WO2022268310A1 - Fluidleitanordnung für eine reiblamellenkupplung und kupplungseinheit mit einer fluidleitanordnung - Google Patents
Fluidleitanordnung für eine reiblamellenkupplung und kupplungseinheit mit einer fluidleitanordnung Download PDFInfo
- Publication number
- WO2022268310A1 WO2022268310A1 PCT/EP2021/067169 EP2021067169W WO2022268310A1 WO 2022268310 A1 WO2022268310 A1 WO 2022268310A1 EP 2021067169 W EP2021067169 W EP 2021067169W WO 2022268310 A1 WO2022268310 A1 WO 2022268310A1
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- WO
- WIPO (PCT)
- Prior art keywords
- fluid guide
- section
- carrier
- fluid
- axially
- Prior art date
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- 239000012530 fluid Substances 0.000 title claims abstract description 113
- 230000005540 biological transmission Effects 0.000 claims description 12
- 230000002093 peripheral effect Effects 0.000 claims description 6
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- 238000009826 distribution Methods 0.000 description 11
- 238000001816 cooling Methods 0.000 description 8
- 230000008901 benefit Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 238000007514 turning Methods 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
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- 230000002349 favourable effect Effects 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
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- 238000005755 formation reaction Methods 0.000 description 1
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- 238000012545 processing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/72—Features relating to cooling
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
- B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
- B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
- B60K17/3515—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches with a clutch adjacent to traction wheel, e.g. automatic wheel hub
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/648—Clutch-plates; Clutch-lamellae for clutches with multiple lamellae
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0457—Splash lubrication
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0473—Friction devices, e.g. clutches or brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
- F16H57/0483—Axle or inter-axle differentials
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K2023/085—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles automatically actuated
- B60K2023/0858—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles automatically actuated with electric means, e.g. electro-hydraulic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/74—Features relating to lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
Definitions
- Friction disk clutches are used in drive trains for friction-locked torque transmission between two drive components, such as drive shafts and/or drive wheels. They enable drive trains to be shifted at any speed difference under torque load.
- Wet-running friction disk clutches include several friction disks that are cooled or lubricated by means of a surrounding fluid, for example an oil.
- a wet-running clutch unit for a motor vehicle is known from DE 102015220446 B3. This comprises a friction clutch with a first friction disc assigned to a drive element and second friction discs assigned to a driven element, which form a friction disc pack.
- the first friction discs have first recesses and the second friction discs have second recesses.
- the first and second recesses overlap in the radial and axial direction, so that a friction disc pack recess is formed.
- a fluid manifold is fixedly mounted on the drive member and includes a fluid chamber and a fluid duct.
- the fluid chamber extends axially into the friction disk pack recess so that fluid can be supplied to the friction disk pack.
- the fluid guide channel extends in the axial direction to a bearing in order to supply fluid to it.
- DE 10 2011 086 376 B4 discloses an oil supply device for multi-disk brakes in a transmission module running in slip mode.
- the oil supply device includes an oil channel, the oil flow of which is controlled by a valve and provides additional amounts of oil at defined points in slip operating phases.
- an inner disc carrier is provided with a collecting channel that runs around at a constant diameter. Oil sprayed onto the collecting trough reaches the planetary gear set and the multi-disk brake through elongated holes in the inner disk carrier.
- a clutch arrangement for a drive train of a motor vehicle is known from EP 3 354 920 A1, with a wet-running friction plate clutch, a support plate against which the plate pack is supported axially, an axially movable pressure plate for loading the plate pack, an actuating device for the friction plate clutch and a Flow controller for controlling an oil volume flow through the clutch.
- the inner disk carrier of the clutch has several bores in an axial overlapping area with the disk pack, through which lubricant can flow to the disk pack.
- the flow regulator has an actuator, which can be adjusted by the actuating device, with a plurality of screen sections for covering the mouth areas of the openings. This enables the oil supply to be controlled as required.
- US Pat. No. 8,388,486 B2 discloses a drive train with a rear drive axle that can be switched on or off as required. For this purpose, a controllable coupling between the differential and a side shaft is provided in the rear differential arrangement.
- the object of the present invention is to propose a fluid guide arrangement that enables reliable fluid supply and that is easy to produce is.
