Abstract:
An automotive drive train having an internal combustion engine that is configured as a six-cylinder engine and a hydrodynamic torque converter device. The device has a torsional vibration damper consisting of two energy accumulating devices and a converter lockup clutch. The turbine wheel is interposed between the two energy accumulating devices. The mass moment of inertia should be high between the two energy accumulating devices and masses should be as little as possible between the torsional vibration damper and the transmission input shaft.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is the National Stage of PCT International Application No. PCT/DE2006/001793, filed Oct. 12, 2006, which application published in German and is hereby incorporated by reference in its entirety; said international application claims priority from German Patent Application No. 10 2005 053 601.8, filed Nov. 10, 2005 which is incorporated by reference in its entirety. 
     
    
     FIELD OF THE INVENTION 
       [0002]    The invention relates to an automotive drive train having a combustion engine configured as a six-cylinder engine, wherein the motor vehicle drive train comprises a torque converter device, comprising a torque converter lockup clutch, a torsion vibration damper, and a converter torus, formed by a pump shell, a turbine shell, and a stator shell, wherein the torsion vibration damper furthermore comprises a first energy accumulator means and a second energy accumulator means, and wherein between the first and second energy accumulator means, a first component is provided, which is connected in series with the first and second energy accumulator means, and wherein the turbine shell comprises an outer turbine dish, which is connected non-rotatably to the first component. 
       BACKGROUND OF THE INVENTION 
       [0003]    From German Patent No. DE 103 58 901 A1, a torque converter device is known, which comprises a converter lockup clutch, a torsion vibration damper, and a converter torus formed by a pump shell, a turbine shell and a stator shell, and wherein the torque converter device is obviously intended for a motor vehicle drive train. In the embodiments shown in FIGS. 1, 4 and 5 of German Patent No. DE 103 58 901 A1, a first component is apparently provided between a first and a second energy accumulator means of the torsion vibration damper, the first component is connected in series with the two energy accumulator means and connected non-rotatably to the outer turbine dish of the turbine shell. 
       BRIEF SUMMARY OF THE INVENTION 
       [0004]    It is the object of the invention to configure a motor vehicle drive train comprising a six-cylinder engine and a torque converter device, so it is well suited for motor vehicles with respect to its vibration properties, or torsion vibration properties, so that the motor vehicles provide convenient driving comfort. 
         [0005]    Thus, a motor vehicle drive train is proposed, in particular, which comprises a six-cylinder engine or a combustion engine configured as six-cylinder engine. The combustion engine or the six-cylinder engine has a maximum engine torque M mot, max . The motor vehicle drive train furthermore comprises an engine output shaft or a crank shaft and a transmission input shaft. Furthermore, the motor vehicle train comprises a torque converter device. The torque converter device comprises a converter housing, which is coupled to the engine output shaft, or to the crank shaft, preferably non-rotatably. Furthermore, the torque converter device comprises a converter lockup clutch, a torsion vibration damper and a converter torus formed by a pump shell, a turbine shell and a stator shell. The torsion vibration damper comprises a first energy accumulator means and a second energy accumulator means, connected in series with the first energy accumulator means. The first energy accumulator means comprises one or more first energy accumulators, or is formed by one or more first energy accumulators, and the second energy accumulator means comprises one or more second accumulators, or is formed by one or more second accumulators. Between the first and second energy accumulator means, a first component is provided, which is connected in series with the two energy accumulator means. This is done in particular, so that a torque can be transferred from the first energy accumulator means through the first component to the second energy accumulator means. 
         [0006]    It is appreciated that a means, which is designated as “converter torus”, in this application is sometimes designated as “hydrodynamic torque converter”. The term “hydrodynamic torque converter”, however, is also partially used in prior applications for devices, which comprise a torsion vibration damper, a converter lockup clutch and a means formed by a pump shell, a turbine shell and a stator shell, or according to the language of the present disclosure a converter torus. With this background, the terms “hydrodynamic torque converter device” and “converter torus” are used in the present disclosure for reasons of clarity. 
         [0007]    The turbine shell comprises an outer turbine dish, which is connected non-rotatably to the first component. Furthermore, the torque converter device comprises a third component, which is preferably connected non-rotatably to the transmission input shaft, which in particular abuts to the torque converter device. It can for example be provided, that the third component is directly coupled to the transmission input shaft, in particular coupled non-rotatably. However, it can also be provided that the third component is coupled to the transmission input shaft through one or several components connected in between, in particular coupled non-rotatably. The third component is connected in series to the second energy accumulator means and to the transmission input shaft, so that torque can be transferred from the second energy accumulator means through the third component to the transmission input shaft. The third component is thus disposed in particular between the second energy accumulator means and the transmission input shaft. 
         [0008]    When transferring a torque through the first component, a change of the torque, which is transferred through the first component, is counteracted by a first mass moment of inertia. The first mass moment of inertia thus is also comprised in particular of the mass moment of inertia of the first component and of the mass moments of inertia of one or several possibly additional components, which are coupled to the first component, so that their respective mass moment of inertia also counteracts a change of the torque transfer through the first component, when transferring a torque through the first component. Such couplings can for example be non-rotatable couplings, in particular with reference to a rotation about the rotation axis of the torsion vibration damper. It is discussed supra, that the first mass moment of inertia during the transmission of a torque through the first component counteracts a change of the torque transferred through the first component. It is appreciated, that it is in particular also provided, that when no torque is transferred through the first component, the first mass moment of inertia counteracts the transfer of a torque through the first component. The first component preferably is a flange or a plate, wherein it is provided in particular, that the outer turbine dish and/or an inner turbine dish and/or blades or a blade assembly of the turbine shell or of the turbine is a component, or an assembly of several components, which is (are) coupled to the first component, so that its mass moment(s) of inertia add(s) to the first mass moment of inertia and thus in particular respectively as a summand of several summands. 
         [0009]    When transferring a torque through the third component, a second mass moment of inertia counteracts a change of the torque transferred through the third component. The second mass moment of inertia thus is comprised in particular of the mass moment of inertia of the third component and the mass moments of inertia of one or several respective additional components, which are coupled to the third component, so that their respective mass moment of inertia counteracts the transfer of a torque through the third component when the torque transferred through the third component changes. Such couplings can for example be non-rotatable couplings, in particular with reference to a rotation about the rotation axis of the torsion vibration damper. It is discussed supra, that the second mass moment of inertia when transferring a torque through the third component counteracts a change of the torque transferred through the third component. It is appreciated that it is provided in particular, that when no torque is transferred through the third component, the second mass moment of inertia counteracts the transfer of a torque through the third component. 
