WO2008077376A2 - Dispositif de transmission de force - Google Patents

Dispositif de transmission de force Download PDF

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Publication number
WO2008077376A2
WO2008077376A2 PCT/DE2007/002251 DE2007002251W WO2008077376A2 WO 2008077376 A2 WO2008077376 A2 WO 2008077376A2 DE 2007002251 W DE2007002251 W DE 2007002251W WO 2008077376 A2 WO2008077376 A2 WO 2008077376A2
Authority
WO
WIPO (PCT)
Prior art keywords
output
damper
power transmission
transmission device
input
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE2007/002251
Other languages
German (de)
English (en)
Other versions
WO2008077376A3 (fr
Inventor
Stephan Maienschein
Mario Degler
Katja Weislogel
Bruno MÜLLER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Priority to DE112007002955T priority Critical patent/DE112007002955A5/de
Publication of WO2008077376A2 publication Critical patent/WO2008077376A2/fr
Publication of WO2008077376A3 publication Critical patent/WO2008077376A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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 
    • F16H2045/007—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  comprising a damper between turbine of the 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
    • F16H2045/0226—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
    • F16H2045/0231—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 arranged in series
    • 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
    • F16H2045/0273—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 with an input coupled to a drive shaft and an output coupled to an output, in particular transmission input shaft, with a hydrodynamic component comprising a pump wheel which can be connected to the input and a turbine wheel which can be coupled at least indirectly to the output and a turbine wheel between Output arranged damper unit with at least two damper stages.
  • a generic power transmission device is described in DE 199 20 542 A1.
  • This comprises an input and an output designed as a transmission input shaft, a hydrodynamic component, for example in the form of a hydrodynamic speed / torque converter or a hydrodynamic clutch, with at least one, via a connectable to a drive shaft of a drive unit housing, driven impeller and a with The input shaft of a drive train to be driven connectable turbine wheel and optionally at least one stator.
  • a damper unit In the power flow between the turbine and the output of a damper unit is arranged with a relative to the turbine rotationally fixed input part and connected to the output of the power transmission device output part, which are at least counter to the restoring force of arranged between these force or energy storage relative to each other rotatable.
  • a radially outer damper stage and a radially inner damper stage is provided, wherein both may be designed differently.
  • the damper unit with the outer circumference of the turbine wheel is indirectly or directly connected rotationally.
  • the connection can be free of play with respect to coaxial rotations, but allow axial displacement of the turbine wheel with the input part of the damper.
  • the second radially inner damper stage is arranged in the radial direction in the region of the outer diameter of the turbine wheel.
  • the first inner damper stage is arranged free of offset or with little offset in the radial direction within the outer damper stage.
  • Each of the damper stages is quasi formed by a device for damping vibrations, which is characterized by a so-called input part and an output part, wherein the input part is at least indirectly coupled to the input of the power transmission device and the output part usually with the output.
  • Input part and output part are coupled to each other via means for spring and / or damping coupling.
  • the funds only include Spring elements that allow not only the possibility of power transmission and thus training of the individual devices as elastic coupling but also a torque shock absorption.
  • This embodiment allows optimal utilization of the installation space in the axial direction, but makes full use of the installation space in the radial direction at least up to the area of the outer circumference of the hydrodynamic component.
  • the damper stages are differently active with regard to the power transmission in the individual power branches, so that here an interpretation with regard to both power transmission branches must be made. Additional measures serve, inter alia, the bridging of individual damper stages or the limitation of the rotatability of the individual primary and output parts of a device for damping vibrations against one another.
  • this advantage is reduced due to the centrifugal force-dependent friction between bow spring and housing.
  • the invention is therefore based on the object, a power transmission device of the type mentioned in such a way that it can be constructed even easier, the space in the axial and radial directions should be exploited in an optimized manner. Furthermore, the power transmission device should be characterized by low weight and inertia and cost.
  • the inventive solution is characterized by two basic arrangements of a multi-stage damper unit in the power transmission device, which are characterized by the formation of the damper unit with series damper stages and the different ways of connecting the power transmitting elements of the power transmission device, in particular the turbine wheel of a hydrodynamic component.
  • the power transmission device with an input which can be coupled to a drive machine and with an output part of the drive train, in particular an output which can be coupled to the transmission, preferably in the form of a transmission input shaft, comprises for realizing tion of a power flow via a hydrodynamic power branch arranged in this hydrodynamic component.
  • This hydrodynamic component comprises at least one first impeller wheel, which can be connected to the input and, viewed during power transmission from the input to the output, acting as impeller, and a further second turbine impeller, which can be indirectly connected at least indirectly to the output.
  • at least one switchable coupling device is provided, comprising a first and a second coupling part, which can be brought into operative connection with one another via an actuating device.