- the object is further to propose a clutch unit with such a fluid guide arrangement, which provides a sufficiently good cooling performance, in particular in the slipping operation of the clutch.
- a fluid guide arrangement for a friction disk clutch comprising: an inner disk carrier with a longitudinal axis and with a carrier section, a shoulder section and a shaft section, the carrier section having a connection structure radially on the outside with projections and recesses distributed over the circumference in order to Inner disks with a suitable counter-structure to be held in a rotationally fixed and axially displaceable manner; and a fluid distribution element that is axially firmly connected to the inner disk carrier, the fluid guide element having an annular catch section in which inflowing fluid can be caught, and a plurality of tab sections distributed over the circumference, which extend in the axial direction and each have a radial through-opening exhibit; the inner disk carrier has a plurality of longitudinal grooves radially on the outside over the circumference, which extend axially from the shoulder section into the carrier section, the tab sections of the fluid distribution element being accommodated on the outside in the longitudinal grooves of the inner disk carrier or covering them, so that between
- the fluid guide arrangement offers the advantage that the fluid can flow quickly from the catch section along the tabs of the fluid guide element in the longitudinal grooves of the inner plate carrier to the plate pack.
- the circumferentially distributed tabs distribute the fluid over the circumference.
- the fluid guide element can also be referred to as a Fluidver distribution element.
- the longitudinal grooves in the inner disc carrier provide a stepless geometry, which promotes an even, fast flow of the fluid. Overall, this provides very efficient passive cooling, so that the fluid guide arrangement is particularly suitable in clutch units for the transmission of high torques at low speeds at the same time.
- the fluid serves to dissipate the heat generated by the friction and to lubricate the components that come into frictional contact with one another.
- the fluid can also be referred to as a coolant or lubricant.
- an oil is used as the fluid.
- the front part of the oil baffle preferably has a circular, closed oil collector geometry which is firmly mounted on the inner plate carrier. The fluid deflected radially outwards by the rotating inner disk carrier is thus caught and flows along the inner wall of the catch section to the tab sections.
- the annular catch section can have a radially inwardly directed constriction at its axial end. This constriction prevents the fluid from flowing back out of the annular section back into the housing interior, in which the inner disk carrier is rotatably mounted.
- the fluid guide element can expand conically, starting from the axial end, in the axial direction toward the tab sections. Both measures contribute to improved flow behavior or a larger fluid volume flow and thus to efficient cooling.
- the annular catch portion of the fluid distribution member is preferably closed circumferentially and extends axially beyond the shoulder portion.
- the ring-shaped catching section can protrude beyond the side surface of the shoulder element in particular by a length of at least 0.1 or 0.2 times the axial length of the carrier section. Due to this configuration, the catching section forms a relatively large annular space in which oil splashing around can collect and from here flow on to the lamellar sections.
- the fluid distribution element can have an in particular cylindrical connecting section, which is pushed onto an outer peripheral surface of the shoulder section of the carrier element. Since in the fluid connection element according to a possible embodiment a non-positive connection can be connected to the carrier element, for example by means of a press connection. Alternatively or in addition, the fluid guide element can also be connected to the carrier element via form-fitting connection elements, for example by means of a latching connection. Corresponding latching elements could be provided on the cylindrical connecting section and/or on the ends of the tab sections.
- the shape of the tab sections is in principle arbitrary and is preferably adapted to the design of the longitudinal grooves of the inner disk carrier.
- the tab sections can be designed as elongate elements that extend in the axial direction, that is, parallel to the longitudinal axis; they can also be referred to as bar elements.
- the tab sections of the fluid distribution element can have radially outwardly directed depressions.
- the reductions can be designed as elongated formations or bulges.
- the countersinks increase the area moment of inertia in the radial direction, which improves rigidity and prevents deflection at high speeds.
- the indentations or bulges preferably have a smaller height than the radial height of the connecting structure. Radial gaps can be provided between the tab sections and the lamellae connected to the carrier element.
- At least some of the radial through-openings of the tab sections are positioned axially offset from one another.
- the oil can flow to the disk pack in different axial areas or different transverse planes, so that overall an even distribution of the oil and a good cooling effect over the length are achieved.
- An arrangement of the through openings in the tab sections is particularly favorable in such a way that all openings together cover at least half, preferably two thirds, of the length of the connection structure for the slats.