         [0010]    It is provided that the motor vehicle drive train, or the torque converter device, or the torsion vibration damper, or the first energy accumulator means is configured, so that the spring constant [in the units of Newton meter per degree (Nm/°)] of the first energy accumulator means is greater than or equal to the product of the maximum engine torque [in the units of Newton meter (Nm)] of the six-cylinder engine and the factor of 0.014 [in the units of per degree (1/°)] and less than or equal to the product of the maximum engine torque [in the units of Nm] of the six-cylinder engine and the factor 0.068 [in the units of 1/°]. Put into an equation, this means: 
         [0000]      (M mot,max  [Nm]*0.014 [1/°])≦c 1 ≦(M mot,max  [Nm]*0.068 [1/°]), 
         [0000]    wherein M mot,max  [Nm] is the maximum engine torque of the combustion engine or of the six-cylinder engine of the drive train in the units of “Newton times meter” (Nm), and wherein c 1  is the spring constant of the first energy accumulator means in the units of “Newton times meter divided by degrees” (Nm/°). 
         [0011]    It is furthermore provided, that the motor vehicle drive train, or the torsion vibration damper or the second energy accumulator means is configured, so that the spring constant [in the units of Nm/°] of the second energy accumulator means is greater than or equal to the product of maximum engine torque [in the units of Nm] of the six-cylinder engine and the factor 0.035 [in the units of 1/°] and less than or equal to the product of the maximum engine torque [in the units of Nm] of the six-cylinder engine and the factor 0.158 [in the units of 1/°]. Put into an equation, this means: 
         [0000]      (M mot,max  [Nm]*0.035 [1/°]) ≦c 2 ≦(M mot,max  [Nm]*0.158 [1/°]), 
         [0000]    wherein M mot,max  [Nm] is the maximum engine torque of the combustion engine or of the six-cylinder engine of the drive train in the units of “Newton times meter” (Nm), and wherein c 2  is the spring constant of the second energy accumulator means in the units of “Newton times meter divided by degrees” (Nm/°). 
         [0012]    It is furthermore provided, that the motor vehicle drive train or the torque converter device or the torsion vibration damper is configured, so that the quotient, which on the one hand is formed by the sum of the spring constant of the first energy accumulator means [in the units of Newton meter per radian (Nm/rad)], and the spring constant of the second energy accumulator means [in the units of Nm/rad] and, on the other hand, by the first mass moment of inertia [in the units of kilogram meter squared (kg*m 2 )], is greater than or equal to 17765 N*m/(rad*kg*m 2 ), and less than or equal to 111033 N*m/(rad*kg*m 2 ). Thus, put into an equation it is provided: 
         [0000]      17765 N*m/(rad*kg*m 2 )≦(c 1 +c 2 )/J 1 ≦111033 N*m/(rad*kg*m 2 ), 
         [0000]    wherein c 1 =spring constant of the first energy accumulator means [in the units of Nm/rad], and wherein c 2 =spring constant of the second energy accumulator means [in the units of Nm/rad], and wherein J 1 =first mass moment of inertia [in the units of kg*m 2 ]. The abbreviation “rad” designates the radian measure. 
         [0013]    It is furthermore provided that the motor vehicle drive train or the torque converter device or the torsion vibration damper or the transmission input shaft are configured, so that the quotient, which is on the one hand formed by the sum of the spring constant of the second energy accumulator means [in the units of Nm/rad] and the spring constant of the transmission input shaft [in the units of Nm/rad] and on the other hand of the second mass moment of inertia [in the units of kg*m 2 ] is greater than or equal to 3158273 N*m/(rad*kg*m 2 ) and less than or equal to 12633094 N*m/(rad*kg*m 2 ). Thus, this reads as an equation: 
         [0000]      3158273 N*m/(rad*kg*m 2 )≦(C 2 +c GEW )/J 2 ≦12633094 N*m/(rad*kg*m 2 ), 
         [0000]    wherein c 2 =spring constant of the second energy accumulator means [in the units of Nm/rad] and c GEW =spring constant of the transmission input shaft [in the units of Nm/rad], and J 2 =the second mass moment of inertia [in the units of kg*m 2 ]. 
         [0014]    According to a preferred embodiment it is thus provided that the transmission input shaft is configured, so that the spring constant of the transmission input shaft is greater than or equal to 100 Nm/°, and less than or equal to 350 Nm/°. Thus, put into an equation the following applies preferably: 100 Nm/°≦c GEW ≦350 Nm/°, wherein c GEW =spring constant of the transmission input shaft [in the units of Nm/°]. The following applies in particular: 120 Nm/°≦c GEW ≦300 Nm/°. According to another preferred embodiment the following applies: 120 Nm/°≦c GEW ≦210 Nm/°. According to another preferred embodiment the following applies: 130 Nm/°≦c GEW ≦150 Nm/°. It is preferred in particular, that the spring constant c GEW  of the transmission input shaft is approximately in a range of 140 N*m/° or is 140 N*m/°. These values of the spring constant c GEW  of the transmission input shaft relate in particular to a torsion loading or to a torsion loading about the central longitudinal axis of the transmission input shaft, or the spring constant c GEW  of the transmission input shaft is the spring constant of the transmission input shaft, which is effective or present or occurs under a torsion loading or under a torsion loading about the central longitudinal axis of the transmission input shaft. The transmission input shaft is supported rotatably and thus about its central longitudinal axis or rotation axis. 
         [0015]    It is thus provided in particular that the torsion vibration damper is rotatable about a rotation axis of said torsion vibration damper. The rotation axis of the torsion vibration damper corresponds in an advantageous embodiment to the rotation axis of the transmission input shaft. 
         [0016]    Preferably, a second component, which is for example configured as a plate or as a flange, is provided, which is connected in series with the first energy accumulator means and the first component. Thus, it is provided in particular, that the first energy accumulator means is disposed between the second component and the first component, so that a torque is transferrable from the second component through the first energy accumulator means to the first component. The second component is thus preferably provided between the converter lockup clutch and the first energy accumulator means, so that, when the converter lockup clutch is closed, a torque transferred through the converter lockup clutch can be transferred through the second component to the first energy accumulator means. The converter lockup clutch can be connected to the converter housing non-rotatably, or in a solid manner, so that when the converter lockup clutch is closed, a torque from the converter housing can be transferred through the converter lockup clutch. The converter lockup clutch can for example be configured as multidisc clutch. Thus, it can for example comprise a press component or an axially movable and hydraulically loadable piston, by means of which the multidisc clutch can be closed. Thus it can for example be provided that the second component is the press component or the piston of the multidisc clutch or connected non-rotatably to the press component or the piston. 
         [0017]    The first component is a plate or a flange in a preferred embodiment. The third component is a plate or a flange in a preferred embodiment. The third component can form for example a hub or it can be coupled non-rotatably to a hub. This hub can for example be coupled non-rotatably to the transmission input shaft, or it can engage non-rotatably with the transmission input shaft. 
         [0018]    It is preferably provided that the second component or a component connected non-rotatably therewith forms an input component of the first energy accumulator means. It can be provided in particular, that the second component or a component coupled non-rotatably therewith, engages in particular on the input side with the first energy accumulators of the first energy accumulator means or engages with first face sides of the first energy accumulator means. It is provided in particular, that the first component or a component connected non-rotatably to said first component, and thus in particular on the output side, engages with the first energy accumulators of the first energy accumulator means, or with second front faces, which are different from the first front faces, of the first energy accumulators of the first energy accumulator means. It is furthermore provided in particular that the first component, or possibly an additional component, connected non-rotatably with the first component and in particular on the input side engages with the second energy accumulator of the second energy accumulator means, or with the first front faces of the second energy accumulators of the second energy accumulator means. Furthermore it is provided in particular that the third component or a component connected non-rotatably with the third component and in particular on the output side engages with the second energy accumulators of the second energy accumulator means, or engages with second front faces, which are different from the first front faces of the second energy accumulator means. 
