WO2009105388A2 - Système à multiple embrayage avec compensation de fluide hydraulique - Google Patents

Système à multiple embrayage avec compensation de fluide hydraulique Download PDF

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Publication number
WO2009105388A2
WO2009105388A2 PCT/US2009/034064 US2009034064W WO2009105388A2 WO 2009105388 A2 WO2009105388 A2 WO 2009105388A2 US 2009034064 W US2009034064 W US 2009034064W WO 2009105388 A2 WO2009105388 A2 WO 2009105388A2
Authority
WO
WIPO (PCT)
Prior art keywords
actuating piston
disk carrier
guide element
oil guide
external
Prior art date
Application number
PCT/US2009/034064
Other languages
English (en)
Other versions
WO2009105388A3 (fr
Inventor
Hans Jürgen HAUCK
Original Assignee
Borgwarner Inc.
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 Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2009105388A2 publication Critical patent/WO2009105388A2/fr
Publication of WO2009105388A3 publication Critical patent/WO2009105388A3/fr

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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
    • 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

Definitions

  • the present invention relates to a multiple clutch system having an external clutch and an internal clutch, which are arranged nested in the radial direction, and an actuating piston for the actuation of the external clutch, a pressure chamber being provided on one side of the actuating piston, which pressure chamber can be subjected to pressure in such a way that the actuating piston is displaced in the axial direction, and a compensation chamber being provided on the other side of the actuating piston, whereby an axial force acting on the actuating piston can be generated by rotation of the multiple clutch system by means of a radially oriented first hydraulic fluid column inside the pressure chamber, and an opposing axial force acting on the actuating piston can be generated by means of a radially oriented second hydraulic fluid column in the compensation chamber, whereby an overflow channel for the partial removal of the oil from the compensation chamber discharges into the compensation chamber in such a way that the length of the second hydraulic fluid column in the radial direction is shortened in such a way that the mutually opposing axial forces acting on
  • the two clutches each consist of a disk pack.
  • an actuating piston which can be displaced in the axial direction.
  • a pressure chamber which can be supplied with pressure in such a way that the actuating piston is displaced in the axial direction.
  • a so-called compensation chamber is provided on the other side of the actuating piston.
  • the movement of the actuating piston is thus brought about by varying the pressure inside the pressure chamber.
  • a radially oriented first hydraulic fluid column occurs inside the pressure chamber
  • a radially oriented second hydraulic fluid column occurs inside the compensation chamber.
  • the first hydrauiic fluid column in the pressure chamber causes an axiai force to act on the actuating piston
  • the second hydraulic fluid column in the compensation chamber causes an opposing axiai force to act on the actuating piston.
  • the externa! ciutch and the disks of the externa! disk pack has or have a lower service life than the internal clutch and the disks of the interna! disk pack.
  • an object of the present invention is thus to propose a multiple ciutch system having an
  • the multiple clutch system exhibits an 5 external clutch and an internal clutch, which are arranged nested in the radial direction.
  • Each of the two clutches can thus be formed, for example, from one disk pack as a plurality of inner and outer disks arranged alternately one behind the other.
  • An actuating piston is also provided for the actuation of the external clutch. Executed on one side of the actuating i o piston in relation to the axial direction is a pressure chamber, which can be supplied intentionally with pressure and/or oil pressure in such a way that the actuating piston is displaced in the axial direction.
  • a compensation chamber is executed on the other side of the actuating piston, on the other hand, if the multiple clutch system is caused to rotate, a radially oriented
  • first hydraulic fluid column occurs inside the pressure chamber, whereas a radially oriented second hydraulic fluid column occurs inside the compensation chamber. Whereas an axial force acting on the actuating piston in one direction is produced by the first hydraulic fluid column inside the pressure chamber, the second hydraulic fluid column inside the
  • compensation chamber produces an axial force acting on the actuating piston in the opposite direction, in order to bring about hydraulic fluid compensation, an overflow channel for the partial removal of the oil from the compensation chamber discharges into the compensation chamber in such a way that the length of the second hydraulic fluid column in the radial
  • the overflow channel minimises the length of the second hydraulic fluid column in the radial direction in such a way that a particularly easy hydraulic fluid compensation is achieved.
  • the oil that is led away from the compensation chamber via the overflow channel is not easily led away to the outside in the radial direction in order to be
  • the overflow channel according to the invention is arranged in such a way that the oil that is led away via the overflow channel is supplied to the external clutch, so that additional cooling medium and lubricating medium are available for the external clutch and the externa! disk pack, by means of which adequate cooling and lubrication of the externa! ciutch and an associated increase in their service life are achieved.
