Patent Abstract:
The invention relates to a 9-speed transmission made up of two simple planetary gear sets including a drive group and an output group designed as a Ravigneaux set having six shift elements, namely three clutches and three brakes, certain specific embodiments being expandable to form an 11-speed transmission by adding a fourth brake.

Full Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims priority of German Patent Application No. DE 10 2014 109 616.9, filed Jul. 9, 2014, which is hereby incorporated by reference. 
     FIELD OF THE INVENTION 
     The present invention relates to a 9-speed transmission for a motor vehicle, which theoretically is composed of an input-side drive group made up of two simple planetary gear sets and an output group connected to the drive group via two connecting shafts, each including multiple shift elements. 
     Such a transmission is known both from US 2012/01721 72 A1 and from DE 10 2009 025 609 A1. 
     The output groups of these transmissions and the drive groups are composed of two simple planetary gear sets having associated shift elements. In total, six shift elements are provided, namely three brakes and three clutches. The known transmissions implement a multi-stepped, progressive transmission range of the 9 forward gears where, in each gear, three of the present shift elements are closed and the remaining are open. The disadvantage with the known transmissions is, in part, the very high circumferential speeds which may occur in particular on one of the ring gears of the output group. According to a realistic estimation based on typical stationary gear ratios and transmission dimensions, the ring gear of the output group rotating the fastest may encounter circumferential speeds of 60 m/s to 70 m/s. Such circumferential speeds must be considered borderline even with a very strong (and consequently expensive) design of the elements. 
     SUMMARY OF THE INVENTION 
     It is the object of the present invention to refine the known transmissions in such a way that lower the maximum circumferential speeds which occur at a functionally approximately identical behavior. 
     This object is achieved by a transmission system of the present invention, namely by a transmission system for a motor vehicle including a drive stage coupleable via an input shaft to a drive assembly of the motor vehicle, an output stage connected to the drive stage via a first connecting shaft and a second connecting shaft and couplable to an output of the motor vehicle via an output shaft, and a transmission housing surrounding the drive stage and the output stage, the drive stage including
         a first planetary gear set having a first sun gear, a first ring gear and a first planet carrier, on which a set of first planet gears is rotatably mounted, which mesh with the first sun gear on the one hand and with the first ring gear on the other hand,   a second planetary gear set having a second sun gear, a second ring gear and a second planet carrier, on which a set of second planet gears is rotatably mounted, which mesh with the second sun gear on the one hand and with the second ring gear on the other hand, and   a first clutch and a second clutch, with the aid of which in each case two elements of the planetary gear sets of the drive stage are shiftably coupled to each other, and a first brake and a second brake, with the aid of which in each case one element of the planetary gear sets of the drive stage is shiftably coupled to the housing, and the output stage including   a Ravigneaux planetary gear set having a first Ravigneaux sun gear, a second       

     Ravigneaux sun gear, a Ravigneaux ring gear and a Ravigneaux planet carrier, on which two sets of Ravigneaux planet gears are rotatably mounted, namely one set of short planet gears and one set of stepped long planet gears having one larger and one smaller long planet stage, of which one long planet stage meshes with the short planet gears, one of the Ravigneaux sun gears meshing with the set of short planet gears, and the Ravigneaux ring gear meshing with one of the sets of Ravigneaux planet gears, and the other of the Ravigneaux sun gears meshing with the long planet stage [and] not meshing with the short planet gears,
         a third clutch, with the aid of which one element of the Ravigneaux planetary gear set is shiftably coupled to the second connecting shaft, and   a third brake, with the aid of which the first Ravigneaux sun gear is shiftably coupled to the housing.       

