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WO2010081451A1 - Ensemble embrayage - Google Patents

Ensemble embrayage Download PDF

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Publication number
WO2010081451A1
WO2010081451A1 PCT/DE2009/001805 DE2009001805W WO2010081451A1 WO 2010081451 A1 WO2010081451 A1 WO 2010081451A1 DE 2009001805 W DE2009001805 W DE 2009001805W WO 2010081451 A1 WO2010081451 A1 WO 2010081451A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
clutch
clutch unit
axially
axial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE2009/001805
Other languages
German (de)
English (en)
Inventor
Johannes Arnold
Oliver Nöhl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Priority to DE112009003885T priority Critical patent/DE112009003885A5/de
Publication of WO2010081451A1 publication Critical patent/WO2010081451A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/66—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being metallic, e.g. in the form of coils
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/78—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings
    • F16D3/79—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings the disc or ring being metallic

Definitions

  • the invention relates to a clutch unit for a drive train with at least one hydraulically actuated by a pressure medium wet clutch.
  • Such coupling units are known for example from DE 10 2006 008 205 A1.
  • two radially superimposed wet clutches are cooled by means of a pressure medium flow.
  • the radially inwardly supplied pressure medium is skimmed off radially outside the slats of the wet clutches by means of a scoop tube.
  • a clutch unit for a drive train with a drive unit and a subsequently arranged gear with at least one arranged in a driven by the drive unit housing wet clutch with on an input side and an output side plate carrier and released in the axial direction alternating lamellae and friction plates , wherein the fins and friction plates are clamped by an axially displaceable piston against an end plate and the pressure means for actuating the at least one wet clutch and / or for cooling the friction plates by means of a feeder from the transmission via rotary unions introduced into the housing and discharged by a scoop again and scoop and feeder are designed in modular design.
  • the clutch unit may include one or two radially superimposed wet clutches, which are acted upon axially by means of axially displaceable pistons, for example, hydraulically by supplying pressure medium or by non-hydraulic, such as electrical actuators and interposition of actuation bearings.
  • pressure medium can be supplied and skimmed off through the scoop pipe.
  • the housing of the clutch unit is received on the drive shaft, such as the crankshaft of a drive unit, such as an internal combustion engine, it is equal to axial and / or tumbling oscillations of the drive shaft of advantage to receive the scoop axially floating between a housing wall of the transmission and the housing of the clutch unit.
  • the scoop tube and the feed device form a module which is brought together in the assembly of the clutch unit and the transmission, wherein the scoop tube is received in the clutch unit and is centered on the pre-mounted on the transmission housing feed device.
  • the feed device can be designed in a sandwich construction, in that a structural unit with an annular core is formed with at least one feed passage communicating with a rotary feedthrough and at least one outflow communicating with the drawpipe, and sleeves arranged radially inside and outside the core are formed.
  • a centered receptacle for the scoop and a feeder via which at least one, preferably two pressure medium channels for two wet clutches of a double clutch for a dual clutch transmission can be provided, of which via rotary unions the pressure medium into corresponding pressure chambers for the axial displacement of Piston and optionally for simultaneous cooling of the friction plates or their coverings can be brought.
  • a further pressure medium channel can be provided exclusively for the cooling of the friction linings.
  • the core is advantageously made of plastic, for example reinforced plastic or of light metal such as aluminum and its alloys, preferably in an injection molding or die casting process.
  • the radially inner sleeve has, in accordance with the number of pressure channels, an opening aligned with the rotary feedthrough or passages, seals being provided on the outer surface of the sleeve for sealing the rotary feedthrough and the opening, which are preferably included in the introduction of the rotary unions and the seals Component, such as the clutch hub to be calibrated.
  • the core is sealed against the sleeves, with elastomeric sealing tions and / or in the sleeves after insertion of the core molded, extending over the circumference of the sleeves beads may be provided.
  • the scoop is centered during the assembly process of the clutch unit and gear on the inner sleeve, wherein the feed device is pre-mounted on the housing wall of the transmission.
  • at least one, preferably a plurality of discharges between scoop and core are formed, which are preferably arranged radially outside the pressure channels of the core and have a connection to the transmission sump.
  • the scoop tube which is preferably made of plastic, a deflection of the pressure medium flow from the preferably radially aligned scoop arms into an axially extending pressure medium flow is provided.
