The invention relates to an automotive drive train having a combustion engine configured as a 4-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 a 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 nonrotatably to the first component.
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 nonrotatably to the outer turbine dish of the turbine shell.
It is an object of the invention to configure a motor vehicle drive train comprising a 4-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.
According to the present invention, a motor vehicle drive train is proposed.
Thus, a motor vehicle drive train is proposed in particular, which comprises a 4-cylinder engine or a combustion engine configured as 4-cylinder engine. The combustion engine or the 4-cylinder engine has a maximum engine torque Mmot,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 nonrotatably to the engine output shaft, or to the crank shaft. 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 at least one first energy accumulators, or it is formed by at least one first energy accumulators, and the second energy accumulator means comprises at least one second accumulators, or it is formed by at least one second accumulators. Between the first and the 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.
It is appreciated that a means, which is designated as “converter torus”, in this application is sometimes designated as “(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.
The turbine shell comprises an outer turbine dish, which is connected nonrotatably to the first component. Furthermore, the torque converter device comprises a third component, which is preferably connected nonrotatably to the transmission input shaft, which in particular abuts to the torque converter device. In one embodiment, the third component is directly coupled to the transmission input shaft, in particular coupled nonrotatably. However, in an alternate embodiment, the third component is coupled to the transmission input shaft through one or several components connected in between, preferably nonrotatably 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.
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 e.g. be nonrotatable 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 the torque transferred through the first component. Preferably, 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 mass moment of inertia of the first component and thus in particular respectively as a summand of several summands.
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 e.g. be nonrotatable 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.
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, measured in the units of Nm/°, of the first energy accumulator means is greater than or equal to the product of the maximum engine torque, measured in the unit Nm, of the 4-cylinder engine and the factor of 0.014 [1/°] and less than or equal to the product of the maximum engine torque of the 4-cylinder engine and the factor 0.068 [1/°]. Put into an equation, this means:
(Mmot,max[Nm]*0.014*1/°)≦c1≦(Mmot,max[Nm]*0.068*1/°),
wherein Mmot,max [Nm] is the maximum engine torque of the combustion engine or of the 4-cylinder engine of the drive train in the unit “Newton times meter” (Nm), and wherein c1 is the spring constant of the first energy accumulator means in the unit “Newton times meter divided by degrees” (Nm/°).
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 4-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 4-cylinder engine and the factor 0.158 [1/°]. Put into an equation, this means:
(Mmot,max[Nm]*0.035*1/°)≦c2≦(Mmot,max[Nm]*0.158*1/°),
wherein Mmot, max [Nm] is the maximum engine torque of the combustion engine or of the 4-cylinder engine of the drive train in the unit “Newton times meter” (Nm), and wherein c2 is the spring constant of the second energy accumulator means in the unit “Newton times meter divided by degrees” (Nm/°).
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*m2], is greater than or equal to 14037 N*m/(rad*kg*m2), and less than or equal to 49348 N*m/(rad*kg*m2). Thus, put into an equation it is provided:
14037 N*m/(rad*kg*m2)≦(c1+c2)/J1≦49348N*m/(rad*kg*m2),
wherein c1=spring constant of the first energy accumulator means [in the unit Nm/rad], and wherein c2=spring constant of the second energy accumulator means [in the unit Nm/rad], and wherein J1=first mass moment of inertia [in the unit kg*m2]. The abbreviation “rad” designates the radian measure.
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*m2] is greater than or equal to 1403677 N*m/(rad*kg*m2) and less than or equal to 5614708 N*m/(rad*kg*m2). Thus this reads as an equation:
1403677 N*m/(rad*kg*m2)≦(c2+cGEW)/J2≦5614708 N*m/(rad*kg*m2),
wherein c2=spring constant of the second energy accumulator means [in the unit Nm/rad] and cGEW=spring constant of the transmission input shaft [in the unit Nm/rad], and J2=the second mass moment of inertia [in the unit kg*m2].