  • an output upstream damper unit characterized by at least two damper stages, a first radially outer damper stage and a second radially inner damper stage, wherein “radially outer” and “radially inner” to the arrangement with respect to the rotational axis of the power transmission device refers.
  • Both damper stages are arranged coaxially with the axis of rotation of the power transmission device and can be designed as separate devices for damping vibrations, which are combined to form a structural unit or combined in a structural unit, and each include viewed in the power flow so-called input part and an output part, which are coupled to each other via means for spring and / or damping coupling.
  • the damper unit is connected downstream of the individual power branches.
  • the input of the damper unit is then formed by either the radially outer or the radially inner damper stage.
  • the output is then formed by the radially inner or outer damper stage.
  • the radially outer damper stage of the inner damper stage is connected upstream. In this case, the flow of force from an input part of the outer damper stage to the output part of the inner damper stage.
  • the turbine wheel is connected in the radially inner region with the damper unit, that is in the region of the inner circumference or inner diameter.
  • the space in the radial and axial direction can be minimized, in particular in the area of the damper unit, since no costly, in particular an axial offset compensating connection measures between damper and turbine are required and also the connection to the input part of the outer damper stage at the same time to support the Turbine wheel can be used, so that no further additional support is required.
  • the input part of the radially outer damper at least a partial element of the Ei ⁇ gangs presses in the radial direction in the direction of the axis of rotation out pulled out to form a wall and at the same time a stop in the axial direction of the turbine wheel, in which the input part or the Generaleleme ⁇ t, which is rotatably coupled to the turbine, at least indirectly at the output, preferably a rotatably coupled thereto hub in the axial direction toward the damper unit is supported.
  • the output part of the radially outer damper stage is rotatably connected to the input part of the radially inner damper stage.
  • the input part of the radially outer damper stage preferably comprises two disc-shaped elements which are rotatably connected to each other to form a gap and the output part is arranged between the two disc-shaped elements in the axial direction and also designed as a disc element.
  • the input part of the radially inner damper stage comprises either two disc-shaped elements between which the output part is arranged in the form of a disc element in the axial direction, wherein the output member rotatably connected to the output or a non-rotatably coupled to the output element or the output part of the radially inner damper stage formed by at least two disc-shaped elements, between which in the axial direction of the input part is arranged in the form of a disc element.
  • the input part of the radially inner damper stage and the output part of the radially outer damper stage are then preferably formed by a disc element.
  • a Verwarwinkelbegrenzung is provided between an element of the input part of the second radially inner damper stage and the output or an element rotatably connected thereto.
  • the radially inner and radially outer damper stage are viewed in the axial direction between input and output in an axial plane or with a slight offset in the axial direction to each other.
  • the radially outer damper stage can be arranged in a region which is characterized by an extent in the radial direction, which is smaller than or equal to the radially outer extent of the hydrodynamic component by the connection of the turbine wheel in the region of the inner circumference, the radially outer damper stage
  • the radially inner damper stage is connected upstream of the radially outer.
  • the input of the damper assembly is formed by the input part of the radially inner damper stage, the output of the radially outer damper stage.
  • the input part of the radially outer damper stage is rotatably connected to the output part of the radially inner damper stage.
  • the input part of the radially outer damper stage preferably comprises two disc-shaped elements which are rotatably connected to each other to form a gap and the output member is disposed between the two disc-shaped elements in the axial direction as a disc member and rotatably connected to the output of the power transmission device.
  • the input part of the radially inner damper stage comprises either two disc-shaped E- elements between which the output member is arranged in the form of a disc member in the axial direction, wherein the output member rotatably connected to the input part of the radially outer damper stage or the output part of the radially inner damper stage is of at least formed two disc-shaped elements, between which in the axial direction of the input part is arranged in the form of a disc element.
  • the output part of the radially inner damper stage and the input part of the radially outer damper stage are then preferably formed by a disc element.
  • connection is preferably made in the radially outer region of the turbine wheel.
  • the power transmission device having an input coupled to a drive shaft and an output coupled to an output, in particular a transmission input shaft for realizing the force flow in two power branches, a hydrodynamic power branch and a mechanical power branch, with a hydrodynamic component arranged in the hydrodynamic power branch.
  • a switchable coupling device arranged in the mechanical power branch, comprising a first and a second coupling part which can be brought into operative connection via an actuating device and a damper unit comprising at least two damper stages , a radially outer damper stage and a further radially inner damper stage, each comprising an input part and an output part, which are coupled together via means for spring and / or damping coupling, characterized in that the output of the damper unit at least indirectly with the output is connected and the input of the damper unit is formed in the individual power branches of different damper stages.
  • the input of the damper unit is formed here depending on the direction of force flow and transmission in different power branches either on the radially inner damper stage or the radially outer damper stage.
  • the input of the damper unit is preferably formed in the mechanical power branch at the radially inner damper stage, in the hydrodynamic power branch at the radially outer damper stage.
