WO2008064641A1 - Système de transmission de force - Google Patents

Système de transmission de force Download PDF

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Publication number
WO2008064641A1
WO2008064641A1 PCT/DE2007/002046 DE2007002046W WO2008064641A1 WO 2008064641 A1 WO2008064641 A1 WO 2008064641A1 DE 2007002046 W DE2007002046 W DE 2007002046W WO 2008064641 A1 WO2008064641 A1 WO 2008064641A1
Authority
WO
WIPO (PCT)
Prior art keywords
power transmission
transmission device
coupling
piston
output
Prior art date
Application number
PCT/DE2007/002046
Other languages
German (de)
English (en)
Inventor
Eugen Kombowski
Bruno MÜLLER
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs Kg
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 filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to DE112007002624T priority Critical patent/DE112007002624A5/de
Publication of WO2008064641A1 publication Critical patent/WO2008064641A1/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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H2045/002—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a clutch between prime mover and fluid gearing
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H2045/005—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a clutch between fluid gearing and the mechanical gearing unit
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0252—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a damper arranged on input side of the lock-up clutch
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0257—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a pump adapted for use as a secondary mass of the damping system
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch

Definitions

  • the invention relates to a power transmission device, in detail with the features of the preamble of claim 1.
  • Power transmission devices disposed between a prime mover and a transmission assembly are known in a variety of prior art designs. These usually include an input and at least one output, wherein the input at least indirectly, that is directly or via further transmission elements with the drive motor is coupled and at least one output connected to a power transmission device downstream transmission unit, usually a change gear is and is formed by a transmission input shaft.
  • a hydrodynamic component preferably in the form of a hydrodynamic speed / torque converter, is arranged. This comprises at least one impeller and a turbine wheel.
  • a device is provided, which is also called bridging clutch. This comprises a first coupling part and a second coupling part, which are at least indirectly engageable with each other in operative connection.
  • the lock-up clutch serves for the coupling between the input or the connection between the input and the impeller and the turbine wheel.
  • the actuation of the switchable coupling via an actuating device which comprises in the simplest case, an adjusting device in the form of a pressurizable piston element.
  • an actuating device which comprises in the simplest case, an adjusting device in the form of a pressurizable piston element.
  • the hydrodynamic speed / torque converter or the entire power transmission device is designed as a two-channel or three-channel unit.
  • the lock-up clutch is activated and the power is transmitted between the input and the output of the power transmission device mechanically, bypassing the hydrodynamic power branch.
  • the lockup clutch can disconnect the prime mover from the output in the mechanical branch.
  • the hydrodynamic component remains filled, which is the case with the hydrodynamic speed / torque converter even in the bridged state, a torque is introduced into the hydrodynamic component during coasting, which in turn leads to losses when the engine is idling.
  • torque shocks are introduced from the side of the output in the hydrodynamic component.
  • a coupling device which serves for decoupling of the pump impeller and thus for decoupling the drive machine of a power transmission device downstream transmission unit.
  • the impeller clutch is required only for separation in this operating range. This is often arranged in an area that leads to increase the required installation space in the radial or axial direction.
  • corresponding pressure chambers are to be provided, which at least one connection is to be assigned to the supply of pressure medium, for which corresponding further channels are to be provided.
  • the invention is therefore based on the object, a power transmission device of the type mentioned in such a way that it is designed as a multi-function converter, that is, at least one more switchable clutch device in addition to the lock-up clutch and further the already known for power transmission devices three-channel principle is maintained, that is more than three connections should be avoided if possible.
  • a power transmission device for arrangement in a drive train between a prime mover and a transmission comprising an input and an output formed by a shaft and two switchable clutch devices arranged in an inner space enclosed by a housing and forming a first pressure chamber - a first te and a second coupling device - each having at least one acted upon by a pressure medium piston element is inventively characterized in that both piston elements to form a second pressure-tight and liquid-tight against the other interior pressure chamber at the output or a non-rotatably coupled thereto element are guided and the individual pressure chambers via in the output or with this rotatably coupled element in the circumferential direction offset from one another and intersecting channels can be acted upon with pressure medium.
  • the solution according to the invention allows a space-saving arrangement of the individual actuating devices and an independent supply of individual pressure chambers with operating or pressure medium, usually oil.