     The present invention is based on the basic idea of combining the two simple planetary gear sets of the output group to form one Ravigneaux planetary gear set and of transforming the fastest ring gear of the output group in the known transmissions to one of the sun gears of the Ravigneaux planetary gear set. Due to the very much smaller diameter of the sun gear compared to the ring gear, with an otherwise identical design, considerably lower maximum circumferential speeds arise, which in particular may be below the limiting value of 40 m/s, which is generally considered to be favorable. 
     The drive group may essentially be retained compared to the above-mentioned prior art; however, it may also be varied in moderation within the scope of the present invention. Variation options also exist within the scope of the present invention for the specific design of the output group. 
     It shall be noted at this point that, within the scope of the present description, the term “connect” or “connection” is used for fixed connections of two elements which are not detachable during the intended operation. Contrary to this, the term “couple” or “coupling” is used in a more general manner and includes both the above-mentioned connections and couplings which are detachable during the intended operation, the latter in each case being explicitly referred to as “shiftably coupled” if necessary. The term “shift element” within the scope of the present invention includes both “brakes,” which in each case shiftably couple a rotating element to the transmission housing, and “clutches,” which in each case shiftably couple two elements rotating relative to the transmission housing. This selection of terms shall be understood to be entirely independent of the design of the corresponding elements. 
     In particular, both the described brakes and the described clutches may be implemented as shiftable free wheels, multi-disk clutches, synchronizers or in another manner, for example. With respect to the expressions “sun gear,” “ring gear” and “planet carrier,” those skilled in the art will understand that these may refer both to the particular planetary gear set element and the associated shaft, the specific meaning in each case resulting from the context. 
     The preferred specific embodiments shall be described hereafter in the order of the axial position of the corresponding design engagement option from the transmission input to the transmission output. 
     Preferably it is provided that the input shaft is connected to the second sun gear and the second connecting shaft. Typically, this is the central shaft of the entire transmission system. 
     In one first specific embodiment, it is provided with respect to the connections of the planetary gear sets and the arrangement of the shift elements within the drive group that
         the first connecting shaft is connected to the first ring gear, and the first planet carrier is connected to the second ring gear;   the second sun gear ( 201 ) is shiftably coupled to the second planet carrier with the aid of the first clutch;   the first ring gear is shiftably coupled to the second planet carrier with the aid of the second clutch;   the second planet carrier is shiftably coupled to the housing with the aid of the first brake; and   the first sun gear is shiftably coupled to the housing with the aid of the second brake.       

     Alternatively, it may be provided according to a second specific embodiment that
         the first connecting shaft is connected to the second ring gear, and the second planet carrier is connected to the first ring gear;   the first planet carrier is shiftably coupled to the second sun gear with the aid of the first clutch;   the first planet carrier is shiftably coupled to the second ring gear with the aid of the second clutch;   the first planet carrier is shiftably coupled to the housing with the aid of the first brake; and   the first sun gear is shiftably coupled to the housing with the aid of the second brake.       

     Both variants are known from the prior art as a drive group, however in conjunction with an output group which is composed of two simple planetary gear sets. 
     The two connecting shafts form the output of the drive group and, at the same time, the input of the output group. Those skilled in the art will recognize that these will generally not involve separate shafts, but the customary planetary gear set shafts, which as the only shafts extending between the two groups merely fulfill the function of “connecting shafts” and are therefore referred to in this way here. 
     The first connecting shaft is preferably connected to the second Ravigneaux sun gear within the output group. In contrast, two preferred specific embodiments are provided for the connection of the second connecting shaft. 
     A first specific embodiment is characterized in that the Ravigneaux planet carrier is shiftably coupled to the second connecting shaft with the aid of the third clutch. Correspondingly, the output shaft is connected to the Ravigneaux planet carrier in this specific embodiment. 
     A second specific embodiment is characterized in that the Ravigneaux ring gear is shiftably coupled to the second connecting shaft with the aid of the third clutch. Correspondingly, the output shaft is connected to the Ravigneaux ring gear in this specific embodiment. 
     Each of the specific embodiments of the drive group discussed here may be combined with each of the specific embodiments of the output group discussed here to form a transmission system according to the present invention. It is thus conceivable to have different drive groups and different output groups available, and to combine them within the meaning of a modular transmission kit by connecting the particular shafts acting as connecting shafts. 
     If the transmission system according to the present invention is expanded by a fourth brake, an 11-speed transmission can be implemented. In particular, it is provided for this purpose that the drive group includes a fourth brake, with the aid of which the first planet carrier is shiftably coupled to the housing. 
     The following shifting tables show the activations of the shift elements necessary for setting the individual gears in a 9-speed transmission according to the present invention (Table 1) and in an 11-speed transmission according to the present invention (Table 2). The columns are in each case assigned to one shift element, B 1  denoting the first brake, B 2  the second brake, B 3  the third brake, B 4  the fourth brake, K 1  the first clutch, K 2  the second clutch, and K 3  the third clutch. “X” denotes the shift elements which are closed in the particular gear. Open shift elements are denoted by empty cells in the table. 
     