  • the compensation chamber is delimited among other things by the actuating piston and a disk carrier, preferably an external disk carrier of the multiple ciutch system, in which case an oil guide element is attached to the disk carrier in such a way that the overflow channel is executed between the disk carrier and the oil guide element.
  • the oil guide i o element permits a particularly simple embodiment of the disk carrier, especially as the oil guide element only needs to be attached to the completed disk carrier subsequently in order to provide the overflow channel, intricate machining of the disk carrier, in order to provide an overflow channel inside the disk carrier, is superfluous.
  • oil guide element 15 subsequently attached oil guide element also has the advantage that this can be selected, if necessary, from a multiplicity of oil guide elements, in order to achieve the desired reduction in the length of the second hydraulic fluid column in the radiai direction in a particular application. in order to be able to produce the overflow channel particularly
  • At least one projecting abutment is provided on the side of the oil guide element facing towards the disk carrier for the purpose of supporting the oil guide element on the disk carrier in a further preferred embodiment of the multiple clutch system according to the invention. If, for example, the
  • oil guide element in question is a sheet metal component
  • these projecting abutments can be produced by embossing the oil guide element in sheet form in order to achieve a particularly low production cost.
  • the overflow channel is created
  • the projecting abutments can be provided on the oil guide element in such a way that a press fit is produced when the oil guide element is pushed into or onto the disk carrier.
  • the projecting abutments provided on the oil guide element are far easier to produce than
  • the overflow channel exhibits a radially internal inlet opening and a radially externa! outlet opening, i.e. the iniet opening is arranged further inwards radialiy than the outlet opening, in 5 order to ensure the reliable and rapid removal of the oil from the compensation chamber via the overflow channel. Since the disk carrier extending in the radial direction as a rule provides axial sealing of the oil chambers inside the multiple clutch system, the radially externa!
  • outlet opening is constituted by at least one groove in the disk carrier, in order to i o permit the intentional supply of the oil that is led away via the overflow channel to the external clutch, it is preferable, therefore, for the groove to be executed in a supporting section of the disk carrier, which serves to provide radial support for the disk carrier on a clutch hub or a clutch pipe.
  • the groove constituting the externa! outlet opening couid thus be formed,
  • the groove is particularly preferable for the groove to be executed in a tubular part section of the supporting section, in which
  • tubular part section constitutes a boundary of the compensation chamber and/or the overflow channel in the radial direction.
  • the oil that is led away can thus be discharged particularly effectively via the groove associated with the overflow channel radially towards the outside before then being supplied to the external clutch.
  • a second actuating piston for the actuation of the internal clutch is provided, in which the overflow channel discharges into a further channel between the disk carrier, preferably the supporting section of the disk carrier, and the second actuating piston.
  • the further channel in a particularly preferred embodiment of the muitipie clutch system according to the invention extends in the radial direction towards the outside to such an extent that the oil that is led i o away via the further channel can be used, if necessary, for the cooling or/and lubrication of a radiaily externally located component part of the internal clutch, in an ideal case, the further channel leads outwards in the radial direction to such an extent that the oil that is led away via the further channel is conveyed past the interna! clutch in such a way that the
  • aforementioned oil provides no cooling or/and lubrication of any kind for the internal clutch.
  • the oil that is led away via the overflow channel and the further channel is prevented in this way, with the internal ciutch open, from producing any return torque there. in the case of multiple clutch systems having clutches nesting in the
  • the disk-carrying sections of the disk carriers regularly constitute a flow barrier, so that the externa! clutch in particular can only be provided with an adequate quantity of cooling oil with difficulty.
  • the further channel in the radial direction in an advantageous embodiment of the muitipie ciutch system according to the invention, the further channel in the radial direction
  • the further channel should also be configured in such a way that this extends exclusively or predominantly in the radia! direction, but without this also being inclined in the axial direction.
  • the outlet opening of the further channel in the radial direction is in aiignment with the oil passageways.
  • the oil passageways in the internal disk-carrying section in a particularly advantageous embodiment of the multiple clutch system according to the 5 invention are arranged in the radial direction towards the outside at least partially in alignment with oil passageways in a disk-carrying section of an internal disk carrier of the external clutch.
  • the oil passageways in the radial direction should thus overlap at least partially, in order for them to be able to convey the oil that has been led away directly onwards to the external i o clutch.
  • the oil passageways in the disk-carrying section of the internal disk carrier of the external clutch should be arranged radially inside the external clutch in the disk-carrying section of the internal disk carrier, in order to permit a direct supply.