  • pressure chamber generally stands for a space that can be acted upon by any pressure.
  • the second switchable coupling device on the first piston element i. arranged the piston member of the first coupling means and the second piston member on the first piston member guided to form the pressure medium acted upon pressure chamber in the axial direction displaceable.
  • the first piston element is characterized by a high functional concentration.
  • a plurality of the individual channels - first channels and / or second channels are provided for uniform supply, which are arranged in the circumferential direction alternately to each other.
  • the arrangement of the channels takes place in an advantageous manner in the circumferential direction symmetrically.
  • the supply of the second pressure chamber with pressure medium takes place through the first pressure chamber.
  • the connection channels extend in the axial direction through the connection element or guide element for the individual piston elements, so that the partial pressure chambers are coupled to one another on both sides of the piston arrangement.
  • a plurality of such axially extending channels are provided in the circumferential direction. These are arranged spaced from each other. Between two adjacent channels arranged at least one connecting channel for coupling a central supply line with the second pressure chamber in the radial direction is aligned. This means that the individual pressure chambers are closed in the circumferential direction.
  • the solution according to the invention thus makes it possible on the one hand to provide a high functional concentration with respect to the arrangement and mounting of the individual piston elements and the individual coupling devices, while maintaining the three-channel principle, a supply of the two piston elements of the two switchable coupling devices can be done separately by the both piston elements are displaceable relative to each other in the axial direction and by adjusting the pressures or pressure difference of the individual surrounding the piston assembly pressure chambers.
  • connection element for supporting or guiding the piston arrangement or the individual piston elements can either be a transmission input shaft of a downstream transmission unit which simultaneously forms the output of the power transmission device, a rotation-proof one Transmission input shaft coupling element, for example in the form of a hub element.
  • the hub member itself rotatably with the transmission input shaft directly or at least indirectly, that is connected via other transmission elements, such as a device for damping vibrations.
  • the hub element may be the hub which can be coupled to a turbine wheel or, for example, a hub element of a device for damping vibrations, in particular of the hub element connected to the secondary part.
  • the design with support on a separate intermediate hub which is either rotatably coupled to the transmission input shaft or at least indirectly via further transmission elements with this, in which case at least one pressure and liquid-tight guide against the first pressure chamber in the connection area for the second Provide pressure chamber is the advantage that the transmission input shaft can still be designed very simple and compact and is suitable for a variety of different applications and the appropriate hub design is set only for the specific configuration in this embodiment.
  • the connecting channel for the individual pressure chamber areas of the first pressure chamber is preferably aligned parallel to the axis of rotation and thus extends quasi in the horizontal direction.
  • connection channels for the sub-chambers of the first pressure chamber and for the second pressure chamber are each arranged alternately in the circumferential direction with uniform distances from each other.
  • the guide can be made on a partial area forming an inner circumference or on an outer area forming an outer circumference. However, this depends on the installation situation and the function of the individual piston elements with respect to the coupling devices associated therewith.
  • the piston assembly of the two piston elements can be designed such that the individual piston elements are characterized in terms of the closing direction of the individual coupling devices by the same actuating direction or different actuation directions.
  • the former case has the advantage that the actuation of the one coupling device upon actuation of the second pressure chamber simultaneously causes an opening of the other coupling device or a pressure counteracting the closing pressure is generated on the other piston element.
  • This embodiment is quasi characterized by a kind of positive coupling, which is determined by the pressure in the second pressure chamber and the ambient pressure, ie in the interior. If the direction of actuation of one of the two piston elements is opposite to one another, at least on one piston element, a further piston surface defining the pressure chamber is to be provided, which allows the piston element to be acted upon via the first pressure chamber.
  • the power transmission devices are generally hydrodynamic-mechanical power transmission devices, that is, these are characterized at least by the possibility of power transmission via a first power branch and a second power branch, wherein the first power branch through the hydrodynamic power transmission between the input and at least one output Power transmission device is characterized, while the second power branch includes the purely mechanical power transmission between the input and the output.
  • the hydrodynamic power transmission is realized by the arrangement of a hydrodynamic component. This comprises at least one pump wheel which can be coupled at least indirectly to the input and a turbine wheel which can be coupled at least indirectly to the output, this being either free from a stator in the form of a hydrodynamic coupling or with at least one stator as a hydrodynamic speed / torque converter is. The latter offers the advantage in the starting range of stepless speed and simultaneous torque conversion between input and output.