  • the turbine wheel is quasi interposed between the two damper stages and both damper stages are effective only in power transmission with closed switchable clutch in the mechanical power branch, while in purely hydrodynamic power transmission, only the radially outer damper stage is effective.
  • the inner damper stage serves as absorber due to its coupling with the outer damper stage, in particular the input member of the enlargement of the mass of the turbine wheel and due to the opened coupling device. For this purpose, different possibilities can be distinguished.
  • an element forming the input part with an additional function as an inner disk carrier is characterized by a high functional concentration.
  • the means for spring and / or damping coupling are arranged. These are preferably simple tension or compression springs or bow springs.
  • the turbine wheel is also connected to the damper unit, but here the output of the damper unit is formed by the radially outer damper stage, in particular the output part thereof.
  • the output part is non-rotatably connected to the output or an at least indirectly rotatably coupled to the transmission input shaft coupled element.
  • the turbine wheel is also coupled to the radially outer damper stage, wherein the connection is preferably rotationally fixed again in the region of the inner diameter of the turbine wheel to the outer damper stage, for which purpose this can be carried in the radial direction in the direction of the axis of rotation of the power transmission device and at the same time serves by support on the hub member or the transmission input shaft of the support of the turbine wheel in the axial direction.
  • the individual damper stages can be dimensioned to each other in terms of their effective range and the vote.
  • the concrete interpretation lies at the discretion of the competent expert. This also applies to the type of means used for spring and / or damping coupling. In the simplest case, spring units are used for both functions. However, it is also conceivable embodiments with additional hydraulic damping chambers or other damping elements, such as additional friction points, etc.
  • the switchable coupling device can be designed in many forms.
  • frictional coupling means are used. These are in disk construction, preferably in lamellar construction, and are characterized in that at least one of the coupling parts friction surfaces having elements which can be brought into operative connection with other intermediate elements of the other coupling part to produce a frictional engagement.
  • the first coupling part is rotatably connected to the input, while the second coupling part is rotatably connected to the damper assembly.
  • the second coupling part is non-rotatably connected to the input of the damper assembly, in particular the outer damper stage connected.
  • the coupling takes place with the input part.
  • AIIe designs can be equipped with additional means for Verfwinkelbegrenzung or bridging the individual damper stages.
  • the non-rotatable connections are realized according to the application requirements. These can be based on form, force or material bond.
  • the formation of the input and output parts can be done in various ways. These may include one or more disc-shaped elements depending on the damper design.
  • FIG. 1 a schematically illustrates the coupling structure and force flow of a first one
  • Figure 1 b illustrates in axial section a first embodiment of a first
  • Figure 1 c illustrates in axial section a second embodiment of a first
  • FIG. 2 a schematically illustrates the coupling structure and the force flow of a second basic embodiment of a power transmission device according to the invention with a multi-stage damper unit;
  • Figure 2b illustrates in axial section a first embodiment of a second
  • Figure 2c illustrates in axial section a second embodiment of a second
  • Figure 3a illustrates a sub-variant of the first basic design with arrangement of
  • FIG. 3b illustrates a structural design according to FIG. 3a.
  • FIG. 1 a schematically illustrates the coupling structure of a first basic embodiment of a power transmission device 1 designed according to the invention with a multi-stage damper unit 9.
  • FIG. 1b illustrates a possible structural design of the first basic embodiment in axial section.
  • the power transmission device 1 comprises a hydrodynamic component 2 with at least one first impeller wheel functioning as an impeller P during power transmission from an input E to an output A and a second impeller wheel acting as a turbine wheel T.
  • the hydrodynamic component is designed as a hydrodynamic speed / torque converter 3 and additionally comprises at least one stator L, which is supported on a stationary element via a freewheel F to a stationary or rotatable element. In the case shown, the support is on the support shaft 13.
  • the design of the hydrodynamic component 2 in the form of a hydrodynamic coupling is free of a stator.
  • the function is then only in the speed conversion, while the hydrodynamic speed / torque converter 3 acts as a hydrodynamic transmission.
  • the connection between input E and output A via the hydrodynamic component 2 describes a hydrodynamic power branch 14.
  • the power transmission device 1 comprises a connectable to a drive shaft of a drive unit housing 4, which is rotatably connected to the impeller P and in the axial and in the radial direction of the Turbine T surrounds to form an inner space 5.
  • the housing 4 can be made in one or more parts.
  • this generally comprises a cover element 6, which forms the input E of the power transmission device 1 or is non-rotatably coupled thereto and is connected to a pump wheel shell 50 that is non-rotatably connected to the impeller P or an integral structural unit.
  • the impeller P is driven via the housing 4, in particular the cover element 6.