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/°≦cGEW≦350 Nm/°, wherein cGEW=spring constant of the transmission input shaft [in the unit Nm/°]. The following applies in particular: 120 Nm/°≦cGEW≦300 Nm/°. According to another preferred embodiment the following applies: 120 Nm/°≦cGEW≦210 Nm/°. According to another preferred embodiment the following applies: 130 Nm/°≦cGEW≦150 Nm/°. It is preferred in particular, that the spring constant cGEW 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 cGEW 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 cGEW 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 rotatable and thus about its central longitudinal axis or rotation axis.
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.
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 transferable 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 torque proof, 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 multidisc clutch. Thus, it can comprise a press component or an e.g. axially movable and e.g. hydraulically loadable piston, by means of which the multidisc clutch can be closed. Thus, for example, it can be provided that the second component is the press component or the piston of the multidisc clutch or connected nonrotatably to the press component or the piston.
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 nonrotatably to a hub. This hub can, for example be coupled nonrotatably to the transmission input shaft, or it can engage nonrotatably with the transmission input shaft.
It is preferably provided that the second component or a component connected nonrotatably 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 nonrotatably 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 nonrotatably 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 nonrotatably 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 nonrotatably 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.
According to a preferred embodiment, the first energy accumulator means comprises at least one 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 accumulator(s) are disposed, distributed, or offset about the circumference with circumference referring to the circumferential direction of the rotation axis of the torsion vibration damper. However, in an alternate improved embodiment, several first energy accumulators may be 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.
According to a preferred embodiment, the second energy accumulator means comprises several second energy accumulators. The second energy accumulators, according to a preferred embodiment, are at least one coil spring or compression spring or straight spring. In one embodiment, all the second energy accumulators are connected in parallel. According to an improved embodiment, the at least one 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, in an alternate embodiment, a plurality of 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 the alternate embodiment, 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.
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.
The spring constant of the first energy accumulator means is in particular the spring constant, or the combined spring constant, which is effective 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.
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 axis of rotation 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.
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 nonrotatably 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 is thus 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.
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.
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:
(Mmot,max[Nm]*0.02*1/°)≦c1≦(Mmot,max[Nm]*0.06*1/°);
or the following applies:
(Mmot,max[Nm]*0.03*1/°)≦c1≦(Mmot,max[Nm]*0.05*1/°).
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:
(Mmot,max[Nm]*0.04*1/°)≦c2≦(Mmot,max[Nm]*0.15*1/°); or the following applies:
(Mmot,max[Nm]*0.05*1/°)≦c2≦(Mmot,max[Nm]*0.13*1/°); or the following applies:
(Mmot,max[Nm]*0.06*1/°)≦c2≦(Mmot,max[Nm]*0.1*1/°).
Preferably the motor vehicle drive train or the torque converter device or the torsion vibration damper is configured, so that the following applies:
17000 N*m/(rad*kg*m2)≦(c1+c2)/J1≦46000 N*m/(rad*kg*m2);
or so that the following applies:
20000 N*m/(rad*kg*m2)≦(c1+c2)/J1≦43000 N*m/(rad*kg*m2);
or so that the following applies:
23000 N*m/(rad*kg*m2)≦(c1+c2)/J1≦40000 N*m/(rad*kg*m2).
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:
1800000 N*m/(rad*kg*m2)≦(c2+cGEW)/J2≦5200000 N*m/(rad*kg*m2);
or so that the following applies:
2200000 N*m/(rad*kg*m2)≦(c2+cGEW)/J2≦4800000 N*m/(rad*kg*m2);
or so that the following applies:
2400000 N*m/(rad*kg*m2)≦(c2+cGEW)/J2≦4400000 N*m/(rad*kg*m2);
or so that the following applies:
2800000 N*m/(rad*kg*m2)≦(c2+cGEW)/J2≦4000000 N*m/(rad*kg*m2).
The nature and mode of the 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:
a schematic view of an exemplary motor vehicle drive train;
At the outset, it should be appreciated that like drawing numbers on different drawing views identify identical structural elements of the invention. It also should be appreciated that figure proportions and angles are not always to scale in order to clearly portray the attributes of the present invention.