  • the first clutch device may be a so-called pump or primary wheel clutch. This allows an optional coupling or decoupling of the impeller from the input. Furthermore, it is conceivable to design the first coupling device as a turbine coupling. In this case, the turbine wheel is selectively decoupled from the output, in particular the transmission input shaft, or can be coupled thereto.
  • the former design has the advantage that in power transmission between input and output, the hydrodynamic component is completely decoupled in the bridged state from the input, that is no entrainment of the impeller takes place.
  • the second embodiment with a possible turbine wheel clutch offers the advantage of a complete decoupling of the hydrodynamic component from the transmission output shaft in overrun mode, so that the idling losses can be considerably reduced here, in particular during idling.
  • a separate co-rotating housing is required, whereas in designs with turbine wheel coupling this can be dispensed with and the housing is formed by an element coupled to a rotationally fixed pump shell. Due to the formation of a pressure chamber by combining the two piston elements of the individual coupling devices to form a piston arrangement, the individual coupling devices can be arranged in the smallest possible space. Preferably, the arrangement takes place in the axial direction next to each other with minimal offset.
  • the individual piston surfaces are interpreted.
  • the piston elements themselves are disc-shaped elements which, viewed in the axial direction in cross-section, are characterized by a corresponding shaping in order to ensure the possible contact surfaces or contact surfaces.
  • the individual coupling devices with different diameters, in particular outer and inner diameters, are formed, so that the simplest possible configuration of the first piston element with connection possibility for the second coupling device is provided.
  • the coupling possibilities between the first coupling part of the second coupling device and the piston element there are a plurality of possibilities.
  • non-positive or positive connections are selected, which ensure a rotationally fixed connection in the circumferential direction, but viewed in the axial direction in cross-section, ensure a displacement.
  • the power transmission device is suitable for use in drive trains, in particular for coupling with a prime mover and a transmission.
  • This is characterized by three pressure chambers, a first pressure chamber, which is formed by the inner circumference of the housing and the outer circumference of the hydrodynamic component, a second pressure chamber, which is formed by the piston assembly and a third pressure chamber, of the hydrodynamic component, in particular the working space, is formed.
  • Each of these pressure chambers is associated with a corresponding port for coupling to a Radioffenerss- or leadership system.
  • connection is to be understood in terms of its function and not in terms of a concrete structural design. It is therefore understood that a plurality of corresponding terminals can be provided viewed in the circumferential direction.
  • FIG. 1 illustrates, on the basis of an axial section, a particularly advantageous embodiment of a power transmission device, in particular a multi-function transducer unit according to a first embodiment
  • Figure 2 illustrates on the basis of a section in a view from the right, the resource guide in the first and second channels;
  • FIG. 3 illustrates another possible second embodiment of a power transmission device designed according to the invention with a clutch device designed as a turbine wheel clutch.
  • the power transmission device 1 shows in an axial section a particularly advantageous embodiment of an inventively designed power transmission device 1.
  • This is arranged in a drive train between a prime mover, not shown here and a transmission not shown here in detail and serves the power, in particular torque transmission.
  • the power transmission device 1 at least one input E and an output A.
  • the input E is at least indirectly coupled to the drive machine, not shown here, while the output A with an output, usually one of the power transmission device 1 downstream transmission is connected and is formed by a shaft, in particular transmission input shaft 22.
  • a first switchable coupling device 2 is provided between the input E and the output A.
  • This has an adjusting device 3, comprising at least a first pressurizable piston element with pressure element 4.
  • a further second switchable coupling device 5 is provided.
  • Each of the switchable coupling devices - first switchable coupling device 2 and second switchable coupling device 5 - comprise at least one first coupling part 2.1 or 5.1 and a second coupling part 2.2 or 5.2, at least indirectly can be brought into operative connection with each other.
  • the active compound is generated via adjusting devices 3 and 6 respectively.
  • Both coupling devices 2 and 5 are arranged in a, an interior 10 enclosing housing 56.
  • the interior 10 acts as a pressure medium acted upon first pressure chamber 55.
  • both piston elements 4 and 7 were supported in a piston assembly 9 to form a further second pressure medium acted upon chamber 8, which is pressure and liquid-tight against the first pressure chamber 10, on a common connection element at least indirectly at the output A from.