  • a spring device preferably a disk spring, for pre- tensioning of the actuating piston is arranged in an initial position between the actuating piston and the disk carrier.
  • the spring device can thus be utilized for returning the actuating piston to the initial position relative to the disk carrier.
  • the spring device only has to apply a small force in order to force the actuating piston back into the initial position, so that a particularly light and space-saving spring device can be selected.
  • the aforementioned spring device in this case
  • the spring device 25 preferably a disk spring, is capable of being supported or is supported on the disk carrier with the interposition of the oil guide element. Two important advantages are associated with this.
  • the spring device which as a rule consists of a harder material than the disk carrier, is prevented on the one hand from causing wear in the support area. It is thus possible in
  • the oil guide element is capable of assembly by being pushed together, or is assembled by being pushed together, with the disk carrier, preferably in the axia! direction, and 5 particularly preferably it is capable of assembly by being pressed together, or is pressed together, so that simple assembly of the oil guide element on the disk carrier is possible.
  • the press fit in this case could be produced by the projecting abutments on the oil guide element.
  • the oil guide element is capable of being introduced or is introduced into a depression in the disk carrier.
  • a depression which can be produced by repositioning the supporting section of the disk carrier rearwards in an internally located area in the axial
  • the oil guide element in this case is preferably configured as a bowl-shaped annular component, that is to say the oil guide element is of bowl-shaped configuration, although it exhibits a
  • the oil guide element exhibits an external collar
  • the external collar is preferably supported outside the depression on the disk carrier.
  • the externa! collar can also be supported directly or indirectly on the disk carrier and thus serves, among other things, to establish the attachment position for the oil guide elements
  • the external collar of the oil guide element serves not only as an abutment or, as described below, as a seal, but rather the external collar is configured in such a way that the spring
  • the 35 device is capable, with the interposition of the external collar, of being supported or is supported on the disk carrier. As already mentioned above, it is possible by this means to ensure that the oil guide element is already retained in its attachment position by the spring device via the external collar. In addition, the external collar prevents damage to the disk carrier in the support area of the spring device. in order to achieve a particularly specific and loss-free supply of the oil that is led away via the overflow channei to the external clutch, a seai for 5 sealing the overflow channei in relation to a space other than the compensation chamber is provided on the oil guide element in a further preferred embodiment of the multiple clutch system according to the invention.
  • the seal is thus intended in particular to provide sealing of the overflow channel in relation to a further space, which is formed between the i o actuating piston and the disk carrier, but is arranged further towards the outside in the radial direction than the compensation chamber, especially as the greatest oil loss takes place as a rule via this further space, but without the possibility of making the discharged oil available to one of the two dutches for further cooling, in the embodiment described here, it is
  • the seal could preferably be configured and arranged in such a way that the overflow channei is sealed by the compression of the externa! collar of the oil guide element against the disk carrier.
  • assembly openings are provided in the actuating piston to permit the passage of an assembly tool, for example the die of a press tool, which in the axial direction are arranged at least partially in alignment with the external collar of the oil guide element.
  • 25 oil guide element can initially be assembled or pushed together with the actuating piston to form a module, and this module can then be incorporated into the multiple clutch system.
  • the dies of a press tool or similar can be passed through the assembly openings in the actuating piston in order to press against the
  • the actuating piston can be
  • the actuating piston for example, can thus exhibit a bulbous section projecting in the axial direction, which is introduced into the aforementioned depression and into the oil guide element, which, for example, is configured as a bowi- shaped annular component, in order to seal the annular gap between the actuating piston and the oil guide element, a sealing lip is provided on the actuating piston.
  • a sealing lip of this kind should be of circumferential configuration and should preferably extend in the radial and axial direction 5 in order to achieve the highest possible sealing effect.
  • At least one projecting abutment is provided on the side of the oil guide element facing towards the actuating piston.
  • This projecting abutment can be configured similarly to the aforementioned projecting abutments, for example.
  • the projecting abutment is provided on the oil guide element in i o such a way that the actuating piston in an end position is supported on the projecting abutment in the axial direction, in which case the sealing Sip is positioned at a distance from the oil guide element in the end position of the actuating piston in the axial direction. Supporting of the actuating piston on the projecting abutment can take place indirectly or directly in this case.