         [0019]    According to a preferred embodiment, the first energy accumulator means comprises several first energy accumulators or is comprised of several first energy accumulators. The first energy accumulators are coil springs or arc springs according to a preferred embodiment. It can be provided that all of the first energy accumulators are connected in parallel. According to an improved embodiment, the or all first energy accumulators are disposed distributed, or offset, about the circumference with reference to the circumferential direction of the rotation axis of the torsion vibration damper. However, it can also be provided that several first energy accumulators are disposed distributed, or offset, about the circumference with reference to the circumferential direction of the rotation axis of the torsion vibration damper, wherein the energy accumulators, which are disposed distributed, or offset, about the circumference are configured as arc springs or as coil springs, and receive respectively one or several additional first energy accumulators in their interior. In an embodiment of the latter type, it can be provided that when loading the first energy accumulator means, gradually increasing the load from the unloaded state, initially only those first energy accumulators store energy, which receive one or several first energy accumulators in their interior and which store energy in the first energy accumulator, received in the interior, when the load on the first energy accumulator means is above a predetermined threshold load, or above a predetermined threshold torque, or vice versa. 
         [0020]    According to a preferred embodiment, the second energy accumulator means comprises several second energy accumulators, or it is comprised of several second energy accumulators. The second energy accumulators according to a preferred embodiment are coil springs or compression springs or straight springs. It can be provided that all the second energy accumulators are connected in parallel. According to an improved embodiment, the or all second energy accumulators are disposed distributed, or offset, about the circumference with reference to the circumferential direction of the rotation axis of the torsion vibration damper. However, it can also be provided that several second energy accumulators are disposed distributed, or offset, about the circumference with reference to the circumferential direction of the rotation axis of the torsion vibration damper, wherein the second energy accumulators which are disposed distributed, or offset, about the circumference are provided as compression springs or as straight springs or as coil springs and receive one or several additional second energy accumulators in their interior. In an embodiment of the latter type, it can be provided that under a loading, which gradually increases from the unloaded state of the second energy accumulator means, initially only those second energy accumulators accumulate energy, which receive one or several additional second energy accumulators in their interior, and the second energy accumulator received in the interior only store energy, when the loading of the second energy accumulator means is above a predetermined threshold loading or above a predetermined threshold torque or vice versa. 
         [0021]    Preferably, the first energy accumulators are disposed, or the first energy accumulator means is disposed radially outside of the second energy accumulators or of the second energy accumulator means. This relates in particular to the radial direction of the rotation axis of the torsion vibration damper. 
         [0022]    The spring constant of the first energy accumulator means is in particular the spring constant, or the combined spring constant, which is effective or given or occurs at torque loads of the first energy accumulator means and thus in particular under torque loads, which act about the rotation axis of the torsion vibration damper upon the first energy accumulator means. The spring constant of the first energy accumulator means is determined in particular by the spring constants of the first energy accumulators and their disposition and their connection. The spring constant of the first energy accumulator means is thus in particular a combined spring constant, which is determined by the spring constants of the first energy accumulators and their arrangement or their connection. As discussed, the first energy accumulators are connected in parallel in a preferred embodiment. However, it can also be provided for example that the first energy accumulators are connected, so that they basically form a parallel assembly, wherein first energy accumulators are connected in series in the parallel paths of this parallel assembly thus formed. 
         [0023]    The spring constant of the second energy accumulator means is in particular the spring constant or the combined spring constant, which is effective or given or occurs under torque loadings of the second energy accumulator means, and thus in particular under torque loadings, which impact the second energy accumulator means about the rotation axis of the torsion vibration damper. The spring constant of the second energy accumulator means is determined in particular by the spring constants of the second energy accumulators and their disposition or connection. The spring constant of the second energy accumulator means is thus in particular a combined spring constant, which is defined by the spring constants of the second energy accumulators and their disposition or their connection. As described, the second energy accumulators are connected in parallel in an advantageous embodiment. However, it can also be provided, for example, that second energy accumulators are connected, so that they basically form a parallel connection, wherein second energy accumulators are connected in series in the parallel paths of the parallel assembly. 
         [0024]    The first mass moment of inertia particularly relates to the rotation axis of the torsion vibration damper. The first component is for example a plate. It can be provided that the outer turbine dish is connected non-rotatably to the first component by means of one or more driver components. Thus, it is provided in particular that the mass moment of inertia of such driver component(s) determine(s) or co-determine(s) the first mass moment of inertia and thus in particular as a summand. It is provided in particular that the mass moments of inertia of the components, in particular of the first component, or of the component, through which a torque is transferred from the first energy accumulators of the first energy accumulator means to the to the second energy accumulators of the second energy accumulator means, or which are connected between the first energy accumulators of the first energy accumulator means and the second energy accumulators of the second energy accumulator means determine or co-determine the first mass moment of inertia. The mass moments of inertia respectively relate in particular to the rotation axis of the torsion vibration damper. 
         [0025]    The second mass moment of inertia relates to the rotation axis of the torsion vibration damper in particular. The third component is for example a plate. 
         [0026]    Preferably the motor vehicle drive train or the torque converter device or the torsion vibration damper or the first energy accumulator means are configured so that the following applies: 
         [0027]    (M mot,max  [Nm]*0.02 [1/°])≦c 1 ≦(M mot,max  [Nm]*0.06 [1/°]); or the following applies: 
         [0028]    (M mot,max  [Nm]*0.03 [1/°])≦c 1 ≦(M mot,max  [Nm]*0.05 [1/°]). 
         [0029]    Preferably the motor vehicle drive train or the torque converter device or the torsion vibration damper or the second energy accumulator means are configured so that the following applies: 
         [0030]    (M mot,max  [Nm]*0.04 [1/°])≦c 2 ≦(M mot,max  [Nm]*0.15 [1/°]); or the following applies: 
         [0031]    (M mot,max  [Nm]*0.05 [1/°])≦c 2 ≦(M mot,max  [Nm]*0.13 [1/°]); or the following applies: 
         [0032]    (M mot,max  [Nm]*0.06 [1/°])≦c 2 ≦(M mot,max  [Nm]*0.1 [1/°]). 
         [0033]    Preferably the motor vehicle drive train or the torque converter device or the torsion vibration damper is configured, so that the following applies: 
         [0034]    25000 N*m/(rad*kg*m 2 )≦(c 1 +c 2 )/J 1 ≦105000 N*m/(rad*kg*m 2 ); or so that the following applies: 
         [0035]    35000 N*m/(rad*kg*m 2 )≦(c 1 +c 2 )/J 1 ≦95000 N*m/(rad*kg*m 2 ); or so that the following applies: 
         [0036]    40000 N*m/(rad*kg*m 2 )≦(c 1 +c 2 )/J 1 ≦90000 N*m/(rad*kg*M 2 ). 