  • the second coupling device 5 is arranged on the adjusting device 3 of the first switchable coupling device 2, in particular one of the coupling parts, here 5.1 mounted on the pressurizable with pressure medium first piston member 4. Furthermore, the second piston element 7 of the second switchable coupling device 5 on the first piston element 4 can be displaced in the axial direction to form the chamber 8 which can be subjected to pressure medium. leads.
  • the two piston elements 7 and 4 thereby form a piston arrangement 9, which is arranged in the interior 10 of the force transmission device 11 functioning as the first pressure chamber 55, wherein the first piston element 4 can be subjected to pressure medium via the interior 10.
  • connection is to be understood in the functional sense and not limited to a specific structural design. Connection means only a connection to the respective interior 10 or to the chamber 8 toward the purpose of pressurization, in particular supply o- the removal and / or application of pressures.
  • the chamber 8 is thereby limited as already stated by the two piston elements 4 and 7, wherein the second piston member 7 pressure and liquid-tight on the first piston member 4 is performed.
  • the second piston element 7 at the output A or on a non-rotatably coupled to the output A element also pressure and liquid-tight in the axial direction, for example, via a sealing device 13.1 in the region of the radial outer periphery 14 of the second piston element Directed displaced. This takes place here, for example, via a further sealing device 13.2, which is arranged in the radial direction in the region of the inner circumference or a partial region of the piston element 7 which forms an inner circumference and which is designated here by 15.
  • the chamber 8 is thus virtually in the interior 10 and is enclosed by the pressure chamber 55 formed.
  • intersecting channels 16 and 17 are provided on the radially inwardly located connection elements for the pressure chambers for acting on the first and second piston elements 4, 7, viewed in the circumferential direction of the connection element are arranged offset to one another, that is, are fluidically decoupled from each other.
  • These channels 16 and 17 are guided by the piston elements 4 and 7 supporting elements in the radial or in the axial direction, in which it is the output A forming the transmission input shaft 22 or a non-rotatably coupled with this hub member 28.
  • the lockup clutch 19 functions with regard to the bypassing of a hydrodynamic power branch, which is formed by a hydrodynamic component 20, which is preferably in the form of a hydrodynamic speed / torque converter 21 and at least a first as impeller P during power transmission from the input E to the output A acting paddle wheel and a second, at power transmission between a gear E and output A acting as a turbine wheel and at least indirectly connected to the output A paddle wheel comprises.
  • a hydrodynamic speed / torque converter 21 at least one stator L is also provided.
  • the hydrodynamic speed / torque converter 21 serves for the simultaneous conversion of speed and torque during power transmission.
  • hydrodynamic components 20 in the form of a hydrodynamic coupling not shown here this is free of a stator and acts only as a speed converter at the same torque.
  • the impeller clutch 18 is arranged between the input E and the impeller P and is used for the selective coupling or decoupling of the impeller P of this.
  • the second switchable coupling device 5 acting as a bridging clutch 19 serves to bypass the power transmission via the hydrodynamic component 20 and thus the direct coupling between the input E and the output A.
  • the output A is in the case illustrated by a shaft which can be coupled to the downstream transmission Also referred to as transmission input shaft 22 is formed. All components, in particular hydrodynamic component 20, first switchable coupling device 2 and second coupling device 5 are arranged coaxially with each other and also coaxial to a rotation axis R of the power transmission device 1. Further, in the case shown, a device 23 for damping vibrations is provided.
  • This is designed as a torsional or torsional vibration damper and comprises at least one damper stage, which of a primary part 24 and a secondary part 25 which are rotatable in the circumferential direction limited relative to each other, is formed, wherein the primary part 24 and secondary part 25 via means 26 for spring and / or damping coupling connected to each other.
  • the means 26 for spring and / or damping coupling can be designed in various ways. In purely mechanical damper versions, the coupling is done only via spring units 27, which in addition to the torque transmission and the function of damping, that is absorption of torque surges take over. In other embodiments, such as combined hydraulic mechanical damper designs, in addition to spring units, for example, with damping medium, in particular fat-filled damping chambers are provided.