- the number of tabs distributed over the circumference can be selected as required, for example the fluid distribution element can have two, three, four or more tab sections, which can be distributed particularly evenly over the circumference.
- the number and arrangement of circumferentially distributed tab sections preferably corresponds to the number and arrangement of the longitudinal grooves in the inner disk carrier.
- the tab sections cover the longitudinal grooves of the inner disc carrier radially on the outside, so that a substantially closed channel is formed between the respective longitudinal groove and the associated tab section, through which the fluid flows to the opening.
- a trough shape is thereby formed in which the oil flows to the opening.
- the tab sections cover the longitudinal grooves as far as possible.
- the tab sections each in a radial view, can cover a clear surface of the associated longitudinal groove, for example by at least 90%.
- the oil guiding element can be produced as a formed sheet metal part made of a me-metallic material.
- it can also be made of plastic, which can offer design advantages, such as the provision of clamping or locking features.
- the inner disk carrier can be manufactured as a forged part and/or by mechanical processing.
- the longitudinal grooves and the connecting structure can be produced by forming or by machining.
- the longitudinal grooves are preferably arranged between two recesses of the connecting structure in the circumferential direction.
- the maximum width of the tab sections can be smaller, for example, than the circumferential distance between three or two recesses of the connecting structure that are adjacent in the circumferential direction.
- the bottom of the longitudinal grooves of the inner disk carrier is preferably on a smaller radius than a lowest area of the connection structure for the inner disks.
- the toothing elements for the disks can extend radially outwards, while the grooves are formed radially inwards.
- the depth of the longitudinal grooves can be, for example, between 0.5 times and 1.5 times the radial height of the connecting structure.
- the longitudinal grooves preferably extend over at least 75% of the axial extension of the connection structure for the slats.
- the grooves can have grooves directed radially inwards, so that fluid from the catch section can flow easily into the grooves.
- the longitudinal grooves can in particular be closed axially.
- the inner disk carrier can have a central longitudinal bore and a plurality of radial passage openings to the longitudinal grooves distributed over the circumference. In this way, additional oil can be supplied to the lamellae from the central inner opening of the lamellar carrier. Depending on the operating state, the openings can also prevent a fluid build-up in the fluid channels. Fluid can flow from the longitudinal grooves through the radial openings into the central longitudinal bore and thus returns to the fluid circuit, with additional components such as bearings or seals being able to be lubricated if necessary.
- the central longitudinal bore can have an inner turning, with the radial passage openings in the carrier section being formed in the axial overlapping area of the inner turning with the outer longitudinal grooves.
- the solution also consists in a clutch unit for a drive train of a motor vehicle, comprising: a wet-running friction disk clutch with an outer disk carrier, in which a disk pack of outer disks and inner disks is arranged; a support plate against which the disk pack is axially supported; an axially movable pressure plate for axially loading the disk pack; an actuating device for actuating the friction plate clutch by axial movement of the pressure plate; a fluid guide arrangement according to one or more of the above-mentioned embodiments, wherein the inner disk carrier is mounted so that it can rotate about the axis of rotation relative to the outer disk carrier, with inner disks of the disk pack being connected to the connecting structure of the inner disk carrier in a rotationally fixed and axially movable manner, so that fluid flows when the inner disk carrier rotates flows from the catch portion along the inner wall of the fluid distribution member to the tab portions to lubricate the disk pack.
- the clutch unit enables a drive train to be switched on or off as required.
- the arrangement can be designed in the drive train for a vehicle with a driven axle, for a four-wheel drive vehicle, for a fly-brid vehicle and/or an electric vehicle.
- the clutch unit can be arranged anywhere in the drive train in the power path between a drive source and the wheels, for example in front of, in or behind a transmission and/or in front of, in or behind an angular gear and/or in front of, in or behind a transfer case (PTU ) and/or within a propeller shaft or in front of, in or behind a differential gear and/or in a sideshaft.
- PTU transfer case
- a clutch unit according to the invention has the advantage that it can provide high torques at low speeds at the same time due to the effi cient oiling system.
- the fluid distribution arrangement has a supporting effect in order to retrieve the entire potential of the controllable clutch.
- oil is directed to the longitudinal grooves, where it can flow through the holes in the tab sections as a result of centrifugal force to the outside of the disk pack.
- the oil can get back into the oil sump through corresponding holes in the outer plate carrier.