  • the scoop can be provided with a single scoop or more flooded, preferably double-flow with two scoop arms, with one inflow, each one inflow of the scoop arms opens into a separate discharge of the core.
  • a pump drive for a transmission oil pump, for example, for actuating the transmission, the at least one wet clutch and / or the cooling of this directly through the housing of the clutch unit, so that it regardless of the operating state of the at least one wet clutch of the drive unit is driven directly.
  • a pump drive can be accommodated on the housing wall of the transmission in a rotatable and centered manner radially outside the feed device.
  • the recording takes place by means of a roller bearing, for example by means of a needle bearing, which allows an axially limited displacement of the pump drive relative to the gear housing and the housing of the clutch unit.
  • thrust washers for example, for actuating the transmission, the at least one wet clutch and / or the cooling of this directly through the housing of the clutch unit, so that it regardless of the operating state of the at least one wet clutch of the drive unit is driven directly.
  • a pump drive can be accommodated on the housing wall of the transmission in a rotatable and centered manner radially outside the feed device.
  • a deep groove ball bearing can be provided instead of the needle bearing, by means of which the pump drive can be axially fixed, so that the thrust washers can be omitted.
  • an axially limited displacement is provided between the housing of the clutch unit and the pump drive, so that the axial and tumbling oscillations of the housing relative to the firmly fixed to the housing wall of the transmission pump drive can be compensated.
  • the pump drive is formed from a ring gear, which is received by means of an axial projection on the rolling bearing on the housing wall.
  • the housing may have an axial extension with an axial profile, for example, axially projecting, circumferentially distributed lugs, which in a centering of the axial shoulder with the ring gear a positive connection in the circumferential direction with a complementary axial profile of the ring gear, for example corresponding axial grooves or radially inwardly extending noses.
  • a sealing washer with a seal on the axial shoulder of the housing radial shaft seal, which is connected to a sealing disc which seals against the housing wall of the transmission.
  • Figure 2 is an exploded view of a module consisting of scoop and
  • Figure 3 is a view of a core of the module of Figure 2 from an amended
  • FIG. 4 shows a view of the radially inner sleeve of the module of FIG. 2,
  • FIG. 5 shows a partial section through the sleeve of FIG. 4,
  • FIG. 6 shows a section through the feed device of FIG. 2,
  • FIG. 7 is a sectional view of the feeder of FIG. 2;
  • FIG. 8 shows a section through the preassembled feeding device of FIG. 2,
  • FIG. 9 shows a detail of FIG. 1 with the feed device and rotary unions
  • FIG. 10 shows a detail of the clutch assembly of FIG. 1 during assembly
  • FIG. 11 shows an exploded view of the pump drive of FIG. 1.
  • Figure 1 shows the clutch unit 1 in the assembled state as a partial section above the axis of rotation 2.
  • the clutch unit 1 is disposed between the drive unit, of which only the crankshaft 20 is shown, and the transmission, of which only the transmission housing 22 is shown.
  • the housing 8 of the clutch unit 1 is at the Crankshaft 20 is received by means of an axially flexible, axial vibrations and tumbling vibrations of the crankshaft 20 compensating drive plate 21 as Flexplate and is driven by this.
  • the housing 8 is rotatably supported by means of the rolling bearing 23 on the gear housing 22, wherein between the annular axial projection 24 of the housing part 7 and the rolling bearing 23 of the ring gear 25 for the transmission oil pump, which can also circulate the pressure means of the clutch unit 1, by means of a sleeve-shaped approach arranged and driven by the projection 24.
  • the from the sprocket 25 and the rolling bearing 23, which also forms a storage for the housing 8 on the housing wall of the gear housing 22 via the sprocket 25, formed pump drive is preferably preassembled on the transmission housing 22, wherein in the connection of the clutch unit 1 and the transmission Scoop 14 is centered in the feeder and the guide pins 83 pass through this and axially displaceable in the gear housing 22 and the scoop tube 14 rotatably stored stock.
  • a sealing disc 26, for example, made of sheet metal or plastic with a seal 27 as radial shaft sealing ring to the projection 24 for sealing the housing 8 relative to the transmission housing 22 is provided.
  • the input part of the torsional vibration damper 12 is formed by the housing, which are formed in the embodiment shown in the embodiment of preferably two circumferentially arranged arc spring groups each with two radially nested sheet springs 30, 31, by means of the in the end faces of the bow springs 30, 31 radially engaging drivers 17, 18 acted upon in the circumferential direction.
