction ring, which is surrounded by outside air in an installed state, as well as a wheel carrier for holding a wheel-tire combination, wherein the brake disc can be fastened to the wheel carrier with the brake chamber. The brake disc has at least one brake disc channel running entirely within the interior of the brake disc for guiding a cooling fluid, having at least one inlet opening and at least one outlet opening. In addition, the wheel carrier has at least two separate wheel carrier channels that provide fluidic connections between an end face of the wheel carrier and an outer circumference of the wheel carrier, wherein, in the installed state, one of the wheel carrier channels is in fluidic connection with the at least one inlet opening or the at least one outlet opening.

[0029] For the purposes of this invention, a “motor vehicle” is understood to mean, in particular, a passenger car, a lorry, a semi-trailer truck or a bus.

[0030] It is a finding of the present invention that in motor vehicles the greatest instantaneous power conversions occur in the braking systems, which can be used by the proposed braking device at least to heat at least one component of a motor vehicle's drive train. The thermal energy generated during braking, which in conventional braking devices is transferred to the passing air and is thus lost, can be dissipated by the proposed disc brake cooling device at the point of its generation, namely at the friction ring of the brake disc, and made available at one end of the two wheel carrier channels on the outer circumference of the wheel carrier. As is known, temperatures of several hundred degrees Celsius can arise at the brake disc during braking, so that the temperature level of the thermal energy generated during braking can be sufficient for effective transfer.In this way, the heating of at least one component of a drive train of a motor vehicle can take place without any energy being supplied from outside the motor vehicle and is also not dependent on the extraction of electrical energy from an electrical energy storage device of the motor vehicle.

[0031] As a side effect, the brake disc in question can be cooled more effectively than with conventional air cooling by dissipating the heat energy generated during braking, which can open up possibilities for a more compact design of the disc brake system.

[0032] As mentioned above, the brake disc has a plurality of brake disc channels running entirely within the interior of the brake disc for guiding the cooling fluid, each having at least one inlet opening and at least one outlet opening. Furthermore, the wheel carrier is provided on one end face with two circumferential grooves which, when installed, are in fluid communication with the plurality of brake disc channels on the one hand and with the at least two separate wheel carrier channels on the other. For the purposes of the present invention, the term "plurality" is to be understood in particular as a number of at least two. In this way, the thermal energy generated in the brake disc during braking can be dissipated particularly evenly and completely and made available at one of the ends of the two wheel carrier channels on the outer circumference of the wheel carrier.

[0033] Preferably, the brake disc channels are arranged at equal spacings from one another in a circumferential direction of the brake disc. Furthermore, the number of brake disc channels is preferably between two and ten, thereby achieving a favorable compromise between equipment and manufacturing costs and uniform dissipation of heat energy from the brake disc.

[0034] As already mentioned above, the disc brake cooling device further comprises a sealing unit with two separate sealing chambers. The sealing unit is arranged or can be arranged in a sealing manner on the outer circumference of the wheel carrier at the location of the fluid connections for fluidic separation. Furthermore, the sealing unit has at least two fluid connections for supplying and discharging the coolant, each of which is fluidically connected to one of the sealing chambers. This allows, in a structurally simple manner, cooling fluid to be supplied to the brake disc when the wheel carrier is moving, and the heated cooling fluid can be discharged from the brake disc separately.

[0035] The proposed disc brake cooling device can advantageously be used in motor vehicles whose drive train includes at least one engine designed as an internal combustion engine (combustion engine) or as an electric motor, which also includes hybrid electric vehicles (“Hybrid Electric Vehicle”, HEV)) and electric cars (“Battery Electric Vehicle”, BEV).

[0036] In preferred embodiments, the disc brake cooling device includes a coolant pump, a fluidic connection between the coolant pump and one of the fluidic connections of the sealing unit, and at least one heat-transferring connection to a lubricating oil circuit and / or to a cooling circuit of the motor vehicle. The coolant pump is provided to pump coolant through the at least one brake disc channel extending inside the brake disc or through the plurality of brake disc channels, the at least two separate wheel carrier channels of the wheel carrier, and the at least one heat-transferring connection. The term "provided for this purpose" is to be understood, in the context of the present invention, as meaning specifically designed or arranged for this purpose.

[0037] In this way, the thermal energy provided at one of the ends of the two wheel carrier channels on the outer circumference of the wheel carrier can be supplied to at least one component of a drive train of a motor vehicle.

