Abstract:
The invention relates to an automotive drive train having an internal combustion engine ( 266 ) that is configured as a three-cylinder engine and a hydrodynamic torque converter device. Said device has a torsional vibration damper consisting of two energy accumulating devices ( 272, 276 ) and a converter lockup clutch ( 268 ). The turbine wheel ( 274 ) is interposed between the two energy accumulating devices ( 272, 276 ). According to the invention, ranges of values or ratios for the following parameters are claimed: maximum engine torque M mot,max  ( 266 ), spring rate c 1  ( 272 ), mass moment of inertia J 1  ( 274 ), spring rate c 2  ( 276 ), mass moment of inertia J 2  ( 278 ) and spring rate c GEW  of the transmission input shaft ( 280 ). The mass moment of inertia J 1  should be high between the two energy accumulating devices ( 272, 276 ) and masses should be as little as possible between the torsional vibration damper and the transmission input shaft. FIG.  5  shows a spring-mass equivalent circuit diagram with closed converter lockup clutch ( 268 ).

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is the National Stage of PCT International Application No. PCT/DE2006/001872, filed Oct. 21, 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 053 606.9, 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 three-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 two 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 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 according to FIGS. 1, 4 and 5 of DE 103 58 901 A1, furthermore between a first and a second energy accumulator means of the torsion vibration damper, a first component is apparently provided, which 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 three-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 three-cylinder engine or a combustion engine configured as a three-cylinder engine. The combustion engine or said three-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 plural first energy accumulators, or it is formed by one or plural first energy accumulators, and the second energy accumulator means comprises one or plural second accumulators, or it is formed by one or plural second accumulators. Between the first and second energy accumulator means, a first component is provided, which is connected in series with said 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 a “hydrodynamic torque converter”. In prior applications, 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, e.g., 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 non-rotatably coupled. 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 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, e.g., be non-rotatable couplings, in particular with reference to a rotation about the rotation axis of the torsion vibration damper. It was discussed supra, that the first mass moment of inertia during the transmission of a torque through the first component counteracts a change of said 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 said 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 said third component changes. Such couplings can, e.g., be non-rotatable couplings, in particular with reference to a rotation about the rotation axis of the torsion vibration damper. Previously it was discussed 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 unit of Nm/°] of the first energy accumulator means is greater than or equal to the product of the maximum engine torque [in the unit Nm] of the three-cylinder engine and the factor of 0.014 [1/°] and less than or equal to the product of the maximum engine torque [in the unit Nm] of the three-cylinder engine and the factor 0.068 [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 three-cylinder engine of the drive train in the unit “Newton times meter” (Nm), and wherein c 1  is the spring constant of the first energy accumulator means in the unit “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 unit Nm/°] of the second energy accumulator means is greater than or equal to the product of maximum engine torque [in the unit Nm] of the three-cylinder engine and the factor 0.035 [1/°] and smaller than or equal to the product of the maximum engine torque [in the unit Nm] of the three-cylinder engine and the factor 0.158 [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 three-cylinder engine of the drive train in the unit “Newton times meter” (Nm), and wherein c 2  is the spring constant of the second energy accumulator means in the unit “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 unit Nm/rad], and the spring constant of the second energy accumulator means [in the unit Nm/rad] and, on the other hand, by the first mass moment of inertia [in the unit of kg*m 2 ], is greater than or equal to 9993 N*m/(rad*kg*m 2 ), and less than or equal to 27758 N*m/(rad*kg*m 2 ). Thus, put into an equation it is provided: 
         [0000]      9993 N*m /(rad*kg*m 2 )≦( c   1   +c   2 )/ J   1 ≦27758 N*m /(rad*kg*m 2 ), 
         [0000]    wherein c 1 =spring constant of the first energy accumulator means [in the unit Nm/rad], and wherein c 2 =spring constant of the second energy accumulator means [in the unit Nm/rad], and wherein J 1 =first mass moment of inertia [in the unit 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 unit Nm/rad] and the spring constant of the transmission input shaft [in the unit Nm/rad] and on the other hand of the second mass moment of inertia [in the unit kg*m 2 ] is greater than or equal to 789568 N*m/(rad*kg*m 2 ) and less than or equal to 3158273 N*m/(rad*kg*m 2 ). Thus this reads as an equation: 
         [0000]      789568 N*m /(rad*kg*m 2 )≦( c   2   +c   GEW )/ J   2 ≦3158273 N*m /(rad*kg*m 2 ), 
         [0000]    wherein c 2 =spring constant of the second energy accumulator means [in the unit Nm/rad] and c GEW =spring constant of the transmission input shaft [in the unit Nm/rad], and J 2 =the second mass moment of inertia [in the unit 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 unit 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 said 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 the 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, e.g., 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, e.g., be configured as a multidisc clutch. Thus, it can comprise a press component or, e.g., be an axially movable and hydraulically loadable piston, by means of which the multidisc clutch can be closed. Thus it can, e.g., be provided that the second component is the press component or the piston of the multidisc clutch or be 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, e.g., a hub or it can be coupled non-rotatably to a hub. This hub can, e.g., 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 said 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 engage 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 the 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 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 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, e.g., 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, e.g., a plate. It can be provided that the outer turbine dish is connected non-rotatably to the first component by means of one or plural 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 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, e.g., 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: 
         [0000]      ( M   mot,max   [Nm]* 0.02*1/°)≦ c   1 ≦( M   mot,max   [Nm]* 0.06*1/°); 
         [0000]    or the following applies: 
         [0000]      ( M   mot,max   [Nm]* 0.03*1/°)≦ c   1 ≦( M   mot,max   [Nm]* 0.05*1/°). 