         [0037]    Preferably the motor vehicle drive train or the converter device or the torsion vibration damper or the transmission input shaft are configured, so that the following applies: 
         [0038]    3500000 N*m/(rad*kg*m 2 )≦(c 2 +c GEW )/J 2 ≦12000000 N*m/(rad*kg*m 2 ); or so that the following applies: 
         [0039]    4000000 N*m/(rad*kg*m 2 )≦(c 2 +c GEW )/J 2 ≦11000000 N*m/(rad*kg*m 2 ); or so that the following applies: 
         [0040]    4500000 N*m/(rad*kg*m 2 )≦(c 2 +c GEW )/J 2 ≦10500000 N*m/(rad*kg*m 2 ); or so that the following applies: 
         [0041]    5000000 N*m/(rad*kg*m 2 )≦(c 2 +c GEW )/J 2 ≦10000000 N*m/(rad*kg*m 2 ). 
         [0042]    These and other objects and advantages of the present invention will be readily appreciable from the following description of preferred embodiments of the invention and from the accompanying drawings and claims. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS  
         [0043]    The nature and mode of operation of the present invention will now be more fully described in the following detailed description of the invention taken with the accompanying drawing figures, in which: 
           [0044]      FIG. 1  is a schematic view of an exemplary motor vehicle drive train; 
           [0045]      FIG. 2  is a section of an exemplary motor vehicle drive train according to the invention, comprising a first exemplary hydrodynamic torque converter device; 
           [0046]      FIG. 3  is a section of an exemplary motor vehicle drive train according to the invention comprising a second exemplary hydrodynamic torque converter device; 
           [0047]      FIG. 4  is a section of an exemplary motor vehicle drive train comprising a third hydrodynamic torque converter device; and, 
           [0048]      FIG. 5  is a spring rotating mass schematic of a section of an exemplary motor vehicle drive train for the case of the closed converter lockup clutch. 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION  
       [0049]    At the outset, it should be appreciated that like drawing numbers on different drawing views identify identical, or functionally similar, structural elements of the invention. While the present invention is described with respect to what is presently considered to be the preferred aspects, it is to be understood that the invention as claimed is not limited to the disclosed aspects. 
         [0050]    Furthermore, it is understood that this invention is not limited to the particular methodology, materials and modifications described and as such may, of course, vary. It is also understood that the terminology used herein is for the purpose of describing particular aspects only, and is not intended to limit the scope of the present invention, which is limited only by the appended claims. 
         [0051]    Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood to one of ordinary skill in the art to which this invention belongs. Although any methods, devices or materials similar or equivalent to those described herein can be used in the practice or testing of the invention, the preferred methods, devices, and materials are now described. 
         [0052]      FIG. 1  shows an exemplary motor vehicle drive train  2  according to the invention in a schematic illustration. Motor vehicle drive train  2  comprises combustion engine  250  and drive shaft or engine output shaft or crank shaft  18 , which can be driven by combustion engine  250  in a rotating manner. Combustion engine  250  comprises exactly six cylinders  252 , or it is six-cylinder engine  250 . Six-cylinder engine  250  comprises a maximum engine torque M mot,max , or it can impart a maximum torque into drive train  2 , which corresponds to the maximum engine torque M mot,max . 
         [0053]    Motor vehicle drive train  2  comprises hydrodynamic torque converter device  1 , which is configured according to one of the embodiments, which are described with reference to  FIGS. 2 through 4 . 
         [0054]    Motor vehicle drive train  2  furthermore comprises transmission  254 , which is for example an automatic transmission. Furthermore, motor vehicle drive train  2  can comprise transmission output shaft  256 , differential  258  and one or several drive axles  260 . Motor vehicle drive train  2  furthermore comprises transmission input shaft  66  between torque converter device  1  and transmission  254 . Torque converter device  1 , or a component like hub  64  of torque converter device  1  is connected non-rotatably to transmission input shaft  66 . Engine output shaft or crank shaft  18  is coupled non-rotatably to converter housing  16  of torque converter device  1 . Thus a torque can be transferred from drive shaft or engine output shaft or crank shaft  18  through torque converter device  1  to transmission input shaft  66 . 
         [0055]      FIGS. 2 through 4  show various exemplary hydrodynamic torque converter devices  1 , which can be provided in an exemplary motor vehicle drive train  2  according to the invention, or in motor vehicle drive train  2 , shown in  FIG. 1 . 
         [0056]    The embodiments illustrated in  FIGS. 2 through 4  are components of an exemplary motor vehicle drive train  2  according to the invention, which comprises six-cylinder engine  250 , which is not shown in  FIGS. 2 through 4 , or combustion engine  250 , which is not shown in  FIGS. 2 through 4 , which is configured as a six-cylinder engine and thus comprises three cylinders  252 . Hydrodynamic torque converter device  1  comprises torsion vibration damper  10  and converter torus  12  formed by pump shell  20 , turbine shell  24  and stator shell  22 , and comprises converter lockup clutch  14 . 
         [0057]    Torsion vibration damper  10 , converter torus  12 , and converter lockup clutch  14  are received in converter housing  16 . Converter housing  16  is connected substantially non-rotatably to drive shaft  18 , which is in particular the crank shaft or the engine output shaft of a combustion engine. 
         [0058]    As discussed, converter torus  12  comprises pump or pump shell  20 , stator shell  22  and turbine or turbine shell  24 , which interact in a known manner. In a known manner, converter torus  12  comprises converter torus cavity or torus interior  28 , which is provided for receiving oil or for an oil flow. Turbine shell  24  comprises outer turbine dish  26 , which forms wall section  30 , which directly abuts to torus interior  28  and which is provided for defining torus interior  28 . Furthermore, turbine shell  24  comprises inner turbine dish  262  and turbine blades in a known manner. Extension  32  of outer turbine dish  26  connects to wall section  30  directly abutting to torus interior  28 . Extension  32  comprises straight or annular section  34 . Straight or annular section  34  of extension  32  can for example be configured, so that it is substantially straight in a radial direction of rotation axis  36  of torsion vibration damper  10 , and disposed in particular as an annular section in a plane disposed perpendicular to rotation axis  36 , or so that it defines said plane. 
         [0059]    Torsion vibration damper  10  comprises first energy accumulator means  38  and second energy accumulator means  40 . First energy accumulator means  38  and second energy accumulator means  40  are spring means in particular. 
         [0060]    In the embodiments shown in  FIGS. 2 through 4 , it is provided that first energy accumulator means  38  comprises several first energy accumulators  42 , or that it is comprised of the energy accumulators, for example, coil springs or arc springs, offset from one another in a circumferential direction extending about rotation axis  36 . It can be provided that all first energy accumulators  42  are configured identically. It can also be provided that differently configured first energy accumulators  42  are provided. 