[0038] In preferred embodiments of the disc brake cooling device, the cooling fluid is formed by lubricating oil. Furthermore, the at least one heat-transferring connection is designed as a fluidic connection to the lubricating oil circuit of the motor vehicle. The heat transfer, which occurs by mass transfer in the form of the lubricating oil, allows friction losses due to the high viscosity of the lubricating oil to be significantly reduced in a particularly simple design during operation, and particularly during a cold start of the motor vehicle's engine, thus reducing fuel consumption and energy consumption of the motor vehicle.

[0039] In preferred embodiments of the disc brake cooling device, the cooling fluid is formed by transmission oil. Furthermore, the at least one heat-transferring connection is designed as a fluidic connection to a transmission housing of the motor vehicle. The heat transfer, which occurs by mass transfer in the form of the transmission oil, allows friction losses due to the high viscosity of the transmission oil to be significantly reduced in a particularly simple design during operation, and particularly during a cold start of the motor vehicle's engine, thus reducing fuel consumption and energy consumption of the motor vehicle.

[0040] In preferred embodiments of the disc brake cooling device, the cooling fluid is formed by a high-temperature coolant or lubricating oil. Furthermore, the at least one heat-transferring connection is designed as the high-temperature side of a heat exchanger with indirect heat transfer, i.e., without mass transfer. In this way, the thermal energy from the brake disc can be transferred during operation, and in particular during a cold start of the motor vehicle's engine, even to fluids that are not related to the high-temperature coolant or lubricating oil used to dissipate the thermal energy from the brake disc.

[0041] High-temperature coolants are commercially available and are also known to those skilled in the art as heat transfer oil or thermal oil. They can be based on, for example, but are not limited to, silicone oil.

[0042] If the cooling liquid is formed by a high-temperature coolant and a low-temperature side of the heat exchanger can be connected to the lubricating oil circuit of the motor vehicle by means of a fluid connection, cooling liquids whose thermal properties with regard to heat transfer at the expected temperatures are superior to those of lubricating oil can advantageously be used to dissipate the thermal energy from the brake disc instead of lubricating oil.

[0043] In preferred embodiments of the disc brake cooling device, the cooling fluid is formed by a high-temperature coolant or lubricating oil. Furthermore, a low-temperature side of the heat exchanger can be connected to the transmission housing of the motor vehicle via a fluid connection. In this way, cooling fluids can advantageously be used to dissipate the thermal energy from the brake disc instead of transmission oil, as their thermal properties with regard to heat transfer at the expected temperatures are superior to those of transmission oil.

[0044] In preferred embodiments of the disc brake cooling device, the cooling fluid is formed by a high-temperature coolant or lubricating oil. Furthermore, a low-temperature side of the heat exchanger can be connected to the cooling circuit of a motor vehicle engine via a fluid connection. In this way, the duration of a cold start phase of a motor vehicle engine can be shortened in a structurally simple manner, and the engine can often be brought to an optimal operating temperature, thereby reducing fuel consumption and energy consumption of the motor vehicle.

[0045] It should be noted that, within the scope of the invention, it is also contemplated that the low-temperature side of the heat exchanger may have several materially separated regions that can be connected to different components of the drive train. For example, one region of the low-temperature side may contain lubricating oil and be connectable to the lubricating oil circuit of the motor vehicle via a fluid connection, and another, materially separated region of the low-temperature side may contain high-temperature coolant and be connectable to the cooling circuit of the motor vehicle via a fluid connection.

[0046] Further advantageous embodiments of the invention are disclosed in the dependent claims and the following description of the figures. Fig. 1 a schematic representation of a disc brake cooling device with a braking device of a motor vehicle in an installed state in a sectional, partial side view, Fig. 2 a block diagram of the disc brake cooling device with the braking device according to the Fig. 1, Fig. 3 a block diagram of an alternative embodiment of a disc brake cooling device with the braking device according to the Fig. 1, Fig. 4 a block diagram of a further alternative embodiment of a disc brake cooling device with the braking device according to the Fig. 1, and Fig. 5 a block diagram of a further alternative embodiment of a disc brake cooling device with the braking device according to the Fig. 1.

[0047] In the different figures, identical parts are always provided with the same reference symbols, which is why they are usually only described once.

