Patent Publication Number: US-2015065288-A1

Title: Multi-mode continuously variable transmission with transfer gear set

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims the benefit of U.S. Provisional Application No. 61/871,578 filed Aug. 29, 2013. The disclosure of the above application is incorporated herein by reference. 
    
    
     FIELD 
     The present disclosure relates to automatic transmissions and more particularly to a multi-mode continuously variable transmission having a transfer gear set. 
     BACKGROUND 
     The statements in this section merely provide background information related to the present disclosure and may or may not constitute prior art. 
     A continuously variable transmission (“CVT”) typically includes a belt and pulley system that operatively couples a rotary power source, such as an engine or electric motor, to a double gear final drive unit. The belt and pulley system generally includes first and second pairs of pulley cones having a torque transmitting belt or chain extending between the cone pairs. Each pulley cone pair includes an axially stationary pulley member and an axially movable pulley member. Each movable pulley member is axially adjustable with respect to the stationary pulley member by a hydraulic system. The hydraulic system provides primary and secondary hydraulic pressures to the respective movable pulley members to adjust the running radius of the first and second pulley cone pairs which in turn controls the output/input ratio of the continuously variable transmission. Movement of the cones steplessly or continuously varies the ratio of an input speed to an output speed. With the continuously variable transmission, small but effective ratio changes can be attained. This is in contrast to a fixed gear ratio unit where any ratio changes are step values. 
     CVT axial length and mass significantly impact its power density and efficiency. CVT designs that reduce the number of axes of rotation may be particularly desirable in certain configurations. Accordingly, there is a constant need for improved CVT designs that minimize axial length and mass while providing sufficient performance characteristics and having a minimized number of axes of rotation. 
     SUMMARY 
     A multi-mode CVT is provided for a motor vehicle. The multi-mode CVT includes a transfer gear set or speed change device connected to a pulley and belt assembly. The pulley and belt assembly is also connected to a planetary gear set arrangement. The planetary gear set arrangement generally includes two planetary gear sets, two brakes, and one clutch. The planetary gear set arrangement is connected to a final drive unit. 
     For example, in one aspect of the present invention a transmission for a motor vehicle includes a transmission input member, a transmission output member, a transfer gear set having a first transfer member connected for common rotation with the transmission input member and having a second transfer member in mesh with the first transfer member, a continuously variable unit having a first pulley connected for common rotation with the second transfer member of the transfer gear, a second pulley, and an endless member wrapped around the first pulley and the second pulley, a first planetary gear set having a plurality of members, a second planetary gear set having a plurality of members, wherein the second planetary gear set is connected for common rotation to the first planetary gear set, the second pulley, and the transmission output member, a clutch for selectively connecting for common rotation the first planetary gear set to the second planetary gear set, a first brake for selectively connecting the first planetary gear set to a stationary member, and a second brake for selectively connecting the second planetary gear set to the stationary member. Selective engagement of the clutch, first brake, second brake, and selective movement of the first pulley and second pulley provides two forward ranges of continuous gear ratios between the transmission input member and the transmission output member. 
     In another aspect of the present invention, the first planetary gear set includes a first member, a second member, and a third member and the second planetary gear set includes a first member, a second member, and a third member, wherein the first member of the first planetary gear set is connected for common rotation with the second member of the second planetary gear set, and the second member of the first planetary gear set is connected for common rotation with the third member of the second planetary gear set. 
     In yet another aspect of the present invention, the first member of the second planetary gear set is connected for common rotation with the second pulley and the second member of the first planetary gear set and the third member of the second planetary gear set are connected for common rotation with the transmission output member. 
     In yet another aspect of the present invention, the clutch selectively connects for common rotation the first member of the first planetary gear set and the second member of the second planetary gear set to the second member of the first planetary gear set and the third member of the second planetary gear set. 
     In yet another aspect of the present invention, the first brake selectively connects the first member of the first planetary gear set and the second member of the second planetary gear set to the stationary member. 
     In yet another aspect of the present invention, the second brake selectively connects the third member of the first planetary gear set to the stationary member. 
     In yet another aspect of the present invention, the first member of the first planetary gear set and the second member of the second planetary gear set are integrally formed as a single rotating member. 
     In yet another aspect of the present invention, the second member of the first planetary gear set and the third member of the second planetary gear set are integrally formed as a single rotating member. 
     In yet another aspect of the present invention, the first member of the first planetary gear set is a ring gear, the second member of the first planetary gear set is a planet carrier member, the third member of the first planetary gear set is a sun gear, the first member of the second planetary gear set is a sun gear, the second member of the second planetary gear set is a ring gear, and the third member of the second planetary gear set is a planet carrier member. 
     In yet another aspect of the present invention, the second member of the first planetary gear set and the third member of the second planetary gear set both support a plurality of stepped pinions and a plurality of pinions, wherein each of the plurality of stepped pinions have a first portion in mesh with the third member of the first planetary gear set and a second portion in mesh with the integrally formed first member of the first planetary gear set and the second member of the second planetary gear set and in mesh with the plurality of pinions, and wherein the plurality of pinions are in mesh with the first member of the second planetary gear set. 
     In yet another aspect of the present invention, the first gear member is co-planar with the second gear set. 
     In yet another aspect of the present invention, a rotating member is directly connected with the second transfer member and the second planetary gear set, and wherein the transfer gear set is an overdrive transfer gear set that increases a speed and decreases a torque of the rotating member relative to the transmission input member. 
     In yet another aspect of the present invention, the transfer gear set is an underdrive transfer gear set that decreases a speed and increases a torque of the rotating member relative to the transmission input member. 
     In yet another aspect of the present invention, the transfer gear set is a direct drive transfer gear set that maintains a speed and a torque of the rotating member relative to the transmission input member. 
     Further areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure. 
    