  • the drivers 17 are formed from over the circumference of the housing part 6, the driver 18 formed by flared portions of the annular flange 16.
  • the annular flange 16 is applied after insertion of the bow springs 30, 31 to the radial shoulder 32 of the housing part 6 and axially fixed, such as welded and serves the captive recording of the bow springs 30, 31 before assembly and the axial guidance of the bow springs 30, 31 during the operation.
  • a wear protection shell 33 is provided, which are arranged in two parts in the circumferential direction between the drivers 17 are floating relative to the housing 8 can be stored.
  • the torsional vibration damper 12 is effective in the torque flow before the wet clutches 28, 29, so that the output part of the torsional vibration damper 12 at the same time the ge common input part 13 of the wet clutches 28, 29 is.
  • the input part 13 has a flange 13a with the output side drivers 19 of the torsional vibration damper 12, which are formed as radially expanded arms of the flange 13a and in the non-tensioned state of the bow springs 30, 31 on the same circumference of the driver 17, 18, the end faces of the bow springs Apply 30, 31 and thus at a relative rotation of the housing 8 with respect to the input part 13 of the wet clutches 28, 29 cause a tension of the bow springs 30, 31, so that the relative rotations causing torque peaks are damped by the effective energy storage 11 bow springs the energy of this Momentary peaks temporarily buffering.
  • the torque of the drive unit is entered into the input part 13.
  • the input part 13 distributes the torque to the input-side disk carrier 34, 35 of the wet clutches 28, 29, which are centered and supported by means of a common carrier disk 36 which is fixedly connected to the clutch hub 37 as welded.
  • the radially outer plate carrier 34 is made in a constructed manner, while the radially inner plate carrier 35 is deep-drawn.
  • each slats 38, 39 are mounted, which alternate axially with output side friction plates 40, 41 and form a frictional engagement with axial loading.
  • the output side friction plates 40, 41 are mounted in Lamellenträgem 42, 43, each connected to a hub 44, 45 with a toothing 46, 47 connected to the transmission input shaft 48 and arranged around this, designed as a hollow shaft transmission input shaft 49 as welded and therefore are mounted on the two transmission input shafts 48, 49 and centered.
  • the two wet clutches 28, 29 configured with the clutch hub 37 as a structural unit.
  • the clutch hub 37 is mounted axially floating on the transmission input shaft 49 by means of the roller bearings 53, 54.
  • the transmission input shaft 49 is axially and radially fixedly mounted in the transmission housing 22 by means of the rolling bearing 55.
  • the floating bearing of the clutch hub 37 is limited by the two thrust washers 56, 57.
  • the thrust washer 56 is integrally formed of plastic and contains formed in the front side of the clutch hub 37 support member 58 and the lubricating oil grooves 59 formed.
  • the hub 45 is applied axially and rotatably relative to the hub 44 by means of the rolling bearing 60.
  • the hub 44 is supported by means of the roller bearing 61 axially fixed to the housing part 6 rotatable, so that the clutch hub 37 is axially supported on the Shimmario 67 by, for example, by this a defined game is set.
  • the necessary for the bearings 60, 61 axial bias is set by means of the axially effective energy storage 45a, for example, a corrugated spring, which is supported by means of the lock washer 45b on the transmission input shaft 49.
  • the clutch hub 37 is supported by means of the sealing plate 62, which is arranged on the shoulder 63 by means of the securing ring 64 axially fixed thereto, on the scoop 14, which in turn can be formed by means of the thrust washer 65, which can be designed as rolling bearings axially supported on the housing part 7.
  • the axially effective thrust washer 57 is arranged, which allows an axially limited displacement of the clutch hub 37 against its action in the direction of the housing part 7, so that the clutch hub 37 axially displaceable in both directions displaceable relative to the housing 8 displaced and therefore floating.
  • the thrust washer 57 is formed from a toothed plate 66 toothed with the support plate 66 and a firmly recorded thereon Shimmario 67, which comes into contact with a toothed with the scoop 14 thrust washer 68.
  • the two wet clutches 28, 29 are acted upon by means of a pressure medium axially displaceable piston 69, 70 which press the blades 38 and 39 axially with the friction plates 40 and 41 against an end plate 71, 72 and thereby form a frictional engagement.