         [0027]    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: 
         [0000]      ( M   mot,max   [Nm] *0.04*1/°)≦ c   2 ≦( M   mot,max   [Nm] *0.15*1/°); or the following applies: 
         [0000]      ( M   mot,max   [Nm] *0.05*1/°)≦ c   2 ≦( M   mot,max   [Nm] *0.13*1/°); or the following applies: 
         [0000]      ( M   mot,max   [Nm] *0.06*1/°)≦ c   2 ≦( M   mot,max   [Nm] *0.1*1/°). 
         [0028]    Preferably the motor vehicle drive train or the torque converter device or the torsion vibration damper are configured, so that the following applies: 
         [0000]      11000 N*m/ (rad*kg*m 2 )≦( c   1   +c   2 )/ J   1 ≦25000 N*m/ (rad*kg*m 2 ); 
         [0000]    or so that the following applies: 
         [0000]      13000 N*m /(rad*kg*m 2 )≦( c   1   +c   2 )/ J   1 ≦23000 N*m /(rad*kg*m 2 ); 
         [0000]    or so that the following applies: 
         [0000]      15000 N*m /(rad*kg*m 2 )≦( c   1   +c   2 )/ J   1 ≦21000 N*m /(rad*kg*m 2 ). 
         [0029]    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: 
         [0000]      900000 N*m /(rad*kg*m 2 )≦( c   2   +c   GEW )/ J   2 ≦2900000 N*m /(rad*kg*m 2 ); 
         [0000]    or so that the following applies: 
         [0000]      1100000 N*m /(rad*kg*m 2 )≦( c   2   +c   GEW )/ J   2 ≦2700000 N*m /(rad*kg*m 2 ); 
         [0000]    or so that the following applies: 
         [0000]      1300000 N*m /(rad*kg*m 2 )≦( c   2 +c GEW )/ J   2 ≦2500000 N*m /(rad*kg*m 2 ); 
         [0000]    or so that the following applies: 
         [0000]      1500000 N*m /(rad*kg*m 2 )≦( c   2   +c   GEW )/ J   2 &lt;2300000 N*m /(rad*kg*m 2 ). 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS  
         [0030]    Subsequent exemplary embodiments of the invention are described with reference to the figures, wherein: 
           [0031]      FIG. 1  shows a schematic view of an exemplary motor vehicle drive train; 
           [0032]      FIG. 2  shows a section of an exemplary motor vehicle drive train according to the invention, comprising a first exemplary hydrodynamic torque converter device; 
           [0033]      FIG. 3  shows a section of an exemplary motor vehicle drive train according to the invention comprising a second exemplary hydrodynamic torque converter device; 
           [0034]      FIG. 4  shows a section of an exemplary motor vehicle drive train comprising a third hydrodynamic torque converter device; and, 
           [0035]      FIG. 5  shows 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  
       [0036]      FIG. 1  shows an exemplary motor vehicle drive train  2  according to the invention in a schematic illustration. The motor vehicle drive train  2  comprises a combustion engine  250  and a drive shaft or an engine output shaft or crank shaft  18 , which can be driven by the combustion engine  250  in a rotating manner. The combustion engine  250  comprises exactly three cylinders  252 , or it is a three-cylinder engine  250 . The three-cylinder engine  250  comprises a maximum engine torque M mot,max , or it can impart a maximum torque into the drive train  2 , which corresponds to said maximum engine torque M mot,max . 