         [0061]    The spring constant c 1  [in the units of Nm/°] of first energy accumulator means  38  is greater than or equal to the product of the maximum engine torque M mot,max  [in the units of Nm] of six-cylinder engine  250  and the factor 0.014 [in the units of 1/°] and less than or equal to the product of the maximum engine torque [in the units of Nm] of six-cylinder engine  250  and the factor 0.068 [in the units of 1/°]. Thus, the following applies: 
         [0062]    (M mot,max  [Nm]*0.014 [1/°])≦c 1 ≦(M mot,max  [Nm]*0.068 [1/°]), wherein M mot,max  [Nm] is the maximum engine torque of the combustion engine or of six-cylinder engine  250  of drive train  2  in the units of “Newton times meter” (Nm), and wherein c 1  is the spring constant of first energy accumulator means  38  in the units of “Newton meter divided by degrees” (Nm/°). The values or ranges however can be also disposed as described supra and infra. 
         [0063]    Second energy accumulator means  40  comprises plural second energy accumulators  44 , respectively configured as coil springs or compression springs or straight springs, or it is formed by second energy accumulators  44 . Thus, in a preferred embodiment, several second energy accumulators  44  are disposed offset from one another relative to the circumferential direction of the rotation axis. It can be provided that second energy accumulators  44  are respectively configured identical. Different second energy accumulators  44  however can also be configured differently. 
         [0064]    The spring constant c 2  [in the units of Nm/°] of second energy accumulator means  40  is greater than or equal to the product of the maximum engine torque M mot,max  [in the units of Nm] of six-cylinder engine  250  and the factor 0.035 [in the units of 1/°] and less than or equal to the product of the maximum engine torque M mot,max  [in the units of Nm] of six-cylinder engine  250  and the factor 0.158 [in the units of 1/°]. Thus, the following applies: 
         [0065]    (M mot,max  [Nm]*0.035 [1/°])≦c 2 ≦(M mot,max  [Nm]*0.158 [1/°]), wherein M mot,max  [Nm] is the maximum engine torque of the combustion engine or six-cylinder engine  250  of drive train  2  in the units of “Newton times meter” (Nm), and wherein c 2  is the spring constant of the second energy accumulator means in the units of “Newton times meter divided by degrees” (Nm/°). The values or ranges however can be also disposed as described supra and infra. 
         [0066]    According to the embodiments shown in  FIGS. 2 through 4 , second energy accumulator means  40  is disposed with reference to the radial direction of rotation axis  36  radially within first energy accumulator means  38 . First energy accumulator means  38  and second energy accumulator means  40  are connected in series. Torsion vibration damper  10  comprises first component  46 , which is disposed between first energy accumulator means  38  and second energy accumulator means  40 , or connected in series with energy accumulator means  38  and  40 . It is also provided in particular for example when lockup clutch  14  is closed, that a torque can be transferred from first energy accumulator means  38  through first component  46  to second energy accumulator means  40 . First component  46  can also be designated as intermediary component  46 , which is also done infra. 
         [0067]    It is provided in the embodiments shown in  FIGS. 2 through 4 , that outer turbine dish  26  is connected to intermediary component  46 , so that a load, in particular torque and/or force, can be transferred from outer turbine dish  26  to intermediary component  46 . 
         [0068]    Between outer turbine dish  26  and intermediary component  46 , or in the load flow, in particular in the torque or force flow between outer turbine dish  26  and intermediary component  46 , driver component  50  is provided. It can also be provided that extension  32  also forms intermediary component  46  and/or driver component  50 , or takes over their function. It can also be provided that driver component  50  forms a first component or an intermediary component, which is connected in series in the torque flow between energy accumulator means  38  and  40 . It is furthermore provided that along load transfer path  48 , through which a load or a torque can be transferred from outer turbine dish  26  to intermediary component  46 , at least one connection means  52 ,  56  or  54  is provided. Such a connection means  52 ,  56 , or  54  can for example be a plug-in connection or a rivet connection, or a bolt connection (see reference numeral  56  in  FIGS. 2 through 4 ) or a weld (see reference numeral  52  in  FIGS. 2 through 4 ) or similar structure. It is appreciated that in  FIG. 4  at the location, where weld  52  is provided, an additional rivet or bolt connection  52  is drawn, in order to show an alternative configuration. This is also intended to clarify that the connection means can also be configured differently or can be combined differently. By respective connection means  52 ,  54 , and  56 , respective adjoining components of load transfer path  48 , through which the load can be transferred from outer turbine dish  26  to intermediary component  46 , are coupled amongst one another. Thus, extension  32  of outer turbine dish  26  is coupled in the embodiments shown in  FIGS. 2 through 4  with driver component  50  respectively non-rotatable by connection means  52  configured as a weld (which can also alternatively be a rivet or bolt connection according to  FIG. 4 ) and driver component  50  is coupled torque proof to intermediary component  46  through connection means  56 , respectively configured as a rivet or bolt connection. 
         [0069]    It is provided that all connection means  52 ,  54  and  56 , by which components adjoining along load transfer path  48  between outer turbine dish  26  and intermediary component  46 , for example, extension  32  and driver component  50  or driver component  50  and intermediary component  46 , are connected, are offset from wall section  30  of outer turbine dish  26  directly adjoining to torus interior  28 . This facilitates at least according to the embodiments, that the bandwidth of possible connection means is increased. Thus it is possible for example that not only thin plate- or MAG- or Laser- or dot welding is used as welding method, but also for example friction welding. 
         [0070]    Second component  60  and third component  62  are connected in series with first energy accumulator means  38 , second energy accumulator means  40  and intermediary component  46  provided between two energy accumulator means  38  and  40 . Second component  60  forms an input component of first energy accumulator means  38  and third component  62  forms an output component of second energy accumulator means  40 . A load or a torque transferred by second component  60  into first energy accumulator means  38  can thus be transferred on the output side of first energy accumulator means  38  through intermediary component  46  and second energy accumulator means  40  to third component  62 . 
         [0071]    Third component  62  engages hub  64 , forming a non-rotatable connection, which is in turn coupled non-rotatably to output shaft  66  of torque converter device  1 , which is for example transmission input shaft  66  of a motor vehicle transmission. Alternatively it can however also be provided that third component  62  forms hub  64 . Outer turbine dish  26  is radially supported at hub  64  by means of support section  68 . Support section  68 , which is in particular radially supported at hub  64 , is substantially configured sleeve shaped. 
         [0072]    It is appreciated that the radial support of outer turbine dish  26  by means of support section  68  is configured, so that support forces acting upon outer turbine dish  26  through the radial support are not conducted through first or second energy accumulator means  38  and  40 , respectively, from support section  68  to outer turbine dish  26 . Support section  68  is rotatable relative to hub  64 . It can be provided, that a straight bearing or a straight bearing bushing, or a roller bearing, or similar is provided for radial support between hub  64  and support section  68 . Furthermore, respective bearings can be provided for axial support. The connection already discussed supra between outer turbine dish  26  and intermediary component  46  is configured, so that a torque, which is transferrable from outer turbine dish  26  to intermediary component  46 , can be transferred without one of energy accumulator means  38  or  40  being provided along the respective load transfer path  48 . The torque transfer from outer turbine dish  26  to intermediary component  46  through load transfer path  48  can thus be provided in particular by means of a substantially rigid connection. 