       
         
               
               
               
             
               
               
               
               
               
               
               
             
           
               
                   
                 TABLE 1 
               
             
             
               
                   
                   
               
               
                   
                 Mode 
                   
               
             
          
           
               
                 Gear 
                 B1 
                 B2 
                 B3 
                 K1 
                 K2 
                 K3 
               
               
                   
               
               
                 1st gear 
                   
                 X 
                 X 
                   
                 X 
                   
               
               
                 2nd gear 
                   
                   
                 X 
                 X 
                 X 
               
               
                 3rd gear 
                   
                 X 
                 X 
                 X 
               
               
                 4th gear 
                   
                 X 
                 X 
                   
                   
                 X 
               
               
                 5th gear 
                   
                 X 
                   
                 X 
                   
                 X 
               
               
                 6th gear 
                   
                   
                   
                 X 
                 X 
                 X 
               
               
                 7th gear 
                   
                 X 
                   
                   
                 X 
                 X 
               
               
                 8th gear 
                 X 
                   
                   
                   
                 X 
                 X 
               
               
                 9th gear 
                 X 
                 X 
                   
                   
                   
                 X 
               
               
                 Idle 
                   
                 X 
                 X 
               
               
                 Reverse 
                 X 
                 X 
                 X 
               
               
                   
               
             
          
         
       
     
     
       
         
               
               
             
               
               
               
               
               
               
               
               
               
             
           
               
                   
                 TABLE 2 
               
             
             
               
                   
                   
               
               
                   
                 Mode 
               
             
          
           
               
                   
                 Gear 
                 B1 
                 B2 
                 B3 
                 B4 
                 K1 
                 K2 
                 K3 
               
               
                   
                   
               
               
                   
                     1st gear 
                   
                   
                 X 
                 X 
                   
                 X 
                   
               
               
                   
                 2nd gear  
                   
                 X 
                   
                 X 
                   
                 X 
               
               
                   
                 3rd gear 
                   
                   
                   
                 X 
                 X 
                 X 
               
               
                   
                 4th gear 
                   
                 X 
                   
                 X 
                 X 
               
               
                   
                 5th gear 
                   
                 X 
                   
                 X 
                   
                   
                 X 
               
               
                   
                 6th gear 
                   
                 X 
                   
                   
                 X 
                   
                 X 
               
               
                   
                 7th gear 
                   
                   
                   
                   
                 X 
                 X 
                 X 
               
               
                   
                 8th gear 
                   
                 X 
                   
                   
                   
                 X 
                 X 
               
               
                   
                 9th gear 
                   
                   
                 X 
                   
                   
                 X 
                 X 
               
               
                   
                 10th gear  
                 X 
                   
                   
                   
                   
                 X 
                 X 
               
               
                   
                 11th gear  
                 X 
                 X 
                   
                   
                   
                   
                 X 
               
               
                   
                 Idle 
                   
                   
                 X 
                 X 
               
               
                   
                 Reverse 
                 X 
                 X 
                   
                 X 
               
               
                   
                   
               
             
          
         
       