         [0037]    The motor vehicle drive train  2  comprises a hydrodynamic torque converter device  1 , which is configured according to one of the embodiments, which were described with reference to  FIGS. 2 through 4 . 
         [0038]    The motor vehicle drive train  2  furthermore comprises a transmission  254 , which is, e.g., an automatic transmission. Furthermore, the motor vehicle drive train  2  can comprise a transmission output shaft  256 , a differential  258  and one or several drive axles  260 . The motor vehicle drive train  2  furthermore comprises a transmission input shaft  66  between the torque converter device  1  and the transmission  254 . The torque converter device  1 , or a component like the hub  64  of said torque converter device  1  is connected torque proof to said transmission input shaft  66 . The engine output shaft or the crank shaft  18  is coupled torque proof to the converter housing  16  of said torque converter device  1 . Thus a torque can be transferred from the drive shaft or the engine output shaft or the crank shaft  18  through the torque converter device  1  to the transmission input shaft  66 . 
         [0039]      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 the motor vehicle drive train  2 , according to  FIG. 1 . 
         [0040]    The embodiments illustrated in  FIGS. 2 through 4  are components of an exemplary motor vehicle drive train  2  according to the invention, which comprises a three-cylinder engine  250 , which is not shown in the  FIGS. 2 through 4 , or a combustion engine  250 , which is not shown in the  FIGS. 2 through 4 , which is configured as a three-cylinder engine and thus comprises three cylinders  252 . The hydrodynamic torque converter device  1  comprises a torsion vibration damper  10  and a converter torus  12  formed by a pump shell  20 , a turbine shell  24  and a stator shell  22 , and comprises a converter lockup clutch  14 . 
         [0041]    The torsion vibration damper  10 , the converter torus  12 , and the converter lockup clutch  14  are received in a converter housing  16 . The converter housing  16  is connected substantially torque proof to a drive shaft  18 , which is in particular the crank shaft or the engine output shaft of a combustion engine. 
         [0042]    As discussed, the converter torus  12  comprises a pump or a pump shell  20 , a stator shell  22  and a turbine or a turbine shell  24 , which interact in a known manner. In a known manner, the converter torus  12  comprises a converter torus cavity or a torus interior  28 , which is provided for receiving oil or for an oil flow. The turbine shell  24  comprises an outer turbine dish  26 , which forms a wall section  30 , which directly abuts to the torus interior  28  and which is provided for defining the torus interior  28 . Furthermore, the turbine shell  24  comprises an inner turbine dish  262  and turbine blades in a known manner. An extension  32  of the outer turbine dish  26  connects to the wall section  30  directly abutting to the torus interior  28 . The extension  32  comprises a straight or annular section  34 . The straight or annular section  34  of the extension  32  can, e.g., be configured, so that it is substantially straight in the radial direction of the rotation axis  36  of the torsion vibration damper  10 , and disposed in particular as an annular section in a plane disposed perpendicular to the rotation axis  36 , or so that it defines said plane. 
         [0043]    The torsion vibration damper  10  comprises a first energy accumulator means  38  and a second energy accumulator means  40 . The first energy accumulator means  38  and the second energy accumulator means  40  are spring means in particular. 
         [0044]    In the embodiments according to  FIGS. 2 through 4  it is provided that the first energy accumulator means  38  comprises several first energy accumulators  42 , or that it is comprised of the energy accumulators, like, e.g., coil springs or arc springs, offset from one another in a circumferential direction extending about the 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. 
         [0045]    The spring constant c 1  [in the unit Nm/°] of the first energy accumulator means  38  is greater than or equal to the product of the maximum engine torque M mot,max  [in the unit Nm] of the three-cylinder engine  250  and the factor 0.014 [1/°] and less than or equal to the product of the maximum engine torque [in the unit Nm] of said three-cylinder engine  250  and the factor 0.068 [1/°]. Thus the following applies: 
         [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 three-cylinder engine  250  of the drive train  2  in the unit “Newton times meter” (Nm), and wherein c, is the spring constant of the first energy accumulator means  38  in the unit “Newton meter divided by degrees” (Nm/°). The values or ranges however can be also disposed as it is described at another location of the present disclosure. 
         [0046]    The 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 the 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 the second energy accumulators  44  are respectively configured identical. Different second energy accumulators  44  however can also be configured differently. 