- the flowing oil can also cool and lubricate other moving mechanical components such as bearings or seals.
- a controllable actuating device which can move the pressure plate in the direction of the disk pack, ie in the closing direction, or away from the disk pack, ie in the opening direction.
- the actuating device can have any configuration in order to generate a compressive force.
- an electromotive or hydraulic shear actuator can be used.
- An electromotive actuator may include a rotary drive and a ball ramp assembly that translates rotary motion into axial motion.
- the solution also consists in a transmission arrangement for a drive train of a motor vehicle, comprising: a differential gear, which is designed to divide an input torque into two output parts, and a clutch unit as previously described, wherein the shaft portion of the inner disk carrier is non-rotatably connected to one of the two output parts.
- a gear arrangement can, if necessary, transmit the torque introduced by a longitudinal drive shaft to the associated axle, or switch off the drive axle, with all intermediate positions of the friction clutch also being possible.
- FIG. 1 shows a fluid guide arrangement according to the invention in a three-dimensional exploded view
- FIG. 2 shows the fluid guide arrangement from FIG. 1 with a disk pack in a longitudinal section
- FIG. 3 shows a detail of the fluid guide arrangement from FIG. 2 with the oil flow shown
- FIG. 4 shows the fluid guide arrangement from FIG. 1 with a disk pack in a cross section or axial view
- FIG. 5 shows a clutch unit according to the invention with a fluid guide arrangement according to FIG. 1 in a three-dimensional representation
- FIG. 6 shows a transmission arrangement with a clutch unit from FIG. 5 in a longitudinal section.
- FIGS 1 to 3 show a fluid guide arrangement 2 according to the invention for a friction plate clutch, in particular for a drive train of a motor vehicle.
- the fluid guide arrangement 2 has an inner disk carrier 3 with a longitudinal axis A3 and a fluid guide element 4, which are firmly connected to one another.
- the inner disc carrier 3 comprises a carrier section 5 for inner discs, a shaft section 6 for non-rotatable connection with a drive part and a shoulder section 7 arranged in between can be bound.
- the inner disk carrier 3 has a plurality of longitudinal grooves 11 on a radially outer peripheral surface over the circumference, which axially extend, starting from the shoulder section 7 , into the carrier section 5 .
- the inner disk carrier 3 can be produced, for example, by forging as a formed part, where alternatively or additionally production by mechanical machining such as turning, drilling or milling is also possible.
- the fluid guide element 4 can be produced, for example, as a formed sheet metal part made of a metallic material or plastic.
- the fluid guide element 4 has an annular catching section 12 in which the inflowing fluid can be collected, and several Laschenab sections 13 distributed over the circumference, which extend in the axial direction and each have a radial through-opening 14 through.
- the tab portions are generally referred to by the reference numeral 13, with individual tabs also being designated 13, 13', 13", 13"'. The same applies analogously to the openings 14.
- the tab sections 13 are accommodated on the outside in the longitudinal grooves 11 of the inner disk carrier 3 or cover them radially outwards.
- the inner disk carrier 3 and the fluid guide element 4 work together in an advantageous manner, in that cooling oil can easily flow from the catch section 12 along the inner wall 15 of the fluid guide element 4 into the longitudinal grooves 11 of the carrier element or along the tab sections 13 and through the openings 14 of the fluid guide element 4 to the Disk pack can flow.
- the course of the flow is shown with arrows P in FIG.
- the longitudinal grooves 11 in the inner disk carrier 3 provide a stepless geometry so that the cooling oil can flow easily to the disk set. Further preferred details are described below.
- the annular catch section 12 has a radial constriction 16 at its axial end, which forms a support for the oil in the annular space 17 and thus prevents the oil from flowing back.
- a radial constriction 16 As can be seen in particular in FIG the wall of the catching section 12, starting from the radial constriction 16, conically in the direction of the tab sections 13.
- the annular catching section 12 projects laterally beyond the shoulder section 7 in the direction of the shaft section 6, axially.
- the length of the catch section 12 can be, for example, at least 0.1 or 0.2 times the length of the tab sections 13 .
- the fluid guide element 4 can have a particularly cylindrical connecting section 18, which is seated on the outer peripheral surface 19 of the shoulder section 7 with a press connection. It goes without saying that other connecting means for connecting the fluid guide element 3 to the inner disk carrier 3 can also be provided, for example positive and/or material connections.