  • the concrete selection of the respective device for damping vibrations is at the discretion of the competent expert and also depends on the requirements of the application in detail. This also applies to the specific structural design with respect to the primary part 24 and secondary part 25. It is crucial that the secondary part 25 as the output part of acting as a flexible coupling device 23 for damping vibrations rotatably connected to the output A and The primary part 24 is at least indirectly rotatably coupled to the input E, the coupling depending on the type of power transmission - hydrodynamic or purely mechanical - on the hydrodynamic component 20, in particular the turbine wheel T, with this or a non-rotatably coupled thereto element, in particular connection element, which in turn is rotatably connected to the primary part 24, takes place.
  • the coupling of the primary part 24 takes place with the second coupling part 5.2 of the lock-up clutch 19 and thus the output of the second switchable coupling device 5.
  • the power transmission takes place by the coupling of the turbine wheel T with the primary part 24 via a hub member 28.
  • This Hub member 28 serves to support the first piston member 4 and further at least indirectly the leadership and support of the second piston member 7.
  • the second piston member 7 via the sealing device 13.1 on the first piston member 4 pressure and liquid tight in the axial direction slidably guided and
  • the first coupling device 2, in particular the first piston element 4 likewise supports itself on the hub element 28 via the second sealing device 13.
  • the first piston element 4 is designed such that it forms a plate carrier 31 for the first coupling part 5.1 of the second switchable coupling device 5 in the embodiment of the switchable coupling devices 2 and 5 as frictional coupling devices. Furthermore, this forms a plate carrier 32 for the first coupling part 2.1 of the first coupling device 2, which is designed as a pump gear 18.
  • the second coupling part 2.2 of the first coupling device 2 is at least indirectly rotatably connected to the impeller P.
  • the impeller shell 33 acts as a plate carrier 34 for the lamellae of the second coupling part 2.2 of the first coupling device 2.
  • the first piston element 4 of the first switchable clutch device 2 is thus formed in cross section with a projection 35 formed in the axial direction for the realization of said support functions for the individual clutch parts, here 2.1 and 5.1 of the individual switchable clutch devices 2 and 5.
  • this projection 35 which is viewed in the radial direction in each case as a plate carrier in the formation of the first and second coupling devices 2.5 is formed as a switchable frictional coupling devices 2.5 in the form of multi-plate clutches, the rotationally fixed coupling with the input E, in particular a rotatable housing part 55th This takes place in the illustrated case via a further device 36 for damping vibrations.
  • This also comprises a primary part 37 and a secondary part 38, wherein the primary part 37 at least indirectly rotationally fixed to the input E, in particular is connected to the housing part 55, while the secondary part 38 is connected at least indirectly non-rotatably connected to the piston member 5.
  • the primary part 37 and the secondary part 38 are coupled to each other at least indirectly via means 39 for spring and / or damping coupling and limited to each other in the circumferential direction rotatable limited.
  • the means 39 for spring and / or damping coupling comprise either only spring units which serve for torque transmission and at the same time for damping or else additional, differently designed damping elements, for example friction damping pairings or chambers which can be filled with damping medium etc.
  • non-rotatable connections between the individual elements depending on the function and requirements solvable or non-detachable, for example by welding, done. Furthermore, a form or adhesion or a combined mounting is conceivable. In the case of desired axial displaceability, non-rotatable connections preferably take place by means of splined shaft connections.
  • a Verwarwinkelbegrenzung between the primary part 24 and the secondary part 25 are realized via the hub member 29, for example, arranged on this in the circumferential direction and extending recesses or Projections which engage in the projections or recesses on the primary part 24, wherein the tolerances are dimensioned so that a certain predefined angle of rotation is permitted.
  • the function of the power transmission device is designed as followsjm essentially two different modes of operation, the power transmission via the hydrodynamic branch in the form of the hydrodynamic component 20 and the purely mechanical power transmission, bypassing the hydrodynamic component 20, in particular the hydrodynamic speed / torque converter.
  • the adjusting device 3, in particular the first piston element 7, is actuated and brings the two coupling parts 2.1 and 2.2 of the first switchable coupling with each other in operative connection, so that here a coupling with the input E of the power transmission device 1 is produced, said coupling indirectly takes place via the device 36 for damping vibrations.
  • This, in particular their secondary part 38, is rotatably coupled to the piston member 4, in particular the projection 35.