  • the projecting abutment prevents the sealing lip from being pressed against the oil guide element in the axial direction and thus from being deformed in the axial direction when the actuating piston is in the end position.
  • the durability of the sealing lip, and thus its tightness, are significantly increased in this way.
  • the sealing lip is arranged or configured on a sealing element and/or as part of a sealing element, in which case the
  • sealing element can be combined with the actuating piston. It is preferable in this case for the sealing element to be capable of being pushed together or to be pushed together with the actuating piston, it is particularly preferable for the sealing element to be capable of being pressed together or to be pressed together with the actuating piston, especially as the
  • connection between the sealing element and the actuating piston is then particularly easy to produce.
  • the actuating piston, the sealing element and the oil guide element can first be assembled to produce a module, in
  • this module can then be incorporated into the multiple clutch system.
  • This embodiment is advantageous in the sense that the initially separate oil guide element, by causing the same to rotate about its axis of rotation, can be pushed onto the sealing element on the actuating piston, in conjunction with which the rotation prevents the sealing lip from being folded or bent on the sealing element in the direction of attachment, as a result of which the sealing effect would be lost.
  • the module consisting of the actuating piston, the sealing element and the oil guide element thus only requires to be pushed onto the disk carrier in the axiai direction without the need for any rotation, which would be prevented by the actuating fingers.
  • the assembly openings in the actuating piston can be of benefit
  • actuating fingers for the actuation of the external clutch are provided on the actuating piston, which fingers extend through windows in the disk carrier, preferably in the supporting section of the disk carrier to the external clutch.
  • Fig. 1 depicts a partial side view of an embodiment of the multiple 5 clutch system according to the invention in a sectioned representation
  • Fig. 2 depicts the detail A in Fig. 1 as an enlarged representation
  • Fig. 1 depicts an embodiment of the multiple clutch system 2 according to the invention, in which the multiple clutch system 2 in this example is configured as a dual clutch system and a disk clutch device, in i o addition, the multiple clutch system 2 together with a torsional vibration damper 4 forms a clutch/damper unit.
  • the multiple clutch system 2 and the torsional vibration damper 4 exhibit a common axis of rotation 6, which extends in the mutually opposing axial directions 8, 10. in addition, the outwardly oriented radial direction is indicated by the arrow 12, whereas the
  • the clutch/damper unit initially exhibits an input hub 16, which is capable of being attached rigidly to an engine output shaft 18 that is only suggested here.
  • the input hub 16 is rigidly attached to a primary element 20 of the torsional vibration damper 4.
  • the primary element 20 is attached
  • the multiple clutch system 2 exhibits a disk carrier 26, which is drivingly connected to the secondary element 24 via a driver device 28,
  • the disk carrier 26 is configured as an external disk carrier for an external clutch 30 and an internal clutch 32, in conjunction with which it is also possible to speak of an external disk pack in the case of the external clutch 30, and an internal disk pack in the case of the internal clutch 32.
  • the external clutch 30 encloses the internal
  • the disk carrier 26 exhibits a tubular external disk-carrying section 34 intended to receive the external disks of the external clutch 30 and a tubular internal disk-carrying section 36 intended to receive the external disks of the internal clutch 32.
  • the two disk-carrying sections 34, 36 are supported by means of a common supporting section 38 in the radial direction 14 towards the inside on a tubular clutch hub 40.
  • an external internal disk carrier 42 which exhibits a disk-carrying section 44 intended to receive the internal disks of the external clutch 30, in conjunction with which the disk- carrying section 44 is connected to an output hub 48 via a supporting 5 section 46, which is capable of being rigidly connected to a first gearbox input shaft 50.
  • an internal disk carrier 52 which exhibits a tubular disk-carrying section 54 intended to receive the interna!
  • disks of the internal clutch 32 in conjunction with which the disk-carrying section 54 is supported by means i o of a supporting section 56 on a further output hub 58, which can be connected in turn to a second gearbox input shaft 60 configured as a hollow shaft, as illustrated in Fig. 1.
  • the supporting section 38 of the disk carrier 26 comprises an externa! part section 62, which extends in the radial direction 12, 14, a
  • tubular part section 64 which extends in the axia! direction 8 starting from the external part section 62, and an internal part section 66, in conjunction with which the latter extends in the radia! direction 14 inwards as far as the clutch hub 40, starting from the end of the tubular part section 64 facing in the axial direction 8.
  • the interna! part section 66 is
  • the multiple clutch system 2 also exhibits an actuating piston 70, which is so arranged as to be capable of being displaced on the clutch hub
  • the actuating piston 70 in turn comprises an external part section 72, which extends in the radial direction 12, 14, and attached
  • the internal part section 76 is arranged offset in the axial direction 8 in relation to the externa! part section 72.
  • the externa! part section 72 exhibits actuating fingers 78 at its external end projecting in the axial direction 8, which fingers extend through windows 80 in the external part section 62 of the supporting section 38 of the disk carrier 26.