  • the turbine wheel T is connected to a shaft of a strand to be driven, in particular a transmission input shaft 7, at least indirectly non-rotatably. At least indirectly means either directly or via other transmission elements, wherein the speed and the torque can be over or reduced to the transmission elements, that is, a speed and torque conversion can be done or transferred without being converted.
  • the power transmission device 1 further comprises a switchable coupling device 8 arranged in the interior 5 for bridging or bypassing the power transmission via the hydrodynamic component 2 and thus of the hydrodynamic power branch 14 in a second, mechanical power branch 15.
  • the switchable coupling Ventilation device 8 comprises at least two coupling parts 8.1 and 8.2, which can be brought into operative connection with each other. Depending on the type of coupling device used and operating principle, these can be designed in various ways. Preferably, frictional clutches are used.
  • the first and the second coupling part 8.1, 8.2 is formed by Reibvidtragenden or with these operatively engageable elements.
  • Both power branches 14, 15 are arranged parallel to one another, wherein the power transmission can take place via each branch alone or simultaneously in power branching over both.
  • the damper unit 9 comprising at least two damper stages 10 and 11, which are connected to each other in series within the damper unit 9.
  • the damper unit 9 is further connected in series according to the first basic version of both power branches 14 and 15, that is, downstream of each of the two power branches in the power flow between input E and output A.
  • the individual damper stages 10 and 11 are thus passed through or effective in both power branches. This applies to traction as well as power flow reversal in overrun.
  • the damper unit 9 is therefore designed according to the first basic design as a series turbine damper, in which the turbine mass is located in front of the two damper stages 10,11. Spatially, a damper stage is viewed in the radial direction with respect to the axis of rotation R of the power transmission device 1 is arranged radially within the other damper stage, here the damper stage 11 is disposed radially within the damper stage 10.
  • the damper stage 10 is referred to as the first radially outer damper stage and the damper stage 11 as the second radially inner damper stage.
  • the radially outer damper stage acts as the main damper stage and the radially inner damper stage as the damper stage.
  • the main damper stage means that the maximum momentum is to be transmitted via this, which is why it is also characterized by larger transmission means.
  • Pre-damper means that this describes the first part of the torque-spring characteristic in the overall characteristic of the damper unit. In terms of the power flow, this means that first the pre-damper stage acts and then the main damper stage. Due to the general arrangement of this additional damper stage 11 radially inward, overall lower weights, inertia and cost arise.
  • FIG. 1b illustrates a first constructional embodiment.
  • Each of the damper stages 10 and 11 is of a Device 16 for damping vibrations or 17 is formed, wherein the devices 16 and 17 are combined in the damper unit 9.
  • Each individual damper stage 10, 11 is therefore characterized by an input part 16.1 or 17.1 and an output part 16.2 or 17.2.
  • the terms "input part” and “output part” stand for the function and can be constructively composed of one or more components.
  • the function as an input part and output part refers to the direction of power flow in traction mode, that is, in power transmission from the input E to the output A. In overrun operation, the function of the input part is then assigned accordingly the output part.
  • the input and output parts of the individual damper stages 10, 11 are coupled to each other via means 18, 19 for spring and / or damping coupling.
  • a functional concentration can be achieved by individual elements of a device for damping vibrations can be used simultaneously to form an element of the other device for damping vibrations.
  • the arrangement of the means for spring and / or damping coupling 18,19 prevail. The arrangement is carried out on different diameters relative to the axis of rotation R.
  • Each device for damping vibrations comprises an input part 16.1 or 17.1 and at least one output part 16.2 and 17.2, wherein input part and output part are respectively coupled to each other via means 18 and 19 for spring and / or damping coupling.
  • a functional concentration in the means 18, 19 can take place, in that the means for spring and damping coupling are formed by the same components. This also depends in detail on the specific design of the individual devices 16, 17 for damping vibrations and the selected damper principle.
  • Input part 16.1, 17.1 and output part 16.2, 17.2 are limited relative to each other in the circumferential direction rotatable.
  • both damper stages 10 and 11 are connected in series, the damper stage 10 being formed by the device 16 and the damper stage 11 by the device 17.
  • the input 9.1 of the damper unit 9, which is connected to the switchable clutch device 8 and the turbine wheel T is formed by the input part 16. 1 of the radially outer damper stage 16.
  • the output 9.2 of the damper unit is formed by the second radially inner damper stage, in particular its output part 17.2, which is non-rotatably connected to the output A in the form of the transmission input shaft 7.
  • output part 16.2 of the radially outer damper stage 10 and input part 17.1 of the radially inner damping stage 11 are connected to each other in a rotationally fixed manner.
  • FIG. 1 b illustrates a first possible structural design for this purpose.
  • the two damper stages 10 and 11 are arranged in the radial direction in the region of an axial plane, that is, the offset in the axial direction is small or even free of offset.