         [0047]    The spring constant c 2  [in the unit Nm/°] of the second energy accumulator means  40  is greater than or equal to the product of the maximum engine torque M mot,max  [in the unit Nm] of the three-cylinder engine  250  and the factor 0.035 [1/°] and less than or equal to the product of the maximum engine torque M mot,max  [in the unit Nm] of the three-cylinder engine  250  and the factor 0.158 [1/°]. Thus, the following applies: 
         [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 the three-cylinder engine  250  of the drive train  2  in the unit “Newton times meter” (Nm), and wherein c 2  is the spring constant of the second energy accumulator means in the unit “Newton tomes meter divided by degrees” (Nm/ 20  ). The values or ranges however can be also disposed as it is described at another location of the present disclosure. 
         [0048]    According to the embodiments according to  FIGS. 2 through 4 , the second energy accumulator means  40  is disposed with reference to the radial direction of the rotation axis  36  radially within the first energy accumulator means  38 . The first energy accumulator means  38  and the second energy accumulator means  40  are connected in series. The torsion vibration damper  10  comprises a first component  46 , which is disposed between the first energy accumulator means  38  and the second energy accumulator means  40 , or connected in series with the energy accumulator means  38 ,  40 . It is also provided in particular, e.g., when the lockup clutch  14  is closed, that a torque can be transferred from the first energy accumulator means  38  through the first component  46  to the second energy accumulator means  40 . The first component  46  can also be designated as intermediary component  46 , which is also done infra. 
         [0049]    It is provided in the embodiments according to  FIGS. 2 through 4 , that the outer turbine dish  26  is connected to the intermediary component  46 , so that a load, in particular torque and/or force, can be transferred from the outer turbine dish  26  to the intermediary component  46 . 
         [0050]    Between the outer turbine dish  26  and the intermediary component  46 , or in the load flow, in particular in the torque or force flow between the outer turbine dish  26  and the intermediary component  46 , a driver component  50  is provided. It can also be provided that the extension  32  also forms the intermediary component  46  and/or the driver component  50 , or takes over their function. It can also be provided that the driver component  50  forms a first component or an intermediary component, which is connected in series in the torque flow between the energy accumulator means  38 ,  40 . It is furthermore provided that along the load transfer path  48 , through which a load or a torque can be transferred from the outer turbine dish  26  to the intermediary component  46 , at least one connection means  52 ,  56  or  54  is provided. Such a connection means  52 ,  56 , or  54  can, e.g., 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. It is appreciated that in  FIG. 4  at the location, where the 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 the respective connection means  52 ,  54 , and  56 , respective adjoining components of the load transfer path  48 , through which the load can be transferred from the outer turbine dish  26  to the intermediary component  46 , are coupled amongst one another. Thus, the extension  32  of the outer turbine dish  26  is coupled in the embodiments according to  FIGS. 2 through 4  with the driver component  50  respectively non-rotatably by a connection means  52  configured as a weld (which can also alternatively be a rivet or bolt connection according  FIG. 4 ) and said driver component  50  is coupled non-rotatably to the intermediary component  46  through a connection means  56 , respectively configured as a rivet or bolt connection. 
         [0051]    It is provided that all connection means  52 ,  54 ,  56 , by which components adjoining along the load transfer path  48  between the outer turbine dish  26  and the intermediary component  46 , like, e.g., the extension  32  and the driver component  50  or the driver component  50  and the intermediary component  46 , are connected, are offset from the wall section  30  of the outer turbine dish  26  directly adjoining to the torus interior  28 . This facilitates at least according to the embodiments, that the bandwidth of possible connection means is increased. Thus it is possible, e.g., that not only thin plate- or MAG- or Laser- or dot welding is used as welding method, but also, e.g., friction welding. 
         [0052]    A second component  60  and a third component  62  are connected in series with the first energy accumulator means  38 , the second energy accumulator means  40  and the intermediary component  46  provided between the two energy accumulator means  38 ,  40 . The second component  60  forms an input component of the first energy accumulator means  38  and the third component  62  forms an output component of the second energy accumulator means  40 . A load or a torque transferred by the second component  60  into the first energy accumulator means  38  can thus be transferred on the output side of the first energy accumulator means  38  through the intermediary component  46  and the second energy accumulator means  40  to the third component  62 . 
         [0053]    The third component  62  engages the hub  64 , forming a non-rotatable connection, which is in turn coupled non-rotatably to an output shaft  66  of the torque converter device  1 , which is, e.g., a transmission input shaft  66  of a motor vehicle transmission. Alternatively it can however also be provided that the third component  62  forms the hub  64 . The outer turbine dish  26  is radially supported at the hub  64  by means of a support section  68 . The support section  68 , which is in particular radially supported at the hub  64 , is substantially configured sleeve shaped. 