  • An actuating piston 82 is also provided for the internal clutch 32.
  • the actuating piston 82 is supported in the radial direction 14 from the outside on the tubular part section 64 of the supporting section 38 of the disk carrier 26.
  • the actuating piston 82 which is also capable of displacement in the axial direction 8, 10, exhibits an externa! part section i o 84, which, irrespective of the displacement position of the actuating piston 82 in the axial direction 8, is located at a distance from the external part section 62 of the supporting section 38 of the disk carrier 26, in conjunction with which the external part section 84 of the actuating piston 82 extends in the radial direction 12.
  • Fig. 2 depicts the detail A in Fig. 1 as an enlarged representation.
  • a pressure chamber 86 is executed on the side of the actuating piston 70 facing in the axial direction 10.
  • the pressure chamber 86 can be
  • a compensation chamber 92 is provided on the other side of the actuating piston 70 or, to put it more accurately, in the axiai direction 8 behind the actuating piston 70.
  • the compensation chamber 92 in this case
  • the compensation chamber 92 is essentially delimited in the axial direction 8 by the internal part section 66 of the supporting section 38 of the disk carrier 26, in the axiai direction 10 by the internal part section 76 of the actuating piston 70 and in the radial direction 12 by the tubular part section 64 of the supporting section 38 of the disk carrier 26.
  • the compensation chamber 92 is delimited towards the inside by the clutch hub 40, and here too one or a plurality of bores 94 5 is/are provided in the clutch hub 40 for the introduction of oil into the compensation chamber 92 in the radial direction 12.
  • An oii guide element 96 is also positioned on the supporting section 38 of the disk carrier 26.
  • the oil guide element 96 is preferably configured as a sheet metal component and is comprised essentially of a bowl-shaped i o annular component.
  • the oil guide element 96 in this case is inserted or pressed into the depression 68 in the supporting section 38 of the disk carrier 26.
  • the oil guide element 96 is comprised essentiaiiy of an interna! part section 98, which is separated by the clutch hub 40 in the radial direction 12 and extends outwards in the radiai direction 12, of a tubular
  • tubular part section 64 of the supporting section 38 are additional projecting abutments 108, which consequently project in the radial direction 12 and provide a support for the oii guide element 96 in the radial direction 12 on the tubular part section 64 of the supporting section 38.
  • a sealing element 1 12 is arranged in addition on the actuating piston 70.
  • the sealing element 112 comprises a carrying component 114 having an L-shaped cross section, 5 which is pushed or pressed in the axial direction 10 onto the actuating piston 70 and/or onto the bulging part in the form of the internal part section 76 and the tubular part section 74.
  • a sealing lip 116 is also provided on the carrying component 114 , which, for example, can be molded onto the carrying component by vulcanization.
  • the sealing tip 116 provides sealing of the resulting annular gap between the actuating piston 70 and the oi! guide element 96.
  • the sealing lip 116 extends in the radial direction 12 outwards in order to adjoin the tubular part section 100 of the oil guide element 96, in
  • a spring device 120 in the form of a disk spring, which is caused to move by the pre- tensioning of the actuating piston 70 in the axial direction 10 into an initial
  • the spring device 120 in this case is supported on the one hand on the actuating piston 70, and on the other hand indirectly on the supporting section 38, or, to put it more accurately, the external part section 62 of the supporting section 38 of the disk carrier 26.
  • the expression indirectly is used here to denote that the spring device
  • the spring device 120 can also be supported directly on the supporting section 38 of the disk carrier 26, in conjunction with which the external collar 102 could exhibit a short length 12 in the radial direction for this purpose. Thanks to the projecting abutments 104 and 108 on the oil guide element 96, the oil guide element 96 in the installed state is separated from the supporting section 38 of the disk carrier 26 to such an extent that an overflow channel 122 is executed between the oil guide element 96 on the 5 one hand and the supporting section 38 of the disk carrier 26 on the other hand.
  • the overflow channel 122 in this case consists of a first part section 124, which is executed between the internal part section 98 of the oil guide element 96 and the internal part section 66 of the supporting section 38 and extends towards the outside in the radial direction 12, starting from a i o radially internal inlet opening 126, and a second part section 128, which in the radial direction 12 is executed between the tubular part section 100 of the oil guide element 96 and the tubular part section 64 of the supporting section 38 and extends in the axial direction 10.
  • the seal 1 10 on the external collar 102 of the oil guide element 96 in this case produces sealing
  • the second part section 128 of the overflow channel 122 leads to an externally situated outlet opening 130 of the overflow channel 122, in conjunction with which the outlet opening 130 is formed by at least one groove 132 in the tubular part section 64 of the supporting section 38 of the disk carrier 26.
  • the overflow channel 122 discharges via its inlet opening 126 into the compensation chamber 92 in such a way that the effective hydraulic fluid column inside the compensation chamber 92 is shortened in the radial direction 12 in such a way that the axial force resulting from the hydraulic fluid column acting on the actuating piston 70 in the axial direction 10