     
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Additional features and advantages of the present invention are derived from the following, specific description and the drawings. 
         FIG. 1  shows a first specific embodiment of a drive group of a transmission system according to the present invention; 
         FIG. 2  shows a second specific embodiment of a drive group of a transmission system according to the present invention; 
         FIG. 3  shows a third specific embodiment of a drive group of a transmission system according to the present invention; 
         FIG. 4  shows a first specific embodiment of an output group of a transmission system according to the present invention; 
         FIG. 5  shows a second specific embodiment of an output group of a transmission system according to the present invention; 
         FIG. 6  shows a third specific embodiment of an output group of a transmission system according to the present invention; 
         FIG. 7  shows a fourth specific embodiment of an output group of a transmission system according to the present invention; 
         FIG. 8  shows a fifth specific embodiment of an output group of a transmission system according to the present invention; and 
         FIG. 9  shows one specific embodiment of a transmission system according to the present invention, composed of one drive group according to  FIG. 1  and one output group according to  FIG. 4 . 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Identical reference numerals in the figures indicate identical or analogous elements. 
       FIGS. 1 through 3  show different specific embodiments of drive groups within a transmission system according to the present invention. 
       FIGS. 4 through 8  show different specific embodiments of output groups within a transmission system according to the present invention. 
       FIG. 9  shows, purely by way of example, a transmission system according to the present invention, composed of one drive group according to  FIG. 1  and one output group according to  FIG. 4 . Those skilled in the art will understand that each of the shown drive groups in combination with each of the shown output groups results in a transmission system according to the present invention. The graphic representation of each of the possible combinations may thus be dispensed with. The illustration according to  FIG. 9  shall suffice as a representative example. 
     The drive group according to  FIG. 1  includes two simple planetary gear sets, namely a first planetary gear set  10  and a second planetary gear set  20 . First planetary gear set  10  includes a first sun gear  101 , a first ring gear  102  and a first planet carrier  103 , on which a set of first planet gears is rotatably mounted, which mesh with first sun gear  101  on the one hand and with first ring gear  102  on the other hand. Second planetary gear set  20  includes a second sun gear  201 , a second ring gear  202  and a second planet carrier  203 , on which a set of second planet gears is rotatably mounted, which mesh with second sun gear  201  on the one hand and with second ring gear  202  on the other hand. Planetary gear sets  10 ,  20  are situated coaxially and axially adjoining each other. The input-side interface of the drive group is formed by the transmission input shaft. The output-side interface of the drive group is formed by two connecting shafts, namely first connecting shaft CON 1  and second connecting shaft CON 2 . 
     Input shaft  1  is connected to second sun gear  201 . The same is connected at the same time to second connecting shaft CON 2 , so that input shaft  1 , second sun gear  201  and second connecting shaft CON 2  together form the central shaft of the drive group. 
     This central shaft is shiftably coupled to second planet carrier  203  via a first clutch K 1 . At the same time, second planet carrier  203  is shiftably coupled to the housing via a first brake B 1 . Moreover, second planet carrier  203  is shiftably coupled to first ring gear  102  via a second clutch K 2 . First ring gear  102  is additionally connected to first connecting shaft CON 1 . 
     In addition to this shiftable coupling, a fixed coupling also exists between planetary gear sets  10 ,  20 , namely a connection between first planet carrier  103  and second ring gear  202 . First sun gear  101  is shiftably coupled to the housing via a second brake B 2 . In this configuration, the drive group according to  FIG. 1  may be used in combination with any of the output groups described hereafter to create a transmission system according to the present invention, in particular a 9-speed transmission according to the present invention. The connection of the groups takes place in each case via connecting shafts CON 1  and CON  2 , as is indicated by way of example in  FIG. 9 . 
     A further shiftable coupling, which is optionally provided within the scope of the present invention to implement an 11-speed transmission according to the present invention, is shown with a dashed line in  FIG. 1 . First planet carrier  103  is shiftably coupled to the housing with the aid of the brake referred to here as fourth brake B 4 . 
     The drive group according to  FIG. 2  represents a pure isomorphism to the drive group of  FIG. 1 . In particular, the axial sequence of planetary gear sets  10 ,  20  is inverted. All connections within the drive group correspond to those of the specific embodiment of  FIG. 1 , so that reference may be made to the description above. 
     Contrary to the specific embodiment of  FIG. 1 , the drive group according to  FIG. 3  has a fixed connection between second planet carrier  203  and first ring gear  102 . First brake B 1  shiftably couples first planet carrier  103  to the housing, while second brake B 2 , as is also the case in the specific embodiment according to  FIG. 1 , shiftably couples first sun gear  101  to the housing. First clutch K 1  shiftably couples first planet carrier  103  to second sun gear  201 . 