  • the spatial arrangement of the damper unit 9 in the power transmission device 1 takes place in the axial direction between the arrangement of the switchable clutch 8 and the hydrodynamic component 2.
  • the extension of the damper unit 9 in the radial direction preferably takes place only in the region of the outer radial extent 20 of the switchable Coupling device 8 or only slightly above.
  • the radial extent 21 of the damper unit 9 in the radial direction is less than or equal to the maximum extent in the radial direction outer extent 22 of the hydrodynamic component, that is, the dimensions of the outer circumference in the radial direction.
  • the arrangement of the two damper stages 10 and 11 is carried out as already mentioned in the radial direction into each other, wherein the two damper stages are designed either in an axial plane or with a slight offset to each other.
  • the individual coupling parts 8.1 and 8.2 of the switchable coupling device 8 are designed in a lamellar design in each case as a plate carrier with arranged thereon and 'slidably mounted lamellae.
  • the first coupling part 8.1 rotatably connected to the input E, in particular the lid 6, connected.
  • the first coupling part comprises a plate carrier 23, which is designed in particular as an outer plate carrier and is arranged on the inner circumference 24 of the housing, in particular of the cover 6, extends in the axial direction into the inner space 5 and carries friction-surface-carrying elements or counter-elements.
  • the second coupling part 8.2 comprises a plate carrier 25, which is designed as an inner disc carrier and carries Reib medicinalgende elements or counter-elements.
  • the switchable coupling device 8 is further associated with an actuating device 26 which comprises at least one piston element 27, which comprises the two coupling parts 8.1 and 8.2 brings together in operative connection, in the specific case allows a frictional engagement between the Reib schizophreniagenden element and the counter-elements.
  • the assignment of the friction surfaces can be done to the first or the second coupling part 8.1, 8.2.
  • the support takes place on a stationary stop 28, which is arranged on the first coupling part 8.1.
  • the input part 16.1 of the first damper stage 10 is preferably designed according to the embodiment in Figure 1 b at least two parts, consists in the simplest case of two disc-shaped elements 29 and 30, which are arranged spaced apart in the axial direction to each other and preferably rotatably coupled to each other, wherein under training an axial gap 31, the arrangement of the output part 16.2 in the form of a further disc-shaped element 32, for example, a drive plate is effected.
  • the term disc-shaped ele- ment is to be understood here only in terms of the basic design. In analogy, this also applies to the second damper stage 11.
  • the output part 17.2 is formed from two disc-shaped elements 33 and 34, which are arranged spaced apart from one another in the axial direction and are preferably coupled to one another in a rotationally fixed manner.
  • an axial gap 51 is formed, in which the arrangement of the input part 17.1 in the form of another disc-shaped element 35, takes place.
  • the rotationally fixed coupling between the output part 16.2 and the input part 17.1 is realized by combining them into a single disk element.
  • the means for spring and / or damping coupling 18 and 19 of the individual damper stages 10, 11 comprise in the illustrated case each spring units 18.1 Zw.
  • the disk element 35 which forms the input part 17.1 and which is non-rotatably connected to the disk element 32 of the first damper stage 10, has an angle of rotation limitation 52.
  • the disc element 35 has, in the region of its inner circumference, a recess 53 which is aligned in the circumferential direction and which is formed with a stop, which in the case shown is formed by the connecting element, in particular the hub 37.
  • the inner damper stage 11 is bridged, ie only the outer damper stage 10 is then effective.
  • torque is introduced at the input part 16.1 of the main damper stage, which is transmitted via 16.2 to the input part 17.1.
  • the radially inner damping stage 11 is effectively and effectively downstream of the outer.
  • the coupling of the second coupling part 8.2 is rotationally fixed to the input part 16.1 of the first outer damper stage 10, in particular of the device 16 for damping vibrations. Furthermore, there is a direct rotationally fixed coupling between the turbine wheel T and the device 16 for damping vibrations, in particular the input part 16.1.
  • the connection of the turbine wheel, in particular the non-rotatable connection, which is designated here by 36, takes place in the radially inner region of the damper unit 9, that is, here at the radially inner region of the device 16 for damping vibrations.
  • the output part 16.2 of the device 16 for damping vibrations is rotatably connected to the input part 17.1 of the device 17 for damping vibrations of the second radially inner damper stage 11, wherein the output part 17.2 is rotatably coupled to the transmission input shaft 7.
  • the coupling takes place at least indirectly, that is either directly or as shown in Figure 1 b via a hub 37th
  • the embodiment of Figure 1 b shows an embodiment of the power transmission device as a three-channel system.
  • the working space is formed by space enclosed by the primary wall P and by the turbine wheel T.
  • the second pressurizable medium 39 is formed by the inner space 5, which is formed between the inner periphery 24 of the housing and the outer periphery of the hydrodynamic component and in which the switchable coupling device 8 and the damper unit 9 are arranged.