         [0054]    It is appreciated that the radial support of the outer turbine dish  26  by means of the support section  68  is configured, so that support forces acting upon the outer turbine dish  26  through the radial support are not conducted through the first or the second energy accumulator means  38 ,  40  from the support section  68  to the outer turbine dish  26 . The support section  68  is rotatable relative to the 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 the hub  64  and the support section  68 . Furthermore, respective bearings can be provided for axial support. The connection already discussed supra between the outer turbine dish  26  and the intermediary component  46  is configured, so that a torque, which is transferrable from the outer turbine dish  26  to the intermediary component  46 , can be transferred without one of the energy accumulator means  38 ,  40  being provided along the respective load transfer path  48 . The torque transfer from the outer turbine dish  26  to the intermediary component  46  through the load transfer path  48  can thus be provided in particular by means of a substantially rigid connection. 
         [0055]    In the embodiments according to  FIGS. 2 through 4  two respective connection means are provided along the load or force or torque transfer path  48  between the outer turbine dish  26  and the intermediary component  46 , and thus a first connection means  52  or  54  and a second connection means  56 . It is appreciated that with reference to the circumferential direction of the 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. The first connection means  52  or  54  (subsequently the “first connection means  52 ” is referred to for purposes of simplification) connect in particular non-rotatably the extension  32  to the driver component  50  and the second connection mean(s)  56  (subsequently referred to as the second connection means  54  for purposes of simplification) connect in particular non-rotatably the driver component  50  to the intermediary component  46 . 
         [0056]    As illustrated in  FIGS. 2 through 4 , the sleeve shaped support portion  68  can, e.g., be a radially inner section of the driver component  50  with reference to the radial direction of the rotation axis  36 . 
         [0057]    The converter lockup clutch  14  is provided in the embodiments according to  FIGS. 2 through 4  as a respective multidisc clutch and comprises a first disk carrier  72 , by which first disks  74  are received non-rotatably, and a second disk carrier  76  by which second disks  78  are received non-rotatably. When the multidisc clutch  14  is open, the first disk carrier  72  is movable relative to the second disk carrier  76  and thus so that the first disk carrier  72  is rotatable relative to the second disk carrier  76 . The second disk carrier  76  is disposed with reference to the radial direction of the axis  36  radially within the first disk carrier  72 , however, also the opposite can be the case. The first disk carrier  72  is connected to the converter housing  16 . For actuation, the multidisc clutch  14  comprises a piston  80 , which is disposed axially movable and which can be loaded, e.g., hydraulically for actuating the multidisc clutch  14 . The piston  80  is connected in a rigid manner or non-rotatably to the second disk carrier  76 , which can be effectuated, e.g., by means of a welded connection. First disks  74  and second disks  78  alternate viewed in longitudinal direction of the rotation axis  36 . When loading the disk packet  79  formed by the first disks  74  and the second disks  78 , by means of the piston  80 , the disk packet  79  is supported on the side of the disk packet  79  opposite to the piston  80  at a section of the inside of the converter housing  16 . Between adjacent disks  74 ,  78  and at both ends of the disk packet  79 , friction liners  81  are provided, which are, e.g., held at the disks  74  and/or  78 . The friction liners  81  which are provided at the ends of the disk packet  79 , can also be supported on the one side and/or the other side also at the inside of the converter housing  16  or at the piston  80 . 
         [0058]    In the embodiments according to  FIGS. 2 and 3 , the piston  80  is integrally formed with the second component  60 , thus the input component of the first energy accumulator means  38 . In the embodiment according to  FIG. 4 , the piston  80  is connected non-rotatably or fixated to the second component  60  or the input component of the first energy accumulator means  38 , wherein the fixation is performed, e.g., by a weld. As a matter of principle a non-rotatable connection can also be performed in another manner. In the embodiments according to  FIGS. 2 and 3 , in an alternative embodiment, the piston  80  and the input component  60  of the first energy accumulator means  38  can also be provided as separate components connected amongst one another in a fixated or non-rotatable manner, e.g., by a weld or a rivet or a bolt. In the embodiment according to  FIG. 4 , also another suitable connection can be provided between the piston  80  and the input component  60  instead of a weld, in order to generate the solid or non-rotatable connection, like, e.g., a bolt or rivet joint or a plug-in connection or alternatively, the piston  80  with the input component  60  can also be manufactured integrally from one piece. 