     Second clutch K 2  shiftably couples first planet carrier  103  to second ring gear  202 , which is fixedly connected to first connecting shaft CON 1 . As is also the case in the specific embodiment of  FIG. 1 , second connecting shaft CON 2  is connected to input shaft  1  and second sun gear  201 . In addition, reference may be made to the description above with respect to  FIG. 1 , an equivalent arrangement of a fourth brake B 4  not being possible in this specific embodiment due to the inaccessibility of the second planet carrier. 
       FIG. 4  shows a first specific embodiment of an output group, which may be connected to any of the drive groups of  FIGS. 1 through 3  to create a transmission system according to the present invention. The connection is created via connecting shafts CON 1  and CON 2 ; in each case first connecting shaft CON 1  of the drive group is to be connected to first connecting shaft CON 1  of the output group, and second connecting shaft CON 2  of the drive group is to be connected to second connecting shaft CON 2  of the output group. All other shown output groups are also based on this concept, so that each shown output group may be combined with each shown drive group to form a transmission system according to the present invention. 
     The output group according to  FIG. 4  includes a Ravigneaux planetary gear set  30  having a first Ravigneaux sun gear  311 , a second Ravigneaux sun gear  312 , a Ravigneaux ring gear  302  and a Ravigneaux planet carrier  303 . One set of short planet gears  331  and one set of long planet gears  332  are rotatably mounted on Ravigneaux planet carrier  303 . Long planet gears  332  are designed as stepped planet gears, having one larger stage, i.e., one stage having a larger diameter, and one smaller stage, i.e., one stage having a smaller diameter. In the specific embodiment shown in  FIG. 4 , short planetary gear set  331  meshes with the smaller stage of long planets gears  332 . First Ravigneaux sun gear  311 , which is shiftably coupled to the housing via a third brake B 3 , meshes with the set of short planet gears  331 . Second Ravigneaux sun gear  312 , which is fixedly connected to first connecting shaft CON 1 , meshes with the larger stage of long planet gears  332 . Ravigneaux ring gear  302  is fixedly connected to transmission output shaft  2 . A third clutch K 3  shiftably couples Ravigneaux planet carrier  303  to second connecting shaft CON 2 . In the shown specific embodiment, Ravigneaux planetary gear set  30  is oriented with its small long planet stage in the direction of the drive group. 
       FIG. 5  shows a second specific embodiment of an output group, which differs from that of  FIG. 4  only in that Ravigneaux ring gear  302  does not mesh with the larger, but with the smaller stage of long planet gears  332 . In addition, reference may be made to the description above with respect to  FIG. 4 . 
       FIG. 6  shows a third specific embodiment of an output group, in which Ravigneaux planetary gear set  30  is axially reversed, i.e., oriented with its larger long planet stage in the direction of the drive group. Correspondingly, first Ravigneaux sun gear  311  meshes with the larger long planet stage, and second Ravigneaux sun gear  312  meshes with short planet gears  331 . In this specific embodiment, Ravigneaux ring gear  302  also meshes with short planet gears  331 . In addition, reference may be made to the description above with respect to  FIG. 4 . 
       FIG. 7  shows a fourth specific embodiment of the output group, which differs from the specific embodiment shown in  FIG. 6  only in that, instead of Ravigneaux planet carrier  303 , Ravigneaux ring gear  302  is shiftably coupled to second connecting shaft CON 2  via third clutch K 3 . Correspondingly, Ravigneaux planet carrier  303 , instead of Ravigneaux ring gear  302 , is connected to output shaft  2  here. In this specific embodiment, Ravigneaux ring gear  302  meshes with the small stage of long planet gears  332 . 
       FIG. 8  shows a fifth specific embodiment of an output group, which differs from that of  FIG. 7  only in the point of contact of the Ravigneaux ring gear, which meshes with the large stage of long planet gears  332  here, instead of with the small stage. In addition, this specific embodiment corresponds to that of  FIG. 7 . 
       FIG. 9  shows a transmission system according to the present invention composed of one drive group according to  FIG. 1  and one output group according to  FIG. 4 , which is provided purely by way of example and representatively of all remaining combinations of drive and output groups, which those skilled in the art are able to readily carry out. In particular, connecting shafts CON 1  and CON 2  of the drive and output groups assigned to each other merely have to be connected to each other for such a combination. 
     Naturally, the specific embodiments discussed in the specific description and shown in the figures represent only illustrative exemplary embodiments of the present invention. In light of the present disclosure, those skilled in the art are provided with a wide range of variation options. 
     LIST OF REFERENCE NUMERALS 
       1  input shaft 
       2  output shaft 
       10  first planetary gear set 
       101  first sun gear 
       102  first ring gear 
       103  first planet carrier 
       20  second planetary gear set 
       201  second sun gear 
       202  second ring gear 
       203  second planet carrier 
       30  Ravigneaux planetary gear set 
       311  first Ravigneaux sun gear 
       312  second Ravigneaux sun gear 
       302  Ravigneaux ring gear 
       303  Ravigneaux planet carrier 
       331  short planet gears 
       332  long planet gears 
     B 1  first brake 
     B 2  second brake 
     B 3  third brake 
     B 4  fourth brake 
     K 1  first clutch 
     K 2  second clutch 
     K 3  third clutch 
     CON 1  first connecting shaft 
     CON 2  second connecting shaft

Technology Classification (CPC): 5