  • the third actable with pressure medium chamber 40 is associated with the switchable coupling 8 and part of the actuator 26.
  • connection channels that connect these pressure chambers with a corresponding pressure medium supply source or a pressure medium system.
  • the term connection does not include a specification for a concrete structural design of the connection.
  • a first connection is assigned to the working space. This is designated 45.
  • the first port 45 is provided in the region of the inner diameter or inner circumference of the hydrodynamic component 2 and is formed, for example, by a supply line 46 between the impeller shaft 47 and a support shaft 13 for supporting the stator L.
  • the second connection 48 serves to connect to the second pressure chamber 39, and the third connection 49 is connected to the space 40 which can be acted upon with pressure medium, this being guided, for example, through the transmission input shaft 7.
  • the first and the second connection 47, 48 can be coupled together to form a resource circuit, in particular for the external management of resources from the hydrodynamic component 2 during operation or non-operation for the purpose of cooling.
  • the coupling can also take place via corresponding external circuits, which are guided either in the subsequent transmission or otherwise outside the power transmission device 1.
  • the lock-up clutch 8 is deactivated.
  • the impeller P is driven via the housing, in particular the cover 6, and due to the circulation of equipment in the working space there is a power transfer to the turbine wheel, which is rotatably connected to the damper unit, in which case the coupling with the input part of the first damper stage 10 takes place.
  • the input of the damper unit 9 is thus formed in both cases here from the input part 16.1 of the first damper stage 10.
  • FIG. 1 c illustrates an alternative embodiment of the inner damper stage 11 for an embodiment according to FIG. 1 b. The rest of the construction corresponds to that described in FIG. 1 b, for which reason the same reference numerals are used for the same elements and these elements and their coupling are not discussed again.
  • the input 9.1 of the damper unit 9 is formed by the input part 16.1 of the radially outer damper stage 10, in the case illustrated by the disc elements 29 and 30.
  • the output 9.2 of the damper unit 9 is formed by the output part 17.2 of the second inner damper stage 11, which in the embodiment of FIG 1c is present as a disk element 35.
  • the input part 17.1 is formed from the two disk-shaped elements 33 and 34, which are arranged spaced apart in the axial direction to one another and are preferably coupled to each other in a rotationally fixed manner. In this case, an axial gap 51 is formed, in which the arrangement of the output part 17.2 in the form of the disk-shaped element 35, takes place.
  • the rotationally fixed coupling between the output part 16.2 and the input part 17.1 is realized by the summary of this to a single disc element or the disc elements 32 and 33 are rotatably connected with each other.
  • the means for spring and / or damping coupling 18 and 19 of the individual damper stages 10, 11 in the illustrated case also comprise spring units 18.1 Zw. 19.1, which in the circumferential direction with their ends on the input part 16.1 or 17.1 and with the other end portion on the output part 16.1 , 17.2 of the respective damper stage 10, 11 are supported.
  • the spring units 18.1 and 19.1 of the individual damper stages are designed differently, as already stated, the main damper 10 must be able to transmit the maximum torque.
  • the input part 17.1 forming disc element 34 is assigned a Verwarwinkelbegrenzung 52.
  • the disc element 34 in the region of its inner circumference has a recess aligned in the circumferential direction, which with a stop, which in the case illustrated by the connecting element, in particular the hub 37 is formed on. If the angle of rotation defined by the recess is reached, the inner damper stage 11 is bridged, ie only the outer damper stage 10 is then effective.
  • FIGS. 1 a to 1 c illustrate embodiments with pure row turbine dampers
  • FIGS. 2 a to 2 c illustrate an embodiment with the possibility of increasing the turbine mass in a second embodiment of a damper unit 9 according to the invention in a power transmission device 1 with at least two downstream damper stages 10 and 11.
  • the execution of the power transmission device 1 is carried out except the integration of the damper unit 9 as shown in Figure 1a or 1b.
  • the turbine mass is vibrationally arranged between the two damper stages 10 and 11.
  • a first damper stage 10 is provided and a second Damping stage 11, which is effective only in bridged operation.
  • the second radially inner damper stage 11 of the switchable coupling unit 8 is arranged downstream and the first damper stage 10 in power transmission from the input E to the output A upstream. In the unbridged state, the second radially inner damper stage 11 then acts as a absorber.
  • FIG. 2a illustrates the illustration of couplings in the power branches 14 and 15. It can be seen that, although the damper unit 9 is connected in series with both the switchable clutch 8 and the hydrodynamic component 2, the individual damper stages 10, 11 are assigned differently to these elements are and the coupling of the two damper stages 10 and 11 is also done differently.
  • the inner damper stage 11 is connected in series with the coupling device 8 in the power flow between input E and output A and upstream of the first outer damper stage 10 viewed spatially, the turbine wheel T, however, assigned only as additional mass due to the coupling with the input part 16.1.