         [0059]    The piston  80  or the second component  60 , the first component, or the intermediary component  46 , the driver component  50  and the third component  62  are respectively formed by plates. The second component  60  is a flange in particular. The first component  46  is a flange in particular. The third component  62  is a flange in particular. 
         [0060]    In the embodiment according to  FIG. 3 , the plate thickness of the driver component  50  is greater than the plate thickness of the piston  80 , or of the input component  60  of the first energy accumulator means  38 . Furthermore it can be provided in the embodiments according to  FIGS. 2 through 4 , that the mass moment of inertia of the driver component  50  is greater than the mass moment of inertia of the piston  80  or of the input component  60  or of the unit made of these components  60 ,  80 . 
         [0061]    For the 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 the rotation axis  36  at least partially on both sides axially and radially on the outside about the first energy accumulator  42 . In the embodiments according to  FIGS. 2 through 4 , the housing is disposed at the driver component  50 . In most embodiments the non-rotatable disposition at the driver component  50  or at the outer turbine dish is more advantageous from a vibration point of view, than, e.g., a non-rotatable disposition at the second component  60 . The housing  82  in this case comprises a cover  264 , which is, e.g., welded on. 
         [0062]    In the embodiment according to  FIG. 4 , the first energy accumulators  42  can be supported at the 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 the first energy accumulators  42  or for friction reduction can also be accordingly provided in the embodiments according to  FIGS. 2 and 3 . According to  FIGS. 2 and 3 , however, a slider dish or a slider shoe  94  is provided here instead of such a roller shoe  84  for the low friction support of the first energy accumulators  42 . 
         [0063]    Furthermore, a second rotation angle limiter means  92  is provided for the second energy accumulator means  40  in the embodiments according to  FIGS. 2 through 4 , by which the maximum rotation angle or the relative rotation angle of the second energy accumulator means  40  or of the input component of the second energy accumulator means  40  relative to the output component of the second energy accumulator means  40  is limited. This is performed here, so that the maximum rotation angle of the second energy accumulator means  40  is limited by said second rotation angle limiter means  92 , so that it is avoided that the second energy accumulators  44 , which are springs in particular, go into blockage under a respectively high torque loading. The second rotation angle limiter means  92  is configured as shown in  FIGS. 2 through 4 , e.g., so that the driver component  50  and the intermediary component  46  are connected non-rotatably by a bolt, which is in particular a component of the connection means  56 , wherein the bolt extends through a slotted hole, which is provided in the output component of the second energy accumulator means  40  or in the third component  62 . A first rotation angle limiter means can also be provided for the first energy accumulator means  38 , which is not shown in the figures, by which the maximum rotation angle of the first energy accumulator means  38  is limited, so that a blockage loading of the first energy accumulators  42 , which are in particular provided as respective springs, is avoided. In particular when, which is advantageously the case, the second energy accumulators  44  are straight compression springs and the 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 the 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 reduce the number of components or the manufacturing cost. 
         [0064]    In a particularly advantageous embodiment, it is provided in the configurations according to  FIGS. 2 through 4 , that the rotation angle of the first energy accumulator means  38  is limited to a maximum first rotation angle and the rotation angle of the second energy accumulator means  40  is limited to a maximum second rotation angle, wherein the first energy accumulator means  38  reaches its maximum first rotation angle, when a first threshold torque is applied to the first energy accumulator means  38 , and wherein the second energy accumulator means  40  reaches its second maximum rotation angle, when a second threshold torque is applied to the 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 ,  40  or of the energy accumulators  42 ,  44  of the two energy accumulator means  38 ,  40 , possibly or in particular also by the first and/or the second rotation angle limiter means. It can be provided that the first energy accumulators  42  go into blockage under the first threshold torque, so that the first energy accumulator means  38  reaches its maximum first rotation angle, and it is caused by a second rotation angle limiter means for the second energy accumulator means  40 , that the 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. 
         [0065]    This way, a particularly good setting for partial load operations can be reached. 
         [0066]    It is appreciated that the rotation angle of the first energy accumulator means  38  or of the 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 the rotation axis  36  of the 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 the 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 the energy accumulators  42  or  44  of the respective energy accumulator means  38  or  40  absorbing energy or releasing stored energy. 
         [0067]    In the converter torus  12  and also outside of the converter torus  12  within the converter housing  16 , oil is included in particular. 