         [0073]    In the embodiments shown in  FIGS. 2 through 4 , two respective connection means are provided along load or force or torque transfer path  48  between outer turbine dish  26  and intermediary component  46 , and thus first connection means  52  or  54  and second connection means  56 . It is appreciated that with reference to the circumferential direction of rotation axis  36 , distributed in circumferential direction, several distributed first connection means  52  or second connection means  56  can be provided or can preferably be provided. First connection means  52  or  54  (subsequently “first connection means  52 ” is referred to for purposes of simplification) connect non-rotatably extension  32  to driver component  50  and second connection mean(s)  56  (subsequently referred to as second connection means  54  for purposes of simplification) connect non-rotatably driver component  50  to intermediary component  46 . 
         [0074]    As illustrated in  FIGS. 2 through 4 , sleeve shaped support portion  68  can for example be a radially inner section of driver component  50  with reference to the radial direction of rotation axis  36 . 
         [0075]    Converter lockup clutch  14  is provided in the embodiments shown in  FIGS. 2 through 4  as a respective multidisc clutch and comprises first disk carrier  72 , by which first disks  74  are received non-rotatably, and second disk carrier  76  by which second disks  78  are received non-rotatably. When multidisc clutch  14  is open, first disk carrier  72  is movable relative to second disk carrier  76  and thus so that first disk carrier  72  is rotatable relative to second disk carrier  76 . Second disk carrier  76  is disposed with reference to the radial direction of axis  36  radially within first disk carrier  72 , however, also the opposite can be the case. First disk carrier  72  is connected to converter housing  16 . For actuation, multidisc clutch  14  comprises piston  80 , which is disposed axially movable and which can be loaded for example hydraulically for actuating multidisc clutch  14 . Piston  80  is connected in a rigid manner or non-rotatably to second disk carrier  76 , which can be effectuated for example by means of a welded connection. First disks  74  and second disks  78  alternate viewed in the longitudinal direction of rotation axis  36 . When loading disk packet  79  formed by first disks  74  and second disks  78 , by means of piston  80 , disk packet  79  is supported on the side of disk packet  79  opposite to piston  80  at a section of the inside of converter housing  16 . Between adjacent disks  74  and  78  and at both ends of disk packet  79 , friction liners  81  are provided, which are for example held at disks  74  and/or  78 . Friction liners  81  which are provided at the ends of disk packet  79 , can also be supported on the one side and/or the other side also at the inside of converter housing  16  or at piston  80 . 
         [0076]    In the embodiments shown in  FIGS. 2 and 3 , piston  80  is integrally formed with second component  60 , thus the input component of first energy accumulator means  38 . In the embodiment shown in  FIG. 4 , piston  80  is connected non-rotatably or fixated to second component  60  or the input component of first energy accumulator means  38 , wherein the fixation is performed is here for example by a weld. As a matter of principle a non-rotatable connection can also be performed in another manner. In the embodiments shown in  FIGS. 2 and 3 , in an alternative embodiment, piston  80  and input component  60  of first energy accumulator means  38  can also be provided as separate components connected amongst one another in a fixated or non-rotatable manner for example by a weld or a rivet or a bolt. In the embodiment shown in  FIG. 4 , also another suitable connection can be provided between piston  80  and input component  60  instead of a weld, in order to generate the solid or non-rotatable connection, for example, a bolt or rivet joint or a plug-in connection or alternatively, piston  80  with input component  60  can also be manufactured integrally from one piece. 
         [0077]    Piston  80  or second component  60 , the first component, or intermediary component  46 , driver component  50  and third component  62  are respectively formed by plates. Second component  60  is a flange in particular. First component  46  is a flange in particular. Third component  62  is a flange in particular. 
         [0078]    In the embodiment shown in  FIG. 3 , the plate thickness of driver component  50  is greater than the plate thickness of piston  80 , or of input component  60  of first energy accumulator means  38 . Furthermore it can be provided in the embodiments shown in FIGS.  2  through  4 , that the mass moment of inertia of driver component  50  is greater than the mass moment of inertia of piston  80  or of input component  60  or of the unit made of components  60  and  80 . 
         [0079]    For first energy accumulators  42 , a respective type of housing  82  is formed, which extends with reference to the radial direction and to the axial direction of rotation axis  36  at least partially on both sides axially and radially on the outside about first energy accumulator  42 . In the embodiments shown in  FIGS. 2 through 4 , the housing is disposed at driver component  50 . In most embodiments the non-rotatable disposition at driver component  50  or at the outer turbine dish is more advantageous from a vibration point of view, than for example a torque proof disposition at second component  60 . Housing  82  in this case comprises cover  264 , which is for example welded on. 
         [0080]    In the embodiment shown in  FIG. 4 , first energy accumulators  42  can be supported at housing  82  for friction reduction by a respective means  84  comprising roller bodies like balls or rollers, which can also be designated as a roller shoe. Though this is not shown in  FIGS. 2 and 3 , such a device  84 , comprising roller bodies like balls or rollers for supporting first energy accumulators  42  or for friction reduction can also be accordingly provided in the embodiments shown in  FIGS. 2 and 3 . According to  FIGS. 2 and 3 , however, slider dish or slider shoe  94  is provided here instead of roller shoe  84  for the low friction support of first energy accumulators  42 . 
         [0081]    Furthermore, second rotation angle limiter means  92  is provided for second energy accumulator means  40  in the embodiments shown in  FIGS. 2 through 4 , by which the maximum rotation angle or the relative rotation angle of second energy accumulator means  40  or of the input component of second energy accumulator means  40  relative to the output component of second energy accumulator means  40  is limited. This is performed here, so that the maximum rotation angle of second energy accumulator means  40  is limited by second rotation angle limiter means  92 , so that it is avoided that second energy accumulators  44 , which are springs in particular, go into blockage under a respectively high torque loading. Second rotation angle limiter means  92  is configured as shown in  FIGS. 2 through 4  for example, so that driver component  50  and intermediary component  46  are connected non-rotatably by a bolt, which is in particular a component of connection means  56 , wherein the bolt extends through a slotted hole, which is provided in the output component of second energy accumulator means  40  or in third component  62 . A first rotation angle limiter means can also be provided for first energy accumulator means  38 , which is not shown in the figures, by which the maximum rotation angle of first energy accumulator means  38  is limited, so that a blockage loading of first energy accumulators  42 , which are in particular provided as respective springs, is avoided. In particular when, which is advantageously the case, second energy accumulators  44  are straight compression springs and first energy accumulators  42  are arc springs, it can be provided as illustrated in  FIGS. 2 through 4  that only a second rotation angle limiter means is provided for second energy accumulator means  40 , since in such configurations in case of a blockage loading the risk of damaging the arc springs is lower than in case of straight springs and an additional first rotation angle limiter means will increase the number of components or the manufacturing cost. 