  • the pressure medium is in each case from a feed device 3, which forms a module 4 with the scoop tube 14 in modular construction in the assembled state via rotary feedthroughs 73, 74 in supply lines 75, 76 and dosed into the pressure chambers 77, 78, whereby the piston 69, 70 are displaced against the action of the axially effective energy storage 79, 80 and the wet couplings 28, 29 thereby be closed depending on the applied pressure of the pressure medium.
  • the wet clutches are automatically reopened by relaxing the energy storage 79, 80.
  • the supply lines 81, 82 serve to cool the wet clutches 28, 29, in particular the friction linings of the friction plates 40, 41, which are subjected to particular thermal stress, in particular under slipping conditions of the wet clutches 28, 29.
  • the pressure medium metered in this way cools the friction plates 40, 41 and flows radially outward, from where it is skimmed off by the scoop tube 14 fixedly connected to the transmission housing 22 by means of the guide pins 83 and fed via the discharge line 84 to the transmission sump.
  • a friction device 85 may be provided between the torsional vibration damper 12 and the input part 13 of the wet clutches 28, 29, a friction device 85 may be provided.
  • a friction ring 87 can be acted upon, centered by means of the attached to the housing part 6 retaining ring 88 and by means of the axially effective energy storage 89, which may be a plate spring, for example, as shown this is braced.
  • the friction device 85 can serve as a centering of the two wet clutches 28, 29 in the housing 8 before the final assembly, as long as it is not yet centered on the transmission input shaft 49.
  • FIG. 2 shows an exploded view of the module 4 formed from the scoop tube 14 and the feed device 3.
  • the scoop tube 14 may be injection molded or die-cast from plastic or light metal, for example aluminum, and its alloys, and is double-flowed with two scoop arms 90 in the embodiment shown provided, which extend radially outward and are angled at their free ends in the circumferential direction, so that in the housing 8 ( Figure 1) introduced and centrifugally collected radially outside in the housing pressure fluid to the maximum diameter of the scoop arms 90 skimmed is axially deflected in the central center portion 91 of the scoop 14 and via the nozzle 92 in the discharge channels 94 of the core 93 of the feeder 3, which receive the nozzle 92 axially, is passed.
  • the outer diameter of the scoop arms 90 is dimensioned such that, on the one hand, an annular space with pressure medium remains radially on the outside, so that the centrifugal force pendulum 51 (FIG. 1) designed for wet conditions remains in the wet space and, on the other hand, the two wet clutches 28, 29 (FIG. 1) do not are negatively influenced by shear forces of the pressure medium in their effect.
  • lugs 95, 96 provided thrust washers 65, 68 rotatably received on the scoop tube 14.
  • the axially enlarged guide pins 83 are mounted, for example screwed, pinned or molded in one piece, which are guided through the openings 97 of the core 93 and pass through this and engage in corresponding openings of the transmission housing, so that a rotationally fixed and axially floating recording of Scoop tube 14 on the gear housing 22 (Figure 1) is made possible and thus relative displacements of the scoop tube 14 and on this accumulating clutch hub 37 ( Figure 1) are balanced with respect to the transmission.
  • the scoop tube 14 is centered on the radially inner sleeve 98 at its shoulder 99.
  • the sleeve has passage openings, of which only the passage opening 100a is visible, on, in Circumferential direction are formed as slots in order to maintain a sufficient flow cross-section to the pressure channels, of which only the pressure channel 101 is visible and which are introduced into the core 93 even with tolerance-related disorders upright.
  • the passage openings 100a are axially spaced from each other and are aligned with the rotary joints 73, 74 ( Figure 1).
  • the core 93 is surrounded by a radially outer sleeve 102.
  • the sleeves 98, 102 may be made of sheet metal and seal the core 93 from.
  • the sleeves 98, 102 may be finished at their contact surfaces to the core.
  • one or more circumferential - not shown - beads are introduced, which plastically deform the softer material of the core 93 and thereby increase the tightness of the feeder 3.
  • the feeding device 3 is screwed to the transmission housing 22 (FIG. 1) by means of the screws 103 with the shims 104 interposed. It can be provided on one of the components not shown in detail during the effective centering, wherein the scoop tube 14 is received radially relative to the housing 8 ( Figure 1) to compensate axial offsets between the clutch unit 1 and gear housing 22 ( Figure 1) , After assembly of the clutch unit 1, the scoop 14 is centered on the shoulder 99 of the inner sleeve 98. Between the core 93 and the gear housing 22 ( Figure 1) is further provided an axial seal 105 such as a molded gasket, paper seal, sealing plate or the like.