  • first outer damper stage 10 which acts here as the main damper stage, the hydrodynamic component 2 downstream or downstream and thus arranged between the turbine T and output A, while the second radially inner damper stage 11 of the switchable coupling device 8 is arranged downstream, however first outer damper stage 10 only in power transmission via the switchable coupling device 8, that is, the mechanical power branch 15 upstream is.
  • the rotationally fixed coupling between the switchable coupling device 8, in particular the second coupling part at power transmission from the input to the output A with acting as the input input part 17.1 of the second radially inner damper stage 11 of the device 17.
  • the acting as an output of the device 17 elements of the output part 17.2 are non-rotatably connected to the then acting as an input for the downstream damper stage 10 input part 16.1 of the damper stage 10, in particular means 16, respectively.
  • the output part of the damper stage 10, which acts as a main damper stage, is rotatably connected to the output A, here via the hub member, and forms the output 9.2 of the damper unit.
  • FIG. 2b The structural design is shown in FIG. 2b.
  • the damper stage 11 which functions as the front damper stage in this embodiment is arranged in the radial direction within the outer damper stage 10 forming the main damper stage.
  • the arrangement takes place here only with a small offset in the axial direction to each other, wherein the coupling of the output part 17.2 with the input part 16.1 is such that preferably these can be formed from one and the same element.
  • the input part 16.1 of the radially outer damper stage 10 is preferably designed according to the embodiment in Figure 2b at least two parts, consists in the simplest case of two disc-shaped elements 29 and 30, which are arranged spaced apart in the axial direction to each other sihd and preferably rotatably coupled to each other, wherein under training an axial gap 31, the arrangement of the output part 16.2 in the form of a further disc-shaped element 32, for example, a drive plate is effected.
  • the term disk-shaped element is to be understood here only in terms of the basic design. In analogy, this also applies to the second radially inner damper stage 11.
  • the output part 17.1 is formed from two disc-shaped elements 33 and 34, which are arranged spaced apart from one another in the axial direction and are preferably coupled to one another in a rotationally fixed manner.
  • an axial gap 51 is formed, in which the arrangement of the output part 17.2 in the form of another disc-shaped element 35, takes place.
  • the means for spring and / or damping coupling 18 and 19 of the individual damper stages 10, 11 comprise in the illustrated case each spring units 18.1 zw.
  • the disk element 35 forming the input part 17. 1 preferably has an angle of rotation limitation 52.
  • the disc element 35 has, in the region of its inner circumference, a recess 53 oriented in the circumferential direction, which cooperates with a stop, which in the case shown is formed by the connecting element, in particular the hub 37. If the angle of rotation defined by the recess is reached, the inner damper stage 11 is bridged, ie only the outer damper stage 10 is then effective.
  • the turbine wheel T is preferably coupled in its radially inner region 12 with the damper unit 9.
  • FIG. 2c is characterized with respect to FIG. 2b by another embodiment of the radially inner damper stage 10, in particular of the input and output part 17.1, 17.2.
  • the execution of the other components is carried out according to Figure 2b, which is why the same reference numerals are used for the same elements.
  • the input part 17.1 of two disc-shaped elements 33 and 34 which are arranged spaced apart in the axial direction to each other and are preferably rotatably coupled to each other, is formed.
  • the connection with the radially outer damper stage 10 takes place via the output part 17.2 in the form of the disc element 35. This is arranged in the axial intermediate space 51 between the disc elements 33, 34.
  • the means for spring and / or damping coupling 18 and 19 of the individual damper stages 10, 11 comprise in the illustrated case each spring units 18.1 zw. 19.1 , which are supported in the circumferential direction with their ends on the input part 16.1 or 17.1 and with the other end region on the output part 16.1, 17.2 of the respective damper stage 10, 11.
  • the spring units 18.1 and 19.1 of the individual damper stages are preferably designed differently. As already stated, the main damper 10 must be able to transmit the maximum torque.
  • the disk element 34 which forms the input part 17.1 and which is rotationally fixedly connected to the disk element 32 of the radially outer damper stage 10 or forms a structural unit, has an angle of rotation limitation 52 on.
  • the disc element 34 has, in the region of its inner circumference, a recess oriented in the circumferential direction, which cooperates with a stop, which in the case shown is formed by the connecting element, in particular the hub 37. If the rotation angle defined by the recess is reached, the inner damper stage 11 is bridged, ie only the outer damper stage 10 is then effective.
  • the inner lamp carrier 25 is embodied on the input part 17. 1 in a particularly advantageous manner, so that a high functional concentration in the installation element takes place here.