  • the coupling can be designed in many forms.
  • the secondary part 38 has in the region of its inner circumference 40 toothed elements 41 which are in engagement with complementary toothed elements 42 on the piston element 4 and the projection 35, wherein the arrangement on a, an outer circumference 43 forming portion of the projection 35 and des Piston element 4 takes place.
  • a contact pressure force is generated via the piston element 4, which brings the individual coupling parts 2.1 and 2.2, in particular the lamellae having them, in operative connection by pressing.
  • the piston assembly 9 which is formed by the two individual piston elements 4 and 7, divided in connection with their coupling to the output A, here via the hub member 28, while the interior 10 in two sub-chambers 10.1 and 10.2, whose size depending on the position of both piston elements 4 and 7 is mutually variable. The connection of these takes place via the channels 16.
  • the power is transmitted to the transmission input shaft 22 via the coupling with the turbine hub 28, the primary part 24 of the device 23 for damping vibrations on the secondary part 25 and the hub 29 coupled thereto.
  • the second shiftable clutch 5 in the form of the lock-up clutch 19 is not actuated.
  • the lock-up clutch 19 is actuated.
  • the second piston element 7 of the piston assembly 9 is acted upon, in particular the chamber 8 formed by the two piston elements 4 and 7, which is coupled to the connection 12.
  • the supply channel 50 is guided through the transmission input shaft 22 and extends coaxially to the axis of rotation R.
  • the corresponding connecting channel extends to the chamber 8 in the form of a extending in the radial direction of the sub-channel 49, which is arranged in the hub member 28 channel 16 opens into the pressure chamber 8.
  • the first port 11, which serves to couple with the interior 10 is preferably between the transmission input shaft 22, in particular the outer periphery 44 of the transmission input shaft 22, and a support shaft 45, which preferably corresponds to the support shaft for the stator L, is provided.
  • the subdivision of the inner space 10 in the two sub-chambers 10.1 and 10.2 is over the connecting channel 16, which extends substantially parallel to the axis of rotation R through the hub member 28, repealed.
  • Other resource guides are conceivable.
  • At least one individual connecting channel 16 is formed in the axial direction, which can also compensate for differences in height in the radial direction.
  • a channel is selected, which preferably runs parallel to the axis of rotation R.
  • a stop 46 is provided on the first piston element 4, which simultaneously causes pressurization in the chamber 8, the first piston member 4 is claimed to train and in its position relative to the second piston member 7 at a further stop for the piston element 4 is fixed, with an appropriate design of the piston surfaces, the entire piston assembly 9 is free of axial forces on other connection elements.
  • the entire arrangement can furthermore be designed in such a way that the first clutch device 2 is always actuated in the unloaded state, in particular in the unloaded state of the pressure chamber 8, while upon activation of the lock-up clutch 19 due to the pressure setting on the piston element 7 Wheel clutch 18 is solved.
  • the stop 46 is preferably non-rotatably arranged on the piston element 4, in particular the projection 35.
  • the hydrodynamic component 20 is assigned a further third connection 47 for coupling to the working space 57.
  • the hydrodynamic component 20 can then be flowed through centrifugally or centripetally, that is to say either from the region of the inner diameter to the outer diameter or vice versa. It is crucial that in the resource guide outside of the hydrodynamic component 20 in the power transmission device 1, the exchange between the two sub-chambers 10.1 and 10.2 on the preferably horizontally running transverse bores, in particular the channels 16, while the application of the pressure chamber 8 via the substantially radial Direction aligned channel 17 takes place.
  • connection channels 16 and 17 there are no restrictions. In each case, a single such channel may be provided 16 or 17 or a plurality of channels, the latter option is preferably applied.
  • the individual connection channels 16.1 to 16.n are preferably arranged alternately in the circumferential direction with the connection channels 17.1 and 17.n.
  • the connection between the two sub-chambers 10.1 and 10.2 can be realized differently. In the simplest case, this is done via a mounting position in the horizontal direction, that is aligned parallel to the axis of rotation R passage opening.
  • the cross-sectional profile may preferably over the entire axial extent be identical. Changes are also conceivable for influencing the flow conditions.
  • FIG. 2 shows, in a schematized simplified illustration, a possible channel guidance for the connection channels 16.1 to 16.n and 17.1 to 17.n. in a view from the right in the form of a section from a sectional view through a hub 28.