  • This discharged oil now flows via the first part section 124 of the overflow channel 122 in the radial direction 12 outwards, in order to make its way in the axial direction 10 through the second part section 128 of the overflow - 13 - channel 122 as far as the outlet opening 130 in the form of the groove 132.
  • the discharged oii now makes its way through the outlet opening 130 from one side of the supporting section 38 to the other side of the supporting section 38, where it passes into a further channel 134.
  • the further channel 134 extends in a linear fashion in the radial direction 12, in conjunction with which the further channel 134 is delimited in the axial direction 10 by the externa! part section 62 of the supporting section 38 of the disk carrier 26, and in the axiai direction 8 by the external part section 84 of the second actuating piston 82.
  • the externa! part section 84 of the second actuating piston 82 extends outwards in the radial direction 12 to such an extent that the discharged oil, which exits from the further channel 134 in the radial direction 12, can be used if necessary for the cooling or/and lubrication of a radially external part of the internal clutch 32.
  • the further channel 134 carries the discharged oii in the radial direction 12 outwards to the internal disk-carrying section 36 of the disk carrier 26. in order generally to prevent the discharged oil from being
  • oil passageways 136 are provided in the internal disk-carrying section 36, via which the discharged oii can pass in the radial direction 12 in order to find its way to the disk-carrying section 44 of the external interna! disk carrier 42.
  • Oil passageways 138 are also provided in the disk-carrying section 44 of the externa! internal disk carrier
  • the oil passageways 136 are at least partially in alignment in the radia! direction 12 outwards with the oii passageways 138 in the disk- carrying section 44 of the external interna! disk carrier 42.
  • the embodiment of the multiple clutch system 2 described here offers further advantages in addition to the advantageous cooling of the 5 externa! clutch 30. If, for example, the actuating piston 70 were to be displaced in the axial direction 8 as far as an end position, the actuating piston 70 or its internal part section 76, where appropriate with the interposition of the carrying component 114 of the sealing element 112, will come up against the abutment 106 of the internal part section 98 of the oil i o guide element 96 projecting in the axial direction 10.
  • the height of the projecting abutment 106 in the axial direction 10 is selected in such a way that the sealing iip 116 of the sealing element 112 bears against tubular part section 100 of the oil guide element 96, and, to be precise, continuing in the radial direction 12, although the sealing lip remains
  • the projecting abutments 106 should also project to a sufficient extent in the axial direction 10 to ensure that the sealing lip 116 in the end position does not extend as far as the height of the projecting
  • sealing element 1 12 and the oil guide element 96 can thus be combined initially into a common module, in conjunction with which this coherent module is only incorporated into the multiple clutch system 2 subsequently.
  • the following procedure is adopted in this case: the sealing element 112 is first pushed or pressed onto the actuating piston 70 in the axial direction 10.
  • the spring device 120 can already be brought into a position on the module, in which the spring device 120 is supported on the side of the 5 actuating piston 70 facing in the axial direction 8.
  • the oil guide element 96 is then pushed onto the sealing element 112 in the axial direction 10 in such a way that the sealing element 112 and/or the tubular part section 74 of the actuating piston 70 reaches the tubular part section 100 of the oil guide element 96.
  • the oil guide element 96 must be rotated relative to the sealing element 1 12 about the axis of rotation 6, in order to prevent the sealing lip 1 16 of the sealing element 1 12 that is inclined in the axiai direction 8 from being folded down or folded down in the axial direction 10, which would inevitably lead to the loss of the sealing effect of the sealing lip5 116.
  • the particular advantage of the modular configuration is evident here.
  • the actuating fingers 78 of the actuating piston 70 projecting through the 0 windows 80 in the supporting section 38 would lead to a restricted relative ability of the sealing element 1 12 to rotate in relation to the oil guide element 96. It would then not be possible to ensure that the sealing lip 116 at the time of assembly retains its sealing effect for the compensation chamber 92. 5 As already indicated, the module consisting of the actuating piston
  • assembly openings 140 are provided in the external part section 72 of the actuating piston 70,0 and these are arranged in the axial direction 8 at least partially in alignment with the external collar 102 of the oil guide element 96.
  • a die 142 of an assembly too! in the form of a press tool can thus be passed in the axial direction 8 through the assembly openings 140, in order to press in the axial direction 8 against the external5 collar 102 and to cause the oil guide element 96 to be pressed into the depression 68 inside the supporting section 38 of the disk carrier 26.
  • the process of pressing in the oil guide element 96 could also be effected by the actuating piston 70 acting on the oil guide element 96 in the axial direction 8 under compression of the spring device 120, although under certain circumstances this can lead to excessively strong loading of the spring device 120, of the interjacent sealing element 112 or of the internal part section 98 of the oil guide element 96, so that the aforementioned procedure is preferable.