         [0068]    In the embodiments according to  FIGS. 2 through 4 , the piston  80 , or the second component, or the input component  60  of the first energy accumulator means  38  form several lugs  86 , distributed about the circumference, each comprising a non-free end  88  and a free end  90 , and which are provided for a face side, input side loading of the respective first energy accumulator  42 . The non-free end  88  is thus disposed with reference to the radial direction of the rotation axis  36  radially within the free end  90  of the respective lug  86 . 
         [0069]    As shown in  FIGS. 2 through 4 , the radial extension of the driver component  50  can be greater than the center radial distance of the first energy accumulator(s)  42  from the second energy accumulator(s)  44 . 
         [0070]    In the embodiments according to  FIGS. 2 through 4 , it is respectively provided that the transmission input shaft  66  is configured, so that the spring constant c GEW  of the 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 at another location of the present disclosure. The spring constant c GEW  of the transmission input shaft  66  is thus in particular the one, which is effective, when the transmission input shaft  66  is torsion loaded about its central longitudinal axis. 
         [0071]    When transmitting a torque through the first component  46 , a first mass moment of inertia J 1  counteracts the torque transferred through the first component  46 . When transmitting a torque through the third component  62 , a second mass moment of inertia J 2  acts against a change of the torque transmitted through the third component  62 . 
         [0072]    In the embodiments according to  FIGS. 2 through 4  it is respectively provided that the motor vehicle drive train  2 , or the torque converter device  1 , or the 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 the first energy accumulator means  38  [in the unit Nm/rad] and the spring constant c 2  of the second energy accumulator means  40  [in the unit Nm/rad] and on the other hand of the first mass moment of inertia J 1  [in the unit kg*m 2 ], is greater than or equal to 9993 N*m/(rad*kg*m 2 ) and less than or equal to 27758 N*m/(rad*kg*m 2 ). Thus, put into an equation the following applies: 
         [0000]      9993 N*m /(rad*kg*m 2 )≦( c   1   +c   2 )/ J   1 ≦27758 N*m /(rad*kg*m 2 ), 
         [0000]    wherein c 1  is the spring constant of the first energy accumulator means  38  [in the unit Nm/rad] and wherein c 2  is the spring constant of the second energy accumulator means  40  [in the unit Nm/rad] and wherein J 1  is the first mass moment of inertia [in the unit kg*m 2 ]. The values or ranges however can be set in a manner as it is described at another location of the present disclosure. 
         [0073]    In the embodiments according to  FIGS. 2 through 4  it is furthermore respectively provided that the motor vehicle drive train  2 , or the torque converter device  1  or the 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 the second energy accumulator means  40  [in the unit Nm/rad] and the spring constant c GEW  of the transmission input shaft  66  [in the unit Nm/rad] and on the other hand of the second mass moment of inertia J 2  [in the unit kg*m 2 ], is greater than or equal to 789568 N*m/(rad*kg*m 2 ) and less or equal to 3158273 N*m/(rad*kg*m 2 ). Thus, put into an equation, the following applies: 
         [0000]      789568 N*m /(rad*kg*m 2 )≦( c   2   +c   GEW )/ J   2 ≦3158273 N*m /(rad*kg*m 2 ), 
         [0000]    wherein c 2  is the spring constant of the second energy accumulator means  40  [in the unit Nm/rad] and wherein c GEW  is the spring constant of the transmission input shaft  66  [in the unit Nm/rad], and wherein J 2  is the second mass moment of inertia [in the unit kg*m 2 ]. The values or ranges however, can be comprised in a manner as it is described at another location of the present disclosure. 
         [0074]    In the embodiments according to  FIGS. 2 through 4  in particular, it can be provided 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 the 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 the arc springs  42 , possibly a portion of the 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 the rotation axis  36 . 
         [0075]    Furthermore it can be provided in the embodiments according to  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 the flange  62 , and possibly a portion of the transmission input shaft  66  and possibly a portion of the compression springs  44  and possibly a non-illustrated diaphragm spring for a controlled hysteresis, and possibly shaft retaining rings and/or seal elements. 
         [0076]      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 according to  FIG. 1 , comprising a configuration according to  FIG. 2  or according to  FIG. 3 , or according to  FIG. 4  in case the converter lockup clutch is closed. 
         [0077]    The system can be considered in particular in an ideal manner as a series connection comprising a first engine side rotating mass  266 , a clutch  268 , a second rotating mass  270 , connected at the input side of a first spring  272  between the clutch  268 , the first spring  272 , a third rotating mass  274 , connected between the first spring  272  and a second spring  276 , the second spring  276 , a fourth rotating mass  278 , connected between the second spring  276  and a third spring  280 , and the third spring  280 . 