  • Figure 3 shows the core 93 in a view from the transmission-side direction with the pressure channels 101, 101a, closed by the abutment contact of the inner sleeve 98 of Figure 2 and only at the axially staggered passage openings 100 of the sleeve 98 to the axially offset from each other and mutually sealed rotary unions 73, 74 ( Figure 1) are open, so that a separation of the two pressure channels is possible.
  • the openings 97 are used to pass the guide pins 83 ( Figure 2) and form the peripheral support of the scoop tube 14.
  • the guide pins 83 are extended beyond the coupling neck 24 also to be positioned during assembly as the first element in the feeder 3 and immerse in the transmission housing 22 a.
  • the openings 106 serve to pass through the screws 103 (FIG. 2).
  • Figures 4 and 5 show the radially inner sleeve 98 from the transmission side view or in partial section with the passage openings 100, 10Oa and the radially expanded shoulder 99 for centering the scoop tube 14 ( Figure 2).
  • Figures 6 and 7 show the feeder 3 in section and in a sectional partial view.
  • the core 93 and the radially inner sleeve 98 form the pressure channels 101, 101 a.
  • the sleeve 98 with the passage openings 100, 100a forms the transition from the stationary, non-rotating feed device 3 to the rotary feedthroughs 73, 74 of the rotating clutch hub 37 (FIG. 1).
  • the discharge channels 94 are introduced in the peripheral region between the pressure channels 101, 101 a.
  • FIG. 8 shows a section through the feed device 3 in the preassembled state.
  • the complete assembly of the feed device with the core 93 radially surrounding sleeves 98, 102 screwed to the transmission housing 22.
  • the radially inner sleeve 98 is axially expanded in the central opening 107 and centered on this.
  • FIG. 9 shows a detail of the clutch assembly 1 of FIG. 1 arranged around the rotation axis 2 in section for explaining the pressure medium guidance between the transmission housing 22 and the clutch hub 37 via the feed device 3.
  • the transmission housing 22 are corresponding supply lines of the prestressed pressure medium, for example the supply line 108 provided for cooling oil, which are in communication with the pressure channels 101, 101a ( Figure 7) and are supplied via the channel 108a the wet clutches 28, 29. From there, the pressure medium passes through the introduced into the sleeve 98 passages 100, 100a to the rotary joints 73, 74 of the clutch hub 37.
  • the rotary unions can be radial bores in the clutch hub 37, which communicate with connecting channels as hollow holes of the clutch hub 37, so the corresponding wet clutches 28, 29 are actuated by the pistons 69, 70 (FIG. 1) axially displaced by means of the prestressed pressure medium conducted via the rotary unions 73, 74 to the pressure chambers 77, 78.
  • the wet space of the clutch unit can be supplied with pressure medium supplied centrally into the clutch hub 37.
  • the rotary unions 73, 74 are each axially sealed on both sides by dynamic seals 109.
  • the seals 109 are in annular grooves 110 received the clutch hub 37 and form a calibrated sealing surface 111 to the sleeve 98th
  • FIG. 10 shows the detail of FIG. 9 during assembly of the clutch unit 1 of FIG. 1 on the transmission housing.
  • the clutch hub 37 arranged in the housing 8 is pushed along the transmission input shaft 49 in the direction of the transmission housing 22, wherein the seals 109 on the inner surface of the Sleeve 98 are calibrated.
  • the inner circumference 112 of the seals 109 is correspondingly plastically deformed.
  • the seals 109 are not closed but a shock such as butt joint or T-joint.
  • the gap impact is reduced.
  • the gap closes completely due to their thermal expansion.
  • the scoop tube 14 accommodated in the housing 8 is centered by means of the insertion bevels 113 of the guide pins 83 at the openings 97 of the merely indicated core 93 of the feed device 3.
  • the axial projection 24 of the housing 8 is connected to the pump housing 5 preassembled on the transmission housing 22 and centered on this.
  • the axial projection 24 is brought into positive engagement with the toothed ring 25 rotatably received on the housing 22 by means of the roller bearing 23, so that the housing 8 entrains the toothed rim 25 in the direction of rotation by means of the axial profile 10 which comes into operative engagement with a corresponding axial profile 114 and is mounted by means of the axial projection 24 via the ring gear 25 in the transmission housing 22.