While the present invention is described with respect to what is presently considered to be the preferred embodiments, it is understood that the invention is not limited to the disclosed embodiments. The present invention is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
The motor vehicle drive train 2 comprises a hydrodynamic torque converter device 1, which is configured according to one of the embodiments, which are described with reference to
The motor vehicle drive train 2 furthermore comprises a transmission 254, which is, for example, 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 the torque converter device 1 is connected nonrotatably to the transmission input shaft 66. The engine output shaft or the crank shaft 18 is coupled nonrotatably to the converter housing 16 of the 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.
The
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 nonrotatably to a drive shaft 18, which is in particular the crank shaft or the engine output shaft of a combustion engine.
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 radial direction of the axis of rotation 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 the plane.
The torsion vibration damper 10 comprises a first energy accumulator means 38 and a second energy accumulator means 40. In the embodiment shown, the first energy accumulator means 38 and the second energy accumulator means 40 are both spring means in particular.
In the embodiments according to
The spring constant c1, measured in the unit Nm/°, of the first energy accumulator means 38 is greater than or equal to the product of the maximum engine torque Mmot,max, measured in the unit Nm] of the 4-cylinder engine 250 and the factor 0.014 [1/°] and less than or equal to the product of the maximum engine torque in units Nm of the 4-cylinder engine 250 and the factor 0.068 [1/°]. Thus the following applies:
(Mmot,max[Nm]*0.014*1/°)≦c1≦(Mmot,max[Nm]*0.068*1/°),
wherein Mmot,max [Nm] is the maximum engine torque of the combustion engine or of the 4-cylinder engine 250 of the drive train 2 measured in the unit “Newton times meter” (Nm), and wherein c1 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 described at another location of the present disclosure.
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. In one embodiment, the second energy accumulators 44 are respectively configured identically. In an alternate embodiment, second energy accumulators 44 however can also be configured differently.
The spring constant c2 [in the unit Nm/°] of the second energy accumulator means 40 is greater than or equal to the product of the maximum engine torque Mmot,max [in the unit Nm] of the 4-cylinder engine 250 and the factor 0.035 [1/°] and less than or equal to the product of the maximum engine torque Mmot,max[in the unit Nm] of the 4-cylinder engine 250 and the factor 0.158 [1/°]. Thus, the following applies:
(Mmot,max[Nm]*0.035*1/°)≦c2≦(Mmot,max[Nm]*0.158*1/°),
wherein Mmot,max [Nm] is the maximum engine torque of the combustion engine or the 4-cylinder engine 250 of the drive train 2 in the unit “Newton times meter” (Nm), and wherein c2 is the spring constant of the second energy accumulator means in the unit “Newton times meter divided by degrees” (Nm/°). The values or ranges however can be also disposed as described at another location of the present disclosure.
According to the embodiments seen in
It is provided in the embodiments according to
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. In one embodiment, the extension 32 also forms the intermediary component 46 and/or the driver component 50, or takes over their function. In an alternate embodiment, the driver component 50 forms a first component or an intermediary component, which is connected in series in the torque flow between the first energy accumulator means 38 and the second accumulator means 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 and/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
It is provided that all connection means 52, 54, and 56, by which components adjoining along the load transfer path 48 between the outer turbine dish 26 and the intermediary component 46, like, for example, 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 number of possible connection means can be 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.
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.
The third component 62 engages the hub 64, forming a nonrotatable connection, which is in turn coupled nonrotatably 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. In an alternate embodiment, the third component 62 may form 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 as a sleeve.