  • Figure 3 illustrates a particularly advantageous embodiment, with which depending on the connection of the turbine wheel T to the input or output parts 17.1, 17.2 of the radially inner damper stage 11 an embodiment of a pure turbine damper with power flow according to Figure 1, as modified in Figure 3a reproduced or a damper according to Figure 2 with increase of the turbine wheel mass, as illustrated by the connection shown in broken line in Figure 3a, can be realized.
  • the connection of the turbine wheel T does not take place in the region of its inner circumference to the damper unit 9, but due to the spatial conditions in the region of the outer circumference.
  • the coupling of the turbine wheel T is not carried out to the main damper stage 10, but to the radially inner damper stage 11 used as a predamper stage.
  • the figure 3a is characterized by the series circuit of the damper unit 9 to the switchable clutch 8 and the hydrodynamic component 2, in which case the second radially inner damper stage 11 of the first radially outer damper stage is upstream of coupling technology.
  • the input 9.1 of the damper unit 9 is formed by the radially inner damper stage 11, the output 9.2 of the radially outer damper stage 10.
  • Figure 3a illustrates the coupling of the turbine wheel T with the input part 17.1 of the radially inner damper stage 11.
  • the coupling possibility with the output part 17.2 is shown only with a broken line.
  • the input part 17.1 of the second radially inner damper stage 11 is in this case with the switchable
  • the input part 17.1 consists of two disk elements 33 and 34, which are coupled to each other in a rotationally fixed manner.
  • a further rotationally fixed connection between a drive plate of the input part 17.1 and the hydrodynamic component 2 is provided.
  • the output part 17.2 is rotatably coupled to the input part 16.1 of the damper stage 10 of the main damper.
  • the output part 16.2 of the radially outer damper 16 is non-rotatably connected to the output A, in particular the transmission input shaft 7, connected.
  • the pre-damper stage acts directly as a torsional vibration damper or merely as a damper.
  • the turbine wheel would be non-rotatably coupled to the output part 17.2 of the radially inner damper stage 11.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Motor Power Transmission Devices (AREA)

Abstract

Dispositif de transmission de force comportant une entrée couplée à un arbre d'entraînement et une sortie couplée à un élément de sortie, en particulier à un arbre d'entrée de transmission, un composant hydrodynamique comportant une roue de pompe pouvant être couplée à l'entrée et une roue de turbine pouvant être couplée au moins indirectement avec la sortie, et une unité d'amortissement située entre la roue de turbine et la sortie et comprenant deux étages d'amortissement, à savoir un premier étage d'amortissement radial externe et un autre étage d'amortissement radial interne formés chacun de dispositifs pour l'amortissement de vibrations, et comprenant au moins une partie d'entrée et une partie de sortie couplées ensemble par des moyens de couplage élastique et / ou d'amortissement. La présente invention est caractérisée par le fait qu'elle permet différentes possibilités de couplage des différents éléments aux étages d'amortissement.
PCT/DE2007/002251 2006-12-27 2007-12-13 Dispositif de transmission de force Ceased WO2008077376A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112007002955T DE112007002955A5 (de) 2006-12-27 2007-12-13 Kraftübertragungsvorrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006061542 2006-12-27
DE102006061542.5 2006-12-27

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WO2008077376A2 true WO2008077376A2 (fr) 2008-07-03
WO2008077376A3 WO2008077376A3 (fr) 2008-10-16

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975466A2 (fr) 2007-03-26 2008-10-01 ZF Friedrichshafen AG Dispositif d'embrayage hydrodynamique
DE102011003845A1 (de) * 2011-02-09 2012-08-09 Zf Friedrichshafen Ag Drehmomentübertragungsanordnung, insbesondere hydrodynamischer Drehmomentwandler

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19920542A1 (de) * 1998-05-06 1999-11-18 Luk Getriebe Systeme Gmbh Kraftübertragungseinrichtung
ATE449273T1 (de) * 2006-01-12 2009-12-15 Luk Lamellen & Kupplungsbau Wandler mit zwangs-ölführung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975466A2 (fr) 2007-03-26 2008-10-01 ZF Friedrichshafen AG Dispositif d'embrayage hydrodynamique
EP1975466A3 (fr) * 2007-03-26 2011-08-10 ZF Friedrichshafen AG Dispositif d'embrayage hydrodynamique
EP2481952A1 (fr) * 2007-03-26 2012-08-01 ZF Friedrichshafen AG Dispositif d'embrayage hydrodynamique
DE102011003845A1 (de) * 2011-02-09 2012-08-09 Zf Friedrichshafen Ag Drehmomentübertragungsanordnung, insbesondere hydrodynamischer Drehmomentwandler
DE102011003845B4 (de) * 2011-02-09 2018-12-27 Zf Friedrichshafen Ag Drehmomentübertragungsanordnung, insbesondere hydrodynamischer Drehmomentwandler

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DE112007002955A5 (de) 2009-09-03
WO2008077376A3 (fr) 2008-10-16

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