    
     
       DRAWINGS 
       The drawings described herein are for illustration purposes only and is not intended to limit the scope of the present disclosure in any way. 
         FIG. 1  is a schematic diagram of a powertrain according to the principles of the present invention; 
         FIG. 2A  is a schematic lever diagram of an exemplary transmission according to the principles of the present invention; 
         FIG. 2B  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 2C  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 2D  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 2E  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 2F  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 3A  is a diagrammatic illustration of an embodiment of a transmission according to the principles of the present invention; 
         FIG. 3B  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 3C  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 3D  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 3E  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 3F  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 4A  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 4B  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 4C  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 4D  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 4E  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 4F  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 5A  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 5B  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 5C  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 5D  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 5E  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 5F  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 6A  is a schematic lever diagram of an exemplary transmission according to the principles of the present invention; 
         FIG. 6B  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 6C  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 6D  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 6E  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 6F  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 7A  is a diagrammatic illustration of an embodiment of a transmission according to the principles of the present invention; 
         FIG. 7B  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 7C  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 7D  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 7E  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 7F  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 8A  is a schematic lever diagram of an exemplary transmission according to the principles of the present invention; 
         FIG. 8B  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 8C  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 8D  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 8E  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 8F  is a schematic lever diagram of another exemplary transmission according to the principles of the present invention; 
         FIG. 9A  is a diagrammatic illustration of an embodiment of a transmission according to the principles of the present invention; 
         FIG. 9B  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 9C  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 9D  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; 
         FIG. 9E  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention; and 
         FIG. 9F  is a diagrammatic illustration of another embodiment of a transmission according to the principles of the present invention. 
     
    
    