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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

La présente invention porte sur un système à multiple embrayage (2) ayant un embrayage externe (30) ainsi qu'un embrayage interne (32), qui sont disposés de façon emboîtée dans la direction radiale (12, 14), et un piston d'actionnement (70) pour l'actionnement de l'embrayage externe (30). Une chambre de pression (86) est disposée sur un côté du piston d'actionnement (70), laquelle chambre de pression (86) peut être soumise à une pression d'une manière telle que le piston d'actionnement (70) peut être déplacé dans la direction axiale (8), tandis qu'une chambre de compensation (92) est disposée de l'autre côté du piston d'actionnement (70). Une force axiale agissant sur le piston d'actionnement (70) est générée par rotation du système à multiple embrayage (2) au moyen d'une première colonne de fluide hydraulique orientée radialement à l'intérieur de la chambre de pression (86), tandis qu'une force axiale opposée agissant sur le piston d'actionnement (70) est générée au moyen d'une seconde colonne de fluide hydraulique orientée radialement dans la chambre de compensation (92). Un canal de débordement (122) pour le retrait partiel de l'huile de la chambre de compensation (92) décharge la chambre de compensation (92) d'une manière telle que la longueur de la seconde colonne de fluide hydraulique dans la direction radiale (12, 14) est raccourcie d'une manière telle que les forces axiales mutuellement opposées agissant sur le piston d'actionnement (70) sont équilibrées. Selon l'invention, le canal de débordement (122) est conçu d'une manière telle que l'huile déchargée par l'intermédiaire du canal de débordement (122) est capable d'être distribuée particulièrement rapidement et efficacement à l'embrayage externe (30).
PCT/US2009/034064 2008-02-18 2009-02-13 Système à multiple embrayage avec compensation de fluide hydraulique WO2009105388A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102008009702 2008-02-18
DE102008009702.0 2008-02-18
DE102008036852.0 2008-08-07
DE102008036852.0A DE102008036852B4 (de) 2008-02-18 2008-08-07 Mehrfach-Kupplungseinrichtung mit Fliehölausgleich