- the tab sections 13 extending axially away from the annular base body each have a countersink 20 that curves radially outwards, starting from a circular radius of the base body, which can also be referred to as a bulge.
- the depressions or bulges cause greater rigidity, so that the tabs do not bend open even at higher speeds.
- the fleas of the bulges is preferably designed in such a way that the tabs are always not in contact with the clutch plates.
- the radial passage openings 14 to the Lamel len are arranged in the bulges 20.
- the radial through-openings 14 are arranged in the tab sections 13 in an axially offset manner with respect to one another. In this way, the oil can flow to the plate pack in different axial areas or in different transverse planes.
- an opening 14 is axially adjacent to the ring portion, an opening 14' is a little axially offset thereto, a further opening 14" is approximately in a central area of the tab and one adjacent to the tab end.
- the tab sections 13 form a cover for the longitudinal grooves 11 of the inner disc carrier 3, so that between the longitudinal grooves 11 and the tab sections 13 a substantially closed channel 21 is formed through which the fluid flows to the openings 14 .
- a trough shape is formed by the longitudinally extending bulges 20 directed radially outwards, along which the oil flows and then emerges from the respective opening 14 due to the centrifugal force.
- the tab sections 13 cover the longitudinal grooves 11 as far as possible, for example by at least 90%.
- the circumferentially distributed longitudinal grooves 11 form a plurality of connecting segments distributed over the circumference, which jointly form the connecting structure 8 of the inner disk carrier 3 .
- Each connecting segment is formed as a longitudinal toothing with teeth and tooth gaps in between.
- the longitudinal grooves 11 are adjacent to recesses 10 of the connecting structure 8 is arranged in the circumferential direction. In other words, the bottom of the longitudinal grooves 11 of the inner plate carrier 3 is on a smaller radius R11 than the deepest areas of the recesses
- the depth of the longitudinal grooves can be between 0.5 times and 1.5 times the radial height of the connecting structure 8, for example.
- the longitudinal grooves 11 have a closed end in the axial direction, and they can extend over at least 75% of the axial length of the connecting structure 8 .
- the width of the longitudinal grooves 11 or the tab sections 13 can, for example, be smaller than the circumferential distance between three or two recesses 10 adjacent in the circumferential direction. At the shoulder ends, the longitudinal grooves
- the inner disk carrier 3 can have a central longitudinal opening 23 and a plurality of radial through-openings 24 to the longitudinal grooves 11 distributed over the circumference. Excess oil can thus flow radially inwards in order to prevent oil from accumulating in the fluid channels, or depending on the operating state, additional oil can be supplied to the slats from the central inner opening 23 of the slat carrier.
- the central longitudinal opening 23 can have an inner recess 25, where at the radial through-openings 24 in the support section 5 in the axial Kochde ckungs Kunststoff the inner recess 25 with the outer longitudinal grooves 11 is formed are. In this way, the radial openings 24 can be produced in a simple manner, in particular without separate drilling processes.
- FIG. 5 shows a perspective view of a clutch unit 26 according to the invention with a fluid guide arrangement 2 according to the invention, from which further details emerge from FIG. 6, which shows a longitudinal section through the clutch.
- the clutch unit 26 includes a wet-running friction plate clutch 27 and an actuating device 28 for controlling the torque that can be transmitted by the friction plate clutch.
- the friction disk clutch 27 comprises the inner disk carrier 3, with which the inner disks 29 are connected in a rotationally fixed and axially movable manner, and an outer disk carrier 30, with which the outer disks 31 are connected in an axially movable and rotationally fixed manner.
- the outer discs 31 and inner discs 29 are arranged axially alternately and together form a disc pack 32.
- the disc pack 32 is axially supported in a first axial direction against a support portion 33 of the outer disc carrier 30.
- a pressure plate 34 which can be moved axially by the controllable actuating device 28 , is provided for loading the disk set 32 .
- the outer disk carrier 30 is rotatably mounted via a first bearing 59 in the housing 44 and a second bearing 60 on a journal portion of the inner disk carrier 3 about the axis of rotation A3.
- the actuating device 28 is designed or controllable in such a way that the torque to be transmitted by the friction disk clutch 27 can be variably adjusted as required.