  • a plurality of such channels can be provided, which are arranged alternately in the circumferential direction, and each offset from one another, wherein the alignment in the axial direction is free from the parallel position to each other, so that they substantially intersect or inclined in projecting in a plane extend to each other and extend through the hub member 28.
  • FIG. 1 describes the specific embodiment of the subdivision of the inner space 10 by means of the piston assembly 9 and the coupling with the transmission input shaft 22 through the hub member 28 in the two Operakammem 10.1 and 10.2. It would also be conceivable, depending on the design, a corresponding projection in the radial direction on the transmission input shaft 22 itself, in which case additional sealing measures can be dispensed with, but the corresponding connection channels 16, 17 would have to be pre-drilled.
  • the actuation of the individual coupling devices 2, 5 is preferably carried out independently of each other by the possible displaceability of the individual piston elements 4, 7 in axia- ler direction relative to each other by the pressure differences between the individual pressure chambers 55, 8 and 57.
  • the design is designed such that the piston elements 4 and 7 have the same direction of actuation for closing the coupling devices 2, 5.
  • the first clutch device 2 is formed by the turbine clutch 53. This has a first coupling part 53.1, which is non-rotatably connected to the turbine wheel T and a second coupling part 53.2, which is at least indirectly non-rotatably connected to the transmission input shaft 22.
  • the second clutch device 5 is also formed here by the lock-up clutch 19.
  • FIG. 1 illustrate only possible embodiments.
  • the embodiment according to FIG. 1 is characterized in that the actuation or closing direction and opening directions of the two switchable coupling devices are identical in each case; in FIG. 3, these are opposite to one another.
  • the illustrated embodiments are further designed such that here is a guide of the two piston elements 4, 7 to each other, wherein the first piston member 4 may be performed on the second 7 or vice versa.
  • the guide can take place in the region of an inner circumference forming partial area or of an outer circumference forming partial area.
  • the actual design depends on the individual space conditions and the execution of the power transmission device 1. It is also essential, which type are the switchable clutches, in particular whether they are designed as a lock-up clutch or as corresponding turbine or impeller clutches. LIST OF REFERENCES

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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)
  • Control Of Fluid Gearings (AREA)
  • Mechanical Operated Clutches (AREA)
  • Arrangement Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

L'invention concerne un système de transmission de force (1) destiné à être placé dans un ensemble transmission entre un moteur d'entraînement et une boîte de vitesses. Ce système de transmission de force comprend une entrée (E) et une sortie (A) formée par un arbre, ainsi qu'un premier et un second dispositif d'accouplement (2, 5) embrayables disposés dans un espace intérieur (10) qui est entouré par un carter (56) et forme une première chambre de pression (55), chaque dispositif d'accouplement comprenant au moins un élément piston (4, 7) pouvant être soumis à l'action d'un fluide sous pression. L'invention se caractérise en ce que les deux éléments pistons sont guidés sur la sortie ou sur un élément (28) couplé à celle-ci de façon solidaire en rotation, une seconde chambre de pression (8) étanche à la pression et au liquide vis-à-vis de l'espace intérieur étant ainsi formée, et en ce que les chambres de pression individuelles peuvent être alimentées en fluide sous pression par l'intermédiaire de canaux (16, 17) qui se croisent, ces canaux étant situés dans la sortie ou dans l'élément couplé solidaire en rotation, avec un décalage l'un par rapport à l'autre dans le sens périphérique.