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 support section 68 are not conducted through the first energy accumulator means 38 or the second energy accumulator means 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 discussed supra between the outer turbine dish 26 and the intermediary component 46 may be configured, so that torque, which is transferable from the outer turbine dish 26 to the intermediary component 46, can be transferred without one of the energy accumulator means 38 and/or 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.
In the embodiments according to
As illustrated in
The converter lockup clutch 14 is provided in the embodiments according to
In the embodiments according to
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 preferably may be a flange. The first component 46 is a flange preferably. The third component 62 is a flange preferably.
In the embodiment according to
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
In the embodiment according to
Furthermore, a second rotation angle limiter means 92 is provided for the second energy accumulator means 40 in the embodiments according to
In a particularly advantageous embodiment, it is provided in the configurations according to
This way, a particularly good setting for partial load operations can be reached.
It is appreciated that the rotation angle of the first energy accumulator means 38 or of the second energy accumulator means 40, up to the maximum first or maximum second rotation angle, respectively, 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 the 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.
Oil is included in particular in the converter torus 12 and also outside of the converter torus 12 within the converter housing 16.
In the embodiments according to
As shown in
In the embodiments according to
When transmitting a torque through the first component 46, a first mass moment of inertia J1 counteracts the torque transferred through the first component 46. When transmitting a torque through the third component 62, a second mass moment of inertia J2 acts against a change of the torque transmitted through the third component 62.
In the embodiments according to
14037 N*m/(rad*kg*m2)≦(c1+c2)/J1≦49348 N*m/(rad*kg*m2),
wherein c1 is the spring constant of the first energy accumulator means 38 [in the unit Nm/rad] and wherein c2 is the spring constant of the second energy accumulator means 40 [in the unit Nm/rad] and wherein J1 is the first mass moment of inertia [in the unit kg*m2]. The values or ranges however can be set in a manner as described elsewhere in the present disclosure.
In the embodiments according to
1403677 N*m/(rad*kg*m2)≦(c2+cGEW)/J2≦5614708 N*m/(rad*kg*m2),
wherein c2 is the spring constant of the second energy accumulator means 40 [in the unit Nm/rad] and wherein cGEW is the spring constant of the transmission input shaft 66 [in the unit Nm/rad], and wherein J2 is the second mass moment of inertia [in the unit kg*m2]. The values or ranges however, can be comprised in a manner as it is described at another location of the present disclosure.
In the embodiments according to
Furthermore it can be provided in the embodiments according to
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, and 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.
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.
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.
Quite frequently good or optimum insulation properties will be required, when the lockup clutch is completely closed in order to reach the goals of a lower and/or minimum fuel consumption or CO2 output. It can thus be desirable that the goals are 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.
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 the natural frequency coincides with the frequency of rotation of the combustion engine 250, the system vibrates in resonance, meaning 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 so that 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 (=>turbine against the increased mass moment of inertia).
Through the arrangement of the double damper or of the torsion vibration damper 10, 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 38 and of the inner damper, connected in series, or of the second energy accumulator means 40.
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.
A significant improvement of the double damper or of the torsion vibration damper 10 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.
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.
Thus it is seen that the objects of the invention are efficiently obtained, although changes and modifications to the invention should be readily apparent to those having ordinary skill in the art, which changes would not depart from the spirit and scope of the invention as claimed.
Number | Date | Country | Kind |
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10 2005 053 605.0 | Nov 2005 | DE | national |
This application is the National Stage of PCT International Application No. PCT/DE2006/001816, filed Oct. 16, 2006, which application published in German and is hereby incorporated by reference in its entirety, which application claims priority from German Patent Application No. 10 2005 053 605.0, filed Nov. 10, 2005 which is incorporated by reference in its entirety.
Filing Document | Filing Date | Country | Kind | 371c Date |
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PCT/DE2006/001816 | 10/16/2006 | WO | 00 | 5/9/2008 |