- any position can also be used by means of the friction disk clutch 27 intermediate position can be realized.
- the torque to be transmitted can be determined, for example, in an electronic control unit (ECU) on the basis of continuously sensed driving condition variables of the motor vehicle.
- the electronic control unit can be a corresponding control pass the warning signal on to the actuating device 28, which then applies pressure to the pressure plate 34 accordingly, so that the desired torque is transmitted by the friction plate clutch 27.
- the actuator 28 includes a ball ramp mechanism and a drive unit.
- the ball ramp mechanism has a support ring 36, which is axially supported against a stationary component, and an adjusting ring 37 which is opposite the support ring 36 and can be driven in rotation about the axis of rotation A3.
- In the opposite faces of the support ring 36 and adjusting ring 37 are distributed over the circumference ball grooves 38, 39 arranged which have a variable depth over the circumference and in each of which a ball is accommodated.
- an electric motor serves as a drive, which can rotate the adjusting ring 37 in relation to the support ring 36 via a gear train 38 .
- the gear train 38 comprises a drive wheel 40 which can be driven in rotation by the electric motor and which is drivingly connected to an output wheel 41 .
- the output wheel 41 is connected to the adjusting ring 37, in particular designed in one piece with it.
- the adjusting ring 37 can be rotated in a first direction of rotation or in the opposite second direction of rotation.
- rotating the adjusting ring 37 relative to the support ring 36 in a first direction of rotation causes the balls held in the ball grooves to run into areas of shallower depth, see above that the adjusting ring migrates axially in the direction of the clutch 27.
- the adjusting ring 37 is axially supported via the axial bearing 35 against the pressure plate 34, which acts on the disk pack.
- the clutch unit 26 causes very good cooling of the disk set even at low speeds and high torques.
- Such a clutch unit can in principle be used anywhere in the drive train of a motor vehicle.
- An application example for a clutch unit 26 according to the invention is in a transmission arrangement 42 according to FIG. 6, which is described below.
- the gear assembly 42 includes a differential gear 43 with a stationary housing 44 in which a differential carrier 45 is rotatably mounted by means of two bearings 46, 47 about a rotational axis A45.
- a ring gear 48 is provided, which is firmly connected to the differential carrier, for example by means of a welded connection or screw connections.
- a plurality of differential gears 49 are mounted on a pin 50 so as to be rotatable about a pin axis.
- the two differential gears 49 rotate together with the differential carrier 45 and each mesh with a first and a second drive wheel 51, 52, which are arranged coaxially to the axis of rotation A45.
- the two output gears 51, 52 which can also be referred to as sideshaft gears, each have longitudinal teeth 53 (splines) into which a corresponding counter-toothing of a drive shaft can engage for torque transmission.
- the two driven gears 51, 52 can be supported axially with respect to the differential carrier 45 via interposed sliding disks.
- the housing 44 is in particular constructed in several parts and comprises a transmission-side housing section 54, in which the differential gear 43 is accommodated, and a clutch-side housing section 55, in which the clutch unit 26 is accommodated.
- the two housing sections are connected to one another via flanges, without being limited thereto.
- an intermediate plate 56 is provided, in which the bearing 46 for the differential basket 45 is added.
- the inner disc carrier 3 of the clutch unit 26 is connected to the drive wheel 51 which is adjacent to the clutch and extends through a through hole 57 in the intermediate plate 56.
- the actuating device 28 is arranged axially between the intermediate plate 56 and the clutch unit 26, with the support ring 36 being axially supported against the intermediate plate is.
- the intermediate plate 56 has in the region of the fluid guide element 4 a sleeve-shaped set to 58 or collar, the section with axial overlap to Fangab 12 extends into the annular space 17 of the fluid guide element. In this way, an oil labyrinth is formed, so that oil splashing around can be guided well from the fluff attachment into the annular space 17 and from there into the channels 21 .
- the transmission arrangement 42 can provide high torques at low speeds and transmit them to the two sideshafts.
- the fluid distribution arrangement 2 has a favorable effect in order to call up the entire potential of the controllable clutch.