         [0082]    In a particularly advantageous embodiment, it is provided in the configurations shown in  FIGS. 2 through 4 , that the rotation angle of first energy accumulator means  38  is limited to a maximum first rotation angle and the rotation angle of second energy accumulator means  40  is limited to a maximum second rotation angle, wherein first energy accumulator means  38  reaches its maximum first rotation angle, when a first threshold torque is applied to first energy accumulator means  38 , and wherein second energy accumulator means  40  reaches its second maximum rotation angle, when a second threshold torque is applied to second energy accumulator means  40 , wherein the first threshold torque is less than the second threshold torque. This can be performed in particular by a respective setting of the two energy accumulator means  38  and  40  or of energy accumulators  42  and  44  of the two energy accumulator means  38  and  40 , respectively, possibly or in particular also by the first and/or second rotation angle limiter means. It can be provided that first energy accumulators  42  go into blockage under the first threshold torque, so that first energy accumulator means  38  reaches its maximum first rotation angle, and it is caused by a second rotation angle limiter means for second energy accumulator means  40 , that second energy accumulator means  40  reaches its maximum second rotation angle at a second threshold torque, wherein the maximum second rotation angle is reached, when the second rotation angle limiter means reaches a stop position. 
         [0083]    This way, a particularly good setting for partial load operations can be reached. 
         [0084]    It is appreciated that the rotation angle of first energy accumulator means  38  or of second energy accumulator means  40 , and this applies accordingly to the maximum first or maximum second rotation angle, are thus the relative rotation angle with reference to rotation axis  36  of torsion vibration damper  10 , which is given relative to the unloaded resting position between components adjoining one another on the input side and on the output side for a torque transfer respectively directly to the respective components adjoining energy accumulator means  38  or  40 . The rotation angle, which is limited in particular in said manner by the respective maximum first or second rotation angle, can change in particular by energy accumulator  42  or  44  of the respective energy accumulator means  38  or  40  absorbing energy or releasing stored energy. 
         [0085]    In converter torus  12  and also outside of converter torus  12  within converter housing  16 , oil is included in particular. 
         [0086]    In the embodiments shown in  FIGS. 2 through 4 , piston  80 , or the second component, or input component  60  of first energy accumulator means  38  form several lugs  86 , distributed about the circumference, each comprising non-free end  88  and free end  90 , and which are provided for a face side, input side loading of the respective first energy accumulator  42 . Non-free end  88  is thus disposed with reference to the radial direction of rotation axis  36  radially within free end  90  of the respective lug  86 . 
         [0087]    As shown in  FIGS. 2 through 4 , the radial extension of driver component  50  can be greater than the center radial distance of first energy accumulator(s)  42  from second energy accumulator(s)  44 . 
         [0088]    In the embodiments shown in  FIGS. 2 through 4 , it is respectively provided that transmission input shaft  66  is configured, so that the spring constant c GEW  of transmission input shaft  66  is in the range of 100 Nm/° to 350 Nm/°. The value ranges can however also be selected, as it is described supra and infra. The spring constant c GEW  of transmission input shaft  66  is thus in particular the one, which is effective, when transmission input shaft  66  is torsion loaded about its central longitudinal axis. 
         [0089]    When transmitting a torque through first component  46 , a first mass moment of inertia J 1  counteracts the torque transferred through first component  46 . When transmitting a torque through third component  62 , a second mass moment of inertia J 2  acts against a change of the torque transmitted through third component  62 . 
         [0090]    In the embodiments shown in  FIGS. 2 through 4 , it is respectively provided that motor vehicle drive train  2 , or torque converter device  1 , or torsion vibration damper  10  are configured, so that the quotient which is formed on the one hand from the sum (c 1 +c 2 ) of the spring constant c 1  of first energy accumulator means  38  [in the units of Nm/rad] and the spring constant c 2  of second energy accumulator means  40  [in the units of Nm/rad] and on the other hand of the first mass moment of inertia J 1  [in the units of kg*m 2 ], is greater than or equal to 17765 N*m/(rad*kg*m 2 ) and less than or equal to 111033 N*m/(rad*kg*m 2 ). Thus, put into an equation, the following applies: 
         [0000]      17765 N*m/(rad*kg*m 2 )≦(c 1 +c 2 )/J 1 ≦111033 N*m/(rad*kg*m 2 ), 
         [0000]    wherein c 1  is the spring constant of first energy accumulator means  38  [in the units of Nm/rad] and wherein c 2  is the spring constant of second energy accumulator means  40  [in the units of Nm/rad] and wherein J 1  is the first mass moment of inertia [in the units of kg*m 2 ]. The values or ranges however can be set in a manner as it is described supra and infra. 
         [0091]    In the embodiments shown in the  FIGS. 2 through 4 , it is furthermore respectively provided that motor vehicle drive train  2 , or torque converter device  1  or torsion vibration damper  10  are configured, so that the quotient, which is formed on the one hand from the sum (c 1 +c GEW ) of the spring constant c 2  of second energy accumulator means  40  [in the units of Nm/rad] and the spring constant c GEW  of transmission input shaft  66  [in the units of Nm/rad] and on the other hand of the second mass moment of inertia J 2  [in the units of kg*m 2 ], is greater than or equal to 3158273 N*m/(rad*kg*m 2 ) and less than or equal to 12633094 N*m/(rad*kg*m 2 ). Thus, put into an equation, the following applies: 3158273 N*m/(rad*kg*m 2 )≦(c 2 +c GEW )/J 2 ≦12633094 N*m/(rad*kg*m 2 ), wherein c 2  is the spring constant of second energy accumulator means  40  [in the units of Nm/rad] and wherein c GEW  is the spring constant of transmission input shaft  66  [in the units of Nm/rad], and wherein J 2  is the second mass moment of inertia [in the units of kg*m 2 ]. The values or ranges however, can be comprised in a manner as it is described supra and infra. 
         [0092]    In the embodiments shown in  FIGS. 2 through 4  in particular, it can be provide that the first mass moment of inertia J 1  is substantially comprised of the mass moments of inertia of the following components: outer turbine dish  26  with extension  32 , inner turbine dish  262 , turbine blades or blading of the turbine or of turbine shell  24 , driver component  50  with housing  82  and housing cover  264 , first component  46 , first connection means  52  or  54 , second connection means  56 , slider dish(es)  94  or roller shoes  82 , possibly a portion of arc springs  42 , possibly a portion of compression springs  44 , possibly a portion of the oil, or oil, which is included in the arc spring channel(s), and possibly a portion of the oil, or oil with reference to the turbines, or oil, which is in the turbine. The mass moments of inertia thus particularly relate to rotation axis  36 . 
         [0093]    Furthermore it can be provided in the embodiments shown in  FIGS. 2 through 4 , that the second mass moment of inertia J 2  is substantially comprised of the mass moments of inertia of the following components: flange or third component  62 , hub  64 , which furthermore can also be integrally provided with flange  62 , and possibly a portion of transmission input shaft  66  and possibly a portion of compression springs  44  and possibly a non-illustrated diaphragm spring for a controlled hysteresis, and possibly shaft retaining rings and/or seal elements. 