[0048] Fig. Figure 1 shows a schematic representation of a possible embodiment of a disc brake cooling device 10 with a braking device 12 of a motor vehicle in an installed state in a sectional, partial side view. The braking device 12 is mounted in the area of ​​the left rear wheel of the motor vehicle, which is designed as a passenger car (not shown) and can, for example, have a power unit formed by an internal combustion engine. Fig. Figure 1 shows a portion of the braking device 12 located above a rear axle line 72 of the motor vehicle. A mirror-image version of the braking device 12 (not shown) is mounted in the area of ​​the right rear wheel. Of course, the braking device can also be provided on the front wheels, i.e., in addition to the braking device on the rear wheels or on its own. The following describes the braking device shown, with this description being applicable analogously to the design for the braking device on the front wheels and the right rear wheel.

[0049] The braking device 12 comprises a brake disc 14 with a brake chamber 16 and a friction ring 18, which is surrounded by outside air in the illustrated installed state. For reasons of clarity, the usually present brake calliper with the brake pads arranged on both sides of the friction ring 18 and which can be pressed against its annular friction surfaces is shown in the Fig. 1 omitted.

[0050] In the horizontal direction and transverse to a vehicle longitudinal axis which is in the Fig. 1, extending perpendicular to the plane of the drawing, is a wheel carrier 26, which is provided for supporting a wheel-tire combination (not shown). The brake disc 14 is fastened in a conventional manner to the brake chamber 16 by means of screw connections (not shown) on an end face 28 of the wheel carrier 26.

[0051] The brake disc 14 has a plurality of brake disc channels 20 extending entirely within the interior of the brake disc 14 for conveying a cooling fluid 52, each having at least one inlet opening 22 and at least one outlet opening 24. Each of the brake disc channels 20 leads from the respective inlet opening 22, which is arranged in a central region of the brake chamber 16 on a side facing the wheel carrier 26, alternately in the radial or axial direction and parallel to an outer surface of the brake chamber 16 into the friction ring 18 and, parallel and spaced from this path, back to the central region of the brake chamber 16, where the respective brake disc channel 20 ends at the outlet opening 24, which is spaced further radially from the rear axle line 72 than the inlet opening 22. In other embodiments, the positions of the inlet and outlet openings can be reversed.

[0052] For example, six brake disc channels 20 can be provided, wherein the six brake disc channels 20 can be arranged equally spaced from one another in a circumferential direction of the brake disc 14, and wherein one of the brake disc channels 20 in the plane of the drawing of the Fig. 1 lies.

[0053] The wheel carrier 26 is supported on its outer circumference 30 by means of a rolling bearing 70, which as in the Fig. 1 can be designed as a double-row ball bearing, mounted on an axle journal 68 of the rear axle, so that the wheel-tire combination with the wheel carrier 26 and the brake disc 14 attached thereto can rotate around the rear axle line 72.

[0054] The wheel carrier 26 is provided on the end face 28 with two circumferentially extending, concentric, radially spaced grooves of uniform depth (not shown). Furthermore, the wheel carrier 26 has two separate wheel carrier channels 32, 34, which provide a fluidic connection on the end face 28 of the wheel carrier 26 between each of the grooves and the outer circumference 30 of the wheel carrier 26. In the Fig. 1, each of the two grooves is in fluid communication on the one hand with the plurality of brake disc channels 20 in the brake disc 14 and on the other hand with one of the two separate wheel carrier channels 32, 34 of the wheel carrier 26.

[0055] The disc brake cooling device 10 is equipped with a sealing unit 36 ​​having two separate sealing chambers 38, 40. The sealing unit 36 ​​is arranged in a sealing manner on the outer circumference 30 of the wheel carrier 26 at the location of the fluid connections, for fluidic separation thereof, such that each of the fluid connections on the outer circumference 30 of the wheel carrier 26 opens into one of the sealing chambers 38, 40. The sealing unit 36 ​​has two fluid connections 42, 44 for supplying and discharging the coolant 52. The two fluid connections 42, 44 are each fluidly connected to one of the sealing chambers 38, 40.

[0056] Fig. 2 shows a block diagram of the disc brake cooling device 10 with the braking device 12 according to the Fig. 1. The disc brake cooling device 10 is equipped with a coolant pump 50 and fluid connections. The fluid connections can be designed, for example, as hose connections, connecting the coolant pump 50 to one of the fluid connections 42, 44 of the sealing unit 36 ​​( Fig. 1) and provide a material and heat transfer connection 46 ( Fig. 2) to a lubricating oil circuit 62 of the engine 74 of the motor vehicle.