     DETAILED DESCRIPTION 
     The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. 
     With reference to  FIG. 1 , a powertrain for a motor vehicle is generally indicated by reference number  10 . The powertrain  10  generally includes an engine  12  interconnected with a transmission  14 . The engine  12  may be a conventional gasoline, Diesel, or flex fuel internal combustion engine, a hybrid engine, or an electric motor, or any other type of prime mover, without departing from the scope of the present disclosure. The engine  12  supplies a driving torque to the transmission  14  through, for example, a flexplate (not shown) or other connecting device or a starting device  15  such as a hydrodynamic device or launch clutch. 
     The transmission  14  is a variable diameter pulley or sheave drive continuously variable transmission (CVT). The transmission  14  includes a typically cast, metal housing  16  which encloses and protects the various components of the transmission  14 . The housing  16  includes a variety of apertures, passageways, shoulders and flanges which position and support these components. Generally speaking, the transmission  14  includes a transmission input shaft  20  and a transmission output shaft  22 . Connected between the transmission input shaft  20  and the transmission output shaft  22  is a transfer gear set  23 , a pulley assembly  24 , and a gearbox  26  that cooperate to provide forward and reverse speed or gear ratios between the transmission input shaft  20  and the transmission output shaft  22 . The transmission input shaft  20  is functionally interconnected with the engine  12  through the starting device  15  and receives input torque or power from the engine  12 . The transmission output shaft  22  is preferably connected with a final drive unit  28 . The transmission output shaft  22  provides drive torque to the final drive unit  28 . The final drive  28  unit may include a differential, axle shafts, and road wheels (not shown). 
     The transmission input shaft  20  is connected to the transfer gear set  23 . The transfer gear set  23 , as well as the various gearbox  26  arrangements described below, are illustrated in a lever diagram format. A lever diagram is a schematic representation of the components of a mechanical device such as meshing gear sets or planetary gear sets. Each individual lever represents a planetary gear set or meshed gear pair. The three basic mechanical components of the planetary gear are each represented by a node while the gear pairs are represented by a node and the rotation change represented by a node fixed to ground. Therefore, a single lever contains three nodes. In a planetary gear set, one node represents the sun gear, one the planet gear carrier, and one the ring gear. In a meshed gear pair, one node represents a first gear, one a second gear, and the third the rotational direction change between the meshed gears. In some cases, two levers may be combined into a single lever having more than three nodes (typically four nodes). For example, if two nodes on two different levers are interconnected through a fixed connection they may be represented as a single node on a single lever. The relative length between the nodes of each lever can be used to represent the ring-to-sun ratio of each respective gear set. These lever ratios, in turn, are used to vary the gear ratios of the transmission in order to achieve an appropriate ratios and ratio progression. Mechanical couplings or interconnections between the nodes of the various planetary gear sets are illustrated by thin, horizontal lines and torque transmitting devices such as clutches and brakes are presented as interleaved fingers. Further explanation of the format, purpose and use of lever diagrams can be found in SAE Paper 810102, “The Lever Analogy: A New Tool in Transmission Analysis” by Benford and Leising which is hereby fully incorporated by reference. 
     For example, the transfer gear set  23  includes a first node  23 A, a second node  23 B, and a third node  23 C. The first node  23 A is coupled to the transmission input shaft  20 . The second node  23 B is fixed to ground representing a change in rotational direction. The third node  23 C is coupled to a first transfer shaft or rotating member  29  that is connected to the pulley assembly  24 . The first node  23 A preferably represents a first gear while the third node  23 C preferably represents a second gear meshed with the first gear. The gears may be co-planar or partially axially offset. In a preferred embodiment, the transfer gear set  23  is an overdrive transfer gear set  23  that increases the speed of the first transfer shaft  29  relative to the transmission input  20  while decreasing the torque. In a second preferred embodiment, the transfer gear set  23  is an underdrive transfer gear set  23 . In a third preferred embodiment, the transfer gear set  23  acts as a direct drive coupling member with no relative speed change. 