         [0078]    The section formed by the series connection of the first spring  272 , the third rotating mass  274 , the second spring  276 , the fourth rotating mass  278  and the third spring  280  thus forms from an ideal point of view a spring/rotating mass diagram for the first energy accumulator means  38 , the connection of the first energy accumulator means  38  and the second energy accumulator means  40 , the second energy accumulator means  40 , the connection of the second energy accumulator means  40  to the transmission input shaft  66  and the transmission input shaft  66 . 
         [0079]    Subsequently, an exemplary improvement of the exemplary embodiments, advantages and effects according to the invention described supra based on figures, shall be described, which can be provided at least in an improved embodiment of the invention. 
         [0080]    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 said 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. 
         [0081]    The torque converter device  1  or the torque converter  1  comprising the torsion vibration damper or the energy accumulator devices  38 ,  40  constitutes a torsion vibration system in combination with the engine  250  and the drive train  2  of the vehicle. The natural modes of the torsion vibration system are induced due to the variations of the rotation of the 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 the torsion dampers or the energy accumulator means  38 ,  40  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 the 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). 
         [0082]    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. 
         [0083]    At higher speeds, increased friction can lead to an increased stiffness of the outer damper or of the first energy accumulator means  38 . Herein, the inner damper connected in series, or the second energy accumulator means  40  (in particular without friction), leads to more advantageous vibration characteristics in the upper speed range. 
         [0084]    A significant improvement of the double damper or of the torsion vibration damper is performed by the configuration of a torsion vibration damper or a 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. 
         [0085]    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 the 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 the second energy accumulator means  40 . 
       DESIGNATIONS 
       [0086]      1  hydrodynamic torque converter device 
         [0087]      2  motor vehicle drive train 
         [0088]      10  torsion vibration damper 
         [0089]      12  converter torus 
         [0090]      14  converter lockup clutch 
         [0091]      16  converter housing 
         [0092]      18  drive shaft like engine output shaft of a combustion engine 
         [0093]      20  pump or pump shell 
         [0094]      22  stator shell 
         [0095]      24  turbine or turbine shell 
         [0096]      26  outer turbine shell 
         [0097]      28  torus interior 
         [0098]      30  wall section of  26   
         [0099]      32  extension at  30  of  26   
         [0100]      34  straight section of  32  or annular disk shaped section of  32   
         [0101]      36  rotation axis of  10   
         [0102]      38  first energy accumulator means 
         [0103]      40  second energy accumulator means 
         [0104]      42  first energy accumulator 
         [0105]      44  second energy accumulator 
         [0106]      46  first component of  10   
         [0107]      48  load transfer path 
         [0108]      50  driver component 
         [0109]      52  connection means or welded connection between  32  and  50  in  48   
         [0110]      54  connection means or bolt or rivet connection between  32  and  50  in  48   
         [0111]      56  connection means or bolt or rivet connection between  50  and  46  in  48   
         [0112]      60  second component 
         [0113]      62  third component 
         [0114]      64  hub 
         [0115]      66  output shaft, transmission input shaft 
         [0116]      68  support section 
         [0117]      72  first disk carrier of  14   
         [0118]      74  first disk of  14   
         [0119]      76  second disk carrier of  14   
         [0120]      78  second disk of  14   
         [0121]      79  disk packet of  14   
         [0122]      80  piston for actuating  14   
         [0123]      81  friction liner of  14   
         [0124]      82  housing 
         [0125]      84  roller shoe 
         [0126]      86  lug 
         [0127]      88  non-free end of  82   
         [0128]      90  free end of  82   
         [0129]      92  second rotation angle limiter means  92  of  40   
         [0130]      94  slider shoe 
         [0131]      250  combustion engine, three-cylinder engine 
         [0132]      252  cylinder of  250   
         [0133]      254  transmission 
         [0134]      256  transmission output shaft 
         [0135]      258  differential 
         [0136]      260  drive axle 
         [0137]      262  inner turbine dish 
         [0138]      264  cover 
         [0139]      266  engine side rotating mass, first rotating mass 
         [0140]      268  clutch 
         [0141]      270  rotating mass of the connection, second rotating mass 
         [0142]      272  first spring 
         [0143]      274  rotating mass of the connection between  272  and  276 , third rotating mass 
         [0144]      276  second spring 
         [0145]      278  rotating mass of the connection between  276  and  280 , fourth rotating mass 
         [0146]      280  third spring