  • the axial projection 24 and thus the wet space of the housing 8 is sealed to the outside by means of the seal 27, for example, a radial shaft seal.
  • the ring gear 25 has radially inside a cutout 115 into which the seal 27 can engage axially overlapping, so that the seal can be space-neutral.
  • FIG 11 shows an exploded view of the pump drive 5 of Figure 1.
  • the sprocket 25 is rotatably received by means of an axial projection 116 on the rolling bearing 23, for example a needle bearing, on the transmission housing 22.
  • the thrust washer 117 prevents a contact of the ring gear 25 on the gear housing 22.
  • the sealing washer 26 with the seal 27 has a further thrust washer 119 for the ring gear 25.
  • the seal 27 seals against the axial projection 24 of the housing 8.
  • the ring gear 25, the rolling bearing 23, the sealing washer 26 and the thrust washer 117 are pre-assembled on the transmission housing.
  • the axial projection 24 is at the time of mounting on Inner circumference of the ring gear 25 centers and overlaps with its axial profile 10, the axial profile 114, for example in the form of circumferentially distributed lugs, so that a positive fit is formed in the circumferential direction and the ring gear 25 is driven by the housing 8.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un ensemble embrayage comprenant au moins un embrayage humide, un carter formant un espace humide, ce carter étant au moins partiellement rempli d'un fluide sous pression introduit dans l'espace humide pour actionner et/ou refroidir le ou les embrayages humides, ainsi qu'un tuyau d'évacuation pour évacuer le fluide sous pression introduit. Selon l'invention, le tuyau d'évacuation et un dispositif d'amenée du fluide sous pression sont conçus sous la forme d'un module.
PCT/DE2009/001805 2009-01-19 2009-12-22 Ensemble embrayage Ceased WO2010081451A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009003885T DE112009003885A5 (de) 2009-01-19 2009-12-22 Kupplungsaggregat

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EP3114363A2 (fr) * 2014-03-05 2017-01-11 Schaeffler Technologies AG & Co. KG Dispositif de transmission de couple
DE102016210567A1 (de) * 2016-06-14 2017-12-14 Zf Friedrichshafen Ag Doppelkupplungsgetriebeanordnung sowie Kraftfahrzeug
DE102016222457B4 (de) * 2016-11-16 2018-07-12 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung mit einer Fluidführungsbuchse
EP3638527B1 (fr) 2017-06-13 2021-04-07 Schaeffler Technologies AG & Co. KG Module hybride avec embrayage à friction refroidi hydrauliquement ainsi que groupe motopropulseur hybride
DE102017128447A1 (de) * 2017-11-30 2019-06-06 Schaeffler Technologies AG & Co. KG Fluidkanalbuchse, insbesondere für ein Kfz-Getriebe oder eine Kupplungseinrichtung
WO2020229528A1 (fr) 2019-05-14 2020-11-19 Transmisiones Y Equipos Mecanicos, S.A. De Cv Boîte à 8 vitesses
EP3969771B1 (fr) * 2019-05-17 2024-02-14 Transmisiones Y Equipos Mecánicos, S.A. de C.V. Flux d'énergie dans un embrayage concentrique double
EP3969772B1 (fr) 2019-05-17 2024-02-14 Transmisiones Y Equipos Mecánicos, S.A. de C.V. Unité d'embrayage double dans une transmission
DE102019124190B4 (de) 2019-09-10 2022-11-10 Schaeffler Technologies AG & Co. KG Trennkupplung mit drucktopfdurch- und hintergreifender Rückstellfeder mit Formschluss, Antriebsstrang und Verfahren zum Montieren einer Trennkupplung
DE102020004394A1 (de) 2020-07-22 2022-01-27 Daimler Ag Hybridantriebseinrichtung für ein Kraftfahrzeug, insbesondere für einen Kraftwagen, sowie Kraftfahrzeug
DE102021106622B3 (de) 2021-03-18 2022-07-07 Schaeffler Technologies AG & Co. KG Drehmomentübertragungsvorrichtung und Verfahren zur Montage einer Drehmomentübertragungsvorrichtung

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CN103596789B (zh) * 2011-04-04 2016-10-26 舍弗勒技术股份两合公司 用于传递转矩的装置

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