[0057] The coolant pump 50 is provided to pump the cooling liquid 52 formed by lubricating oil through the inside of the brake disc 14 ( Fig. 1) running brake disc channels 20, the two separate wheel carrier channels 32, 34 of the wheel carrier 26 and the material and heat transfer connection 46 ( Fig. 2) into and out of the lubricating oil circuit 62 of the engine 74 of the motor vehicle.

[0058] In the embodiment of the disc brake cooling device 10 according to the Fig. 2, the cooling liquid 52 could also be formed by transmission oil, and the fluid connections could connect the coolant pump 50 to one of the fluid connections 42, 44 of the sealing unit 36 ​​( Fig. 1) and a material and heat transfer connection 46 ( Fig. 2) to a transmission housing 64 of the motor vehicle. In this case, the coolant pump 50 is provided to pump the cooling liquid 52 formed by the transmission oil through the brake disc 14 ( Fig. 1) running brake disc channels 20, the two separate wheel carrier channels 32, 34 of the wheel carrier 26 and the material and heat transfer connection 46 ( Fig. 2) into and out of the gearbox housing 64 of the motor vehicle.

[0059] Fig. 3 shows a block diagram of an alternative embodiment of a disc brake cooling device 80 with the braking device 12 according to the Fig. 1.

[0060] To avoid repetition, only differences between the alternative embodiment of the disc brake cooling device 80 and the embodiment of the disc brake cooling device 10 according to the invention according to the Fig. 1 and Fig. 2 described.

[0061] In the alternative embodiment of the disc brake cooling device 80, the cooling liquid 52 is formed by a high-temperature coolant or lubricating oil, and the at least heat-transferring connection 46 is designed as a high-temperature side 56 of a heat exchanger 54 with indirect heat transfer, ie without mass transfer.

[0062] Here, the coolant pump 50 is provided to pump the cooling liquid 52 formed by the high-temperature coolant or the lubricating oil through the inside of the brake disc 14 ( Fig. 1) running brake disc channels 20, the two separate wheel carrier channels 32, 34 of the wheel carrier 26 and the high-temperature side 56 ( Fig. 3) of the heat exchanger 54.

[0063] In the Fig. In the embodiment of the disc brake cooling device 80 shown in Figure 3, the cooling fluid 52 is formed by the high-temperature coolant, and the low-temperature side 58 of the heat exchanger 54 is fluidically connected to the lubricating oil circuit 62 of the motor vehicle's engine 74. The heat exchanger fluid 76 on the low-temperature side 58 is formed by lubricating oil and is pumped by a separate pump 60 from the lubricating oil circuit 62 of the motor vehicle's engine 74 through the low-temperature side 58 of the heat exchanger 54 and back.

[0064] In a further alternative embodiment of the disc brake cooling device 90 according to the Fig. 4, the cooling fluid 52 is formed by high-temperature coolant or lubricating oil, and the low-temperature side 58 of the heat exchanger 54 is fluidically connected to the transmission housing 64 of the motor vehicle. The heat exchanger fluid 76 on the low-temperature side 58 is formed by transmission oil and is pumped by a separate pump 60 from the transmission housing 64 of the motor vehicle through the low-temperature side 58 of the heat exchanger 54 and back.

[0065] In a further alternative embodiment of the disc brake cooling device 100 according to the Fig.5, the cooling fluid 52 is formed by high-temperature coolant or lubricating oil, and the low-temperature side 58 of the heat exchanger 54 is fluidically connected to a cooling circuit 66 of the motor vehicle's engine 74. The cooling fluid 76 on the low-temperature side 58 is formed by a water-glycol mixture and is pumped by a separate pump 60 from the cooling circuit 66 of the motor vehicle's engine 74 through the low-temperature side 58 of the heat exchanger 54 and back. List of reference symbols: 10 Disc brake cooling device 12 Braking device 14 brake disc 16 brake chamber 18 Friction ring 20 brake disc channel 22 Inlet opening 24 Outlet opening 26 wheel carriers 28 Front side 30 outer circumference 32 wheel carrier channel 34 Wheel carrier channel 36 Sealing unit 38 Sealing chamber 40 Sealing chamber 42 fluid power connection 44 fluid power connection 46 heat transfer connection 50 coolant pump 52 Coolant 54 heat exchangers 56 High temperature side 58 Low temperature side 60 pump 62 Lubricating oil circuit 64 Gearbox housing 66 Cooling circuit 68 axle journals 70 rolling bearings 72 rear axle line 74 Power machine