- the oil flowing through the clutch can also cool and lubricate other movable mechanical components such as bearings or seals of the clutch unit 26 or the transmission.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2021/067169 WO2022268310A1 (de) | 2021-06-23 | 2021-06-23 | Fluidleitanordnung für eine reiblamellenkupplung und kupplungseinheit mit einer fluidleitanordnung |
JP2023566545A JP2024515326A (ja) | 2021-06-23 | 2021-06-23 | 摩擦多板クラッチ用の流体案内アセンブリおよび流体案内アセンブリを備えたクラッチユニット |
DE112021007865.8T DE112021007865A5 (de) | 2021-06-23 | 2021-06-23 | Fluidleitanordnung für eine Reiblamellenkupplung und Kupplungseinheit mit einer Fluidleitanordnung |
CN202180099724.4A CN117545937A (zh) | 2021-06-23 | 2021-06-23 | 用于摩擦片离合器的流体引导装置以及具有流体引导装置的离合单元 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2021/067169 WO2022268310A1 (de) | 2021-06-23 | 2021-06-23 | Fluidleitanordnung für eine reiblamellenkupplung und kupplungseinheit mit einer fluidleitanordnung |
Publications (1)
Publication Number | Publication Date |
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WO2022268310A1 true WO2022268310A1 (de) | 2022-12-29 |
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ID=76796938
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/EP2021/067169 WO2022268310A1 (de) | 2021-06-23 | 2021-06-23 | Fluidleitanordnung für eine reiblamellenkupplung und kupplungseinheit mit einer fluidleitanordnung |
Country Status (4)
Country | Link |
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JP (1) | JP2024515326A (de) |
CN (1) | CN117545937A (de) |
DE (1) | DE112021007865A5 (de) |
WO (1) | WO2022268310A1 (de) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4841807A (en) * | 1988-03-18 | 1989-06-27 | Navistar International Transportation Corp. | Semi-floating differential pinion gear and lubrication thereof |
US8388486B2 (en) | 2009-08-11 | 2013-03-05 | Magna Powertrain Of America, Inc. | AWD vehicle with active disconnect coupling having multi-stage ball ramp |
DE102011086376B4 (de) | 2011-11-15 | 2015-05-07 | Zf Friedrichshafen Ag | Ölzufuhrvorrichtung für eine Lamellenbremse |
DE102015220446B3 (de) | 2015-10-20 | 2016-12-15 | Magna powertrain gmbh & co kg | Nasslaufende Kupplungseinheit |
US20170102065A1 (en) * | 2014-03-10 | 2017-04-13 | Honda Motor Co., Ltd. | Lubricating structure for differential device |
EP3354920A1 (de) | 2017-01-31 | 2018-08-01 | GKN Driveline Bruneck AG | Kupplungsanordnung für einen antriebsstrang und getriebeanordnung mit einer solchen kupplungsanordnung |
-
2021
- 2021-06-23 DE DE112021007865.8T patent/DE112021007865A5/de active Pending
- 2021-06-23 CN CN202180099724.4A patent/CN117545937A/zh active Pending
- 2021-06-23 JP JP2023566545A patent/JP2024515326A/ja active Pending
- 2021-06-23 WO PCT/EP2021/067169 patent/WO2022268310A1/de active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4841807A (en) * | 1988-03-18 | 1989-06-27 | Navistar International Transportation Corp. | Semi-floating differential pinion gear and lubrication thereof |
US8388486B2 (en) | 2009-08-11 | 2013-03-05 | Magna Powertrain Of America, Inc. | AWD vehicle with active disconnect coupling having multi-stage ball ramp |
DE102011086376B4 (de) | 2011-11-15 | 2015-05-07 | Zf Friedrichshafen Ag | Ölzufuhrvorrichtung für eine Lamellenbremse |
US20170102065A1 (en) * | 2014-03-10 | 2017-04-13 | Honda Motor Co., Ltd. | Lubricating structure for differential device |
DE102015220446B3 (de) | 2015-10-20 | 2016-12-15 | Magna powertrain gmbh & co kg | Nasslaufende Kupplungseinheit |
EP3354920A1 (de) | 2017-01-31 | 2018-08-01 | GKN Driveline Bruneck AG | Kupplungsanordnung für einen antriebsstrang und getriebeanordnung mit einer solchen kupplungsanordnung |
Also Published As
Publication number | Publication date |
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JP2024515326A (ja) | 2024-04-08 |
DE112021007865A5 (de) | 2024-04-04 |
CN117545937A (zh) | 2024-02-09 |
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