         [0094]      FIG. 5  shows a spring/rotating mass schematic of a component of an exemplary motor vehicle drive train  2  according to the invention, or of the embodiment shown in  FIG. 1 , comprising a configuration shown in  FIG. 2  or  3 , or shown in  FIG. 4  in case the converter lockup clutch is closed. 
         [0095]    The system can be considered in particular in an ideal manner as a series connection comprising first engine side rotating mass  266 , clutch  268 , second rotating mass  270 , connected at the input side of first spring  272  between clutch  268 , first spring  272 , third rotating mass  274 , connected between first spring  272  and second spring  276 , second spring  276 , fourth rotating mass  278 , connected between second spring  276  and third spring  280 , and third spring  280 . 
         [0096]    The section formed by the series connection of first spring  272 , third rotating mass  274 , second spring  276 , fourth rotating mass  278  and third spring  280  thus forms from an ideal point of view a spring/rotating mass diagram for first energy accumulator means  38 , the connection of first energy accumulator means  38  and second energy accumulator means  40 , second energy accumulator means  40 , the connection of second energy accumulator means  40  to transmission input shaft  66  and transmission input shaft  66 . 
         [0097]    Subsequently, an exemplary improvement of the exemplary embodiments, advantages and effects according to the invention described supra based on the figures, shall be described, which can be provided at least in an improved embodiment of the invention. 
         [0098]    Quite frequently good or optimum insulation properties will be required, when the lockup clutch is completely closed in order to reach a lower or minimum fuel consumption or CO 2  output. It can thus be desirable that the goal is accomplished within a predetermined partial load range, in which the combustion engine is mostly operated. The insulation required for good sound and vibration comfort can be additionally accomplished under high loads, which do not occur that often and under full load, by means of an additional slipping lockup clutch. 
         [0099]    Torque converter device  1  or torque converter  1  comprising torsion vibration damper or energy accumulator devices  38  or  40 , respectively, constitutes a torsion vibration system in combination with engine  250  and drive train  2  of the vehicle. The natural modes of the torsion vibration system are induced due to the variations of the rotation of combustion engine  250 . Each natural mode of the system comprises an associated natural frequency. When said natural frequency coincides with the frequency of rotation of the combustion engine  250 , the system vibrates in resonance, this means at maximum amplitude. It is often useful to avoid high amplitudes, since they can cause disturbing vibrations and noises. The natural frequencies of the system depend on the torsion stiffnesses and rotating masses in the system. Therefore, the major components are in particular configured, so that between torsion dampers or energy accumulator means  38  or  40 , respectively, a large mass is created, or a large mass moment of inertia. On the other hand the major components between the lockup clutch and the torsion vibration damper, and those between torsion vibration damper and transmission input shaft are configured, so that the smallest masses possible are created in this location. The natural frequencies of the system are thereby excited to a lesser extent in the operating range of combustion engine  250 . The insulation due to the support of the damper is performed between the primary side and the secondary side (=&gt;turbine against the increased mass moment of inertia). 
         [0100]    Through the arrangement of the double damper or of the torsion vibration damper, an improved insulation is accomplished at low speeds, when the clutch is closed through the low to medium stiffnesses of the outward positioned damper, or of the first energy accumulator means and of the inner damper, connected in series, or of the second energy accumulator means. 
         [0101]    At higher speeds, increased friction can lead to an increased stiffness of the outer damper or of first energy accumulator means  38 . Herein, the inner damper connected in series, or second energy accumulator means  40  (in particular without friction), leads to more advantageous vibration characteristics in the upper speed range. 
         [0102]    A significant improvement of the double damper or of the torsion vibration damper is performed by the configuration of a torsion vibration damper or an energy accumulator means especially for partial load operation (lower torque), so that a very low spring stiffness of the torsion vibration damper or of the energy accumulator means can be realized in the range. Hereby, the reactive forces between the elastic element and the housing (dish) become smaller, furthermore, the mass of the spring element is smaller and thereby generates less centrifugal force and less friction relative to the housing (dish). This improves insulation. Through this measure, controlled two-mass inertia characteristics of the converter housing relative to the turbine are achieved. 
         [0103]    Through the use of a sliding support or roller body support (slider shoe/ball screw shoe or roller shoe), the friction of the exterior elastic element, or of first energy accumulators  42  over the complete speed range is reduced. Thereby an additional improvement of the insulation is accomplished in combination with the inner damper connected in series and second energy accumulator means  40 . 
         [0104]    Thus, it is seen that the objects of the present invention are efficiently obtained, although modifications and changes to the invention should be readily apparent to those having ordinary skill in the art, which modifications are intended to be within the spirit and scope of the invention as claimed. It also is understood that the foregoing description is illustrative of the present invention and should not be considered as limiting. Therefore, other embodiments of the present invention are possible without departing from the spirit and scope of the present invention. 
       DESIGNATIONS 
       [0000]    
       
           1  hydrodynamic torque converter device 
           2  motor vehicle drive train 
           10  torsion vibration damper 
           12  converter torus 
           14  converter lockup clutch 
           16  converter housing 
           18  drive shaft like engine output shaft of a combustion engine 
           20  pump or pump shell 
           22  stator shell 
           24  turbine or turbine shell 
           26  outer turbine shell 
           28  torus interior 
           30  wall section of  26   
           32  extension at  30  of  26   
           34  straight section of  32  or annular disk shaped section of  32   
           36  rotation axis of  10   
           38  first energy accumulator means 
           40  second energy accumulator means 
           42  first energy accumulator 
           44  second energy accumulator 
           46  first component of  10   
           48  load transfer path 
           50  driver component 
           52  connection means or welded connection between  32  and  50  in  48   
           54  connection means or bolt or rivet connection between  32  and  50  in  48   
           56  connection means or bolt or rivet connection between  50  and  46  in  48   
           60  second component 
           62  third component 
           64  hub 
           66  output shaft, transmission input shaft 
           68  support section 
           72  first disk carrier of  14   
           74  first disk of  14   
           76  second disk carrier of  14   
           78  second disk of  14   
           79  disk packet of  14   
           80  piston for actuating  14   
           81  friction liner of  14   
           82  housing 
           84  roller shoe 
           86  lug 
           88  non-free end of  82   
           90  free end of  82   
           92  second rotation angle limiter means  92  of  40   
           94  slider shoe 
           250  combustion engine, six-cylinder engine 
           252  cylinder of  250   
           254  transmission 
           256  transmission output shaft 
           258  differential 
           260  drive axle 
           262  inner turbine dish 
           264  cover 
           266  engine side rotating mass, first rotating mass 
           268  clutch 
           270  rotating mass of the connection, second rotating mass 
           272  first spring 
           274  rotating mass of the connection between  272  and  276 , third rotating mass 
           276  second spring 
           278  rotating mass of the connection between  276  and  280 , fourth rotating mass 
           280  third spring