[0066] List of reference symbols (continued): 76 Heat exchanger fluid 80 disc brake cooling device 90 Disc brake cooling device 100 disc brake cooling device

Claims

[1] Disc brake cooling device (10; 80; 90; 100) of a motor vehicle, comprising - a brake disc (14) with a brake chamber (16) and a friction ring (18) which is surrounded by outside air in an installed state, and - a wheel carrier (26) for supporting a wheel-tyre combination, wherein the brake disc (14) is fastened to the wheel carrier (26) with the brake chamber (16), characterized by , that - the brake disc (14) has a plurality of brake disc channels (20) extending entirely inside the brake disc (14) for guiding cooling liquid (52), each having at least one inlet opening (22) and at least one outlet opening (24), wherein the inlet opening (22) and the outlet opening (24) are arranged in a central region of the brake chamber (16) on a side facing the wheel carrier (26) and are spaced apart from one another in the radial direction, - at least two separate wheel carrier channels (32, 34) extend within the wheel carrier (26), which provide fluidic connections between an end face (28) of the wheel carrier (26) and an outer circumference (30) of the wheel carrier (26), wherein in the installed state, one of the wheel carrier channels (32, 34) is in fluidic connection with the at least one inlet opening (22) and the at least one outlet opening (24), and wherein - the wheel carrier (26) has on one end face (28) two circumferentially extending, concentric, radially spaced-apart grooves of uniform depth, which in the installed state are in fluid communication on the one hand with the plurality of brake disc channels (20) and on the other hand with the at least two separate wheel carrier channels (32, 34) of the wheel carrier (26), and wherein - a sealing unit (36) has two sealing chambers (38, 40) separated from one another, wherein the sealing unit (36) is arranged in a sealing manner on the outer circumference (30) of the wheel carrier (26) at the location of the fluidic connections for fluidic separation thereof, and which has at least two fluidic connections (42, 44) for supplying and discharging the cooling liquid (52), each of which is in fluidic connection with one of the sealing chambers (38, 40). [2] Disc brake cooling device (10; 80; 90; 100) according to claim 1, characterized by - a coolant pump (50), - a fluid connection between the coolant pump (50) and one of the fluid connections (42, 44) of the sealing unit (36), and - an at least heat-transferring connection (46) to a lubricating oil circuit (62) and / or to a cooling circuit (66) of the motor vehicle, wherein the coolant pump (50) conveys cooling liquid (52) through the plurality of channels (20) running inside the brake disc (14), the at least two separate channels (32, 34) of the wheel carrier (26) and the at least one heat-transferring connection (46). [3] Disc brake cooling device (10) according to claim 1 or 2, characterized by that the cooling liquid (52) is formed by lubricating oil and the at least one heat-transferring connection (46) is designed as a fluidic connection to the lubricating oil circuit (62) of the motor vehicle. [4] Disc brake cooling device (10) according to claim 1 or 2, characterized bythat the cooling liquid (52) is formed by transmission oil and the at least one heat-transferring connection (46) is designed as a fluidic connection to a transmission housing (64) of the motor vehicle. [5] Disc brake cooling device (80; 90; 100) according to claim 1 or 2, characterized by that the cooling liquid (52) is formed by a high-temperature coolant or by lubricating oil and the at least one heat-transferring connection (46) is designed as a high-temperature side (56) of a heat exchanger (54) with indirect heat transfer. [6] Disc brake cooling device (80) according to claim 5, characterized by that the cooling liquid (52) is formed by a high-temperature coolant and that a low-temperature side (58) of the heat exchanger (54) can be connected to the lubricating oil circuit (62) of the motor vehicle by means of a fluidic connection. [7] Disc brake cooling device (90) according to claim 5 or 6, characterized bythat a low-temperature side (58) of the heat exchanger (54) can be connected to the transmission housing (64) of the motor vehicle by means of a fluidic connection. [8] Disc brake cooling device (100) according to one of claims 5 to 7, characterized by that a low-temperature side (58) of the heat exchanger (54) can be connected to a cooling circuit (66) of an engine (74) of the motor vehicle by means of a fluidic connection.

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