Publications (2)

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WO2009105388A2 true WO2009105388A2 (fr) 2009-08-27
WO2009105388A3 WO2009105388A3 (fr) 2009-11-19

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DE (1) DE102008036852B4 (fr)
WO (1) WO2009105388A2 (fr)

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CN105317877A (zh) * 2014-08-01 2016-02-10 Valeo离合器公司 用于机动车辆的离合器装置
CN112997019A (zh) * 2018-11-12 2021-06-18 戴姆勒股份公司 具有第一离合器和第二离合器的离合设备

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CN104315010B (zh) * 2014-09-29 2016-08-31 沈琴仙 双板式离合器机构和包括双板式离合器机构的机械变速器
DE102015220198A1 (de) 2015-10-16 2017-04-20 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung
DE102016220793A1 (de) 2015-11-13 2017-05-18 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung
DE102016221922B4 (de) 2015-11-19 2024-02-29 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung
DE102016223019A1 (de) * 2016-11-22 2018-05-24 Zf Friedrichshafen Ag Betätigungsvorrichtung zum Betätigen eines Schaltelements eines Getriebes
CN110513467A (zh) * 2019-09-06 2019-11-29 深圳臻宇新能源动力科技有限公司 双离合器变速器及具有其的车辆

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US7114605B2 (en) * 2000-12-07 2006-10-03 Zf Sachs Ag Double or multiple disk coupling device and disk arrangement therefor
US20060289269A1 (en) * 2003-07-23 2006-12-28 Zf Friedrichshafen Ag Clutch arrangement in an automatic transmission having an installation space-saving coolant supply
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Publication number Priority date Publication date Assignee Title
CN105317877A (zh) * 2014-08-01 2016-02-10 Valeo离合器公司 用于机动车辆的离合器装置
KR20160016660A (ko) * 2014-08-01 2016-02-15 발레오 앙브라이아쥐 자동차용 클러치 장치
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CN112997019A (zh) * 2018-11-12 2021-06-18 戴姆勒股份公司 具有第一离合器和第二离合器的离合设备
CN112997019B (zh) * 2018-11-12 2023-05-26 梅赛德斯-奔驰集团股份公司 具有第一离合器和第二离合器的离合设备

Also Published As

Publication number Publication date
WO2009105388A3 (fr) 2009-11-19
DE102008036852A1 (de) 2009-08-20
DE102008036852B4 (de) 2018-11-29

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