PCT/DE2007/002046 2006-11-29 2007-11-13 Système de transmission de force WO2008064641A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112007002624T DE112007002624A5 (de) 2006-11-29 2007-11-13 Kraftübertragungsvorrichtung

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DE102006056299.2 2006-11-29
DE102006056299 2006-11-29
US87410406P 2006-12-11 2006-12-11
US60/874,104 2006-12-11
DE102006061553.0 2006-12-27
DE102006061541 2006-12-27
DE102006061541.7 2006-12-27
DE102006061552.2 2006-12-27
DE102006061552 2006-12-27
DE102006061553 2006-12-27
US93423507P 2007-06-12 2007-06-12
US60/934,235 2007-06-12
US96277207P 2007-07-31 2007-07-31
US60/962,772 2007-07-31
US96485507P 2007-08-15 2007-08-15
US60/964,855 2007-08-15

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WO2008064641A1 true WO2008064641A1 (fr) 2008-06-05

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PCT/DE2007/002044 WO2008064639A1 (fr) 2006-11-29 2007-11-13 Combinaison d'un disque d'étanchéité et d'un disque d'entraînement de ressort à lames
PCT/DE2007/002045 WO2008064640A1 (fr) 2006-11-29 2007-11-13 Convertisseur de couple multifonctions destiné à séparer la turbine du moteur au ralenti et procédé de commande pour la séparation d'un convertisseur de couple multifonctions du moteur au ralenti
PCT/DE2007/002046 WO2008064641A1 (fr) 2006-11-29 2007-11-13 Système de transmission de force
PCT/DE2007/002043 WO2008064638A1 (fr) 2006-11-29 2007-11-13 Système de transmission de force, en particulier unité de conversion multifonction

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PCT/DE2007/002044 WO2008064639A1 (fr) 2006-11-29 2007-11-13 Combinaison d'un disque d'étanchéité et d'un disque d'entraînement de ressort à lames
PCT/DE2007/002045 WO2008064640A1 (fr) 2006-11-29 2007-11-13 Convertisseur de couple multifonctions destiné à séparer la turbine du moteur au ralenti et procédé de commande pour la séparation d'un convertisseur de couple multifonctions du moteur au ralenti

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PCT/DE2007/002043 WO2008064638A1 (fr) 2006-11-29 2007-11-13 Système de transmission de force, en particulier unité de conversion multifonction

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DE (4) DE112007002702A5 (fr)
WO (4) WO2008064639A1 (fr)

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JP5428820B2 (ja) * 2009-12-11 2014-02-26 アイシン精機株式会社 クラッチ装置
WO2011110310A2 (fr) * 2010-03-06 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Dispositif de lancement à accouplement hydraulique
WO2012070120A1 (fr) 2010-11-24 2012-05-31 トヨタ自動車株式会社 Dispositif de transmission de puissance pour véhicule
US8974339B2 (en) 2010-11-24 2015-03-10 Toyota Jidosha Kabushiki Kaisha Vehicle power transmission device
JP5594369B2 (ja) 2010-11-24 2014-09-24 トヨタ自動車株式会社 車両用動力伝達装置
US8839922B2 (en) 2010-11-24 2014-09-23 Toyota Jidosha Kabushiki Kaisha Vehicle power transmission device
BR112014007536B1 (pt) 2011-10-05 2021-03-09 Toyota Jidosha Kabushiki Kaisha aparelho para redução de vibração em veículos
JP5983146B2 (ja) * 2012-07-24 2016-08-31 アイシン・エィ・ダブリュ株式会社 発進装置
DE112013006043A5 (de) * 2012-12-17 2015-09-17 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
CN103660910B (zh) * 2013-12-06 2016-01-06 合肥工业大学 一种油电静液复合的混合动力传动***
CN103770623B (zh) * 2014-02-20 2016-03-02 合肥工业大学 一种油电及液压复合的混合动力传动***
DE102015215199A1 (de) * 2015-08-10 2017-02-16 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung
US10041575B2 (en) 2015-12-18 2018-08-07 GM Global Technology Operations LLC Torsional damper system
DE102015226413A1 (de) * 2015-12-22 2017-06-22 Schaeffler Technologies AG & Co. KG Hybridsystem zur Verwendung in einem Hybridfahrzeug
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FR2557658A1 (fr) * 1983-12-29 1985-07-05 Ustav Pro Vyzkum Motorovych Vo Boite hydromecanique de changement de vitesse
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Publication number Publication date
DE112007003308A5 (de) 2009-10-29
DE112007002702A5 (de) 2009-08-13
DE112007002623A5 (de) 2009-08-06
DE112007002624A5 (de) 2009-08-06
JP2008138877A (ja) 2008-06-19
WO2008064639A1 (fr) 2008-06-05
JP2008137650A (ja) 2008-06-19
WO2008064640A1 (fr) 2008-06-05
JP5396627B2 (ja) 2014-01-22
WO2008064638A1 (fr) 2008-06-05
JP5190641B2 (ja) 2013-04-24
JP2008138879A (ja) 2008-06-19

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