     The pulley assembly  24  includes a first pulley or sheave pair  30  and a second pulley or sheave pair  32 . The first pulley  30  includes a first truncated conical sheave or member  30 A and second truncated conical sheave or member  30 B in axial alignment with the first truncated conical sheave  30 A. The second sheave  30 B is directly connected for rotation with the first transfer member  29  and may be integrally formed with the first transfer member  29 . The first sheave  30 A is moveable axially relative to the second sheave  30 B by a hydraulic control system (not shown) or other actuating system. It should be appreciated that the sheaves  30 A and  30 B may be axially switched without departing from the scope of the present invention. 
     The second pulley  32  includes a first truncated conical sheave or member  32 A and second truncated conical sheave or member  32 B in axial alignment with the first truncated conical sheave  32 A. The second sheave  32 B is directly connected for rotation with a second transfer shaft or member  34  or may be integrally formed with the second transfer shaft  34 . The first sheave  32 A is moveable axially relative to the second sheave  32 B by a hydraulic control system (not shown) or other actuating system. It should be appreciated that the sheaves  32 A and  32 B may be axially switched without departing from the scope of the present invention. 
     A torque transmitting belt or chain  36  having a V-shaped cross section is mounted between the first pulley pair  30  and the second pulley pair  32 . It should be appreciated that other types of belts, including positive engagement devices, may be employed without departing from the scope of the present invention. Drive torque communicated from the transmission input shaft  20  is transferred via friction between the sheaves  30 A and  30 B and the belt  36 . The ratio of the input pulley  30  to the output pulley  32  is adjusted by varying the spacing between the sheaves  30 A and  30 B and between the sheaves  32 A and  32 B. For example, to change the ratio between the pulleys  30  and  32 , the axial distance between sheaves  30 A and  30 B may be reduced by moving sheave  30 A towards sheave  32 B while simultaneously the axial distance between sheave  32 A and  32 B may be increased by moving sheave  32 A away from sheave  32 B. Due to the V-shaped cross section of the belt  36 , the belt  36  rides higher on the first pulley  30  and lower on the second pulley  32 . Therefore the effective diameters of the pulleys  30  and  32  change, which in turn changes the overall gear ratio between the first pulley  30  and the second pulley  32 . Since the radial distance between the pulleys  30  and  32  and the length of the belt  36  is constant, the movement of the sheaves  30 A and  32 A must occur simultaneously in order to maintain the proper amount of tension on the belt  36  to assure torque is transferred from the pulleys  30 ,  32  to the belt  36 . 
     The pulley assembly  24  transfers torque to the gearbox  26  via the second transfer shaft  34 . The gearbox  26  comprises one of several planetary gear set transmissions or arrangements, as will be described in greater detail below. The gearbox  26  outputs torque from the pulley assembly  26  to the transmission output shaft  22  and then to the final drive unit  28 . 
     Turning now to  FIGS. 2A-F , various configurations of the gearbox  26  are shown in lever diagram format. The gearboxes illustrated in  FIGS. 2A-F  include specific types of transmissions known as Ravigneaux, powerglide, and ring-carrier and ring-carrier levers, as will be described below. The gearbox  26  includes a first planetary gear set  50  and a second planetary gear set  52 . The first planetary gear set  50  has three nodes: a first node  50 A, a second node  50 B and a third node  50 C. The second planetary gear set  52  has three nodes: a first node  52 A, a second node  52 B and a third node  52 C. 
     The second transfer member  34  is continuously coupled to the first node  52 A of the second planetary gear set  52 . The transmission output member  22  is coupled to the third node  52 C of the second planetary gear set  52 . The first node  50 A of the first planetary gear set  50  is coupled to the second node  52 B of the second planetary gear set  52 . The second node  50 B of the first planetary gear set  50  is coupled to the third node  52 C of the second planetary gear set  52 . 
     A first brake  54  selectively connects the second node  52 B of the second planetary gear set  52  and the first node  50 A of the first planetary gear set  50  with a stationary element or transmission housing  16 . A second brake  56  selectively connects the third node  50 C of the first planetary gear set  50  with the stationary element or transmission housing  16 . A first clutch  58  selectively connects the first node  50 A of the first planetary gear set  50  and the second node  52 B of the second planetary gear set  52  with the third node  50 C of the first planetary gear set  50 . 
     With reference to  FIG. 2B , an alternate gearbox arrangement  26 B is shown. The gearbox  26 B is similar to that shown in  FIG. 2A  and therefore like components are indicated by like reference numbers. However, in  FIG. 2B , the first clutch  58  is relocated and selectively connects the first node  50 A of the first planetary gear set  50  and the second node  52 B of the second planetary gear set  52  with the second node  50 B of the first planetary gear set  50  and the third node  52 C of the second planetary gear set  52 . 
     With reference to  FIG. 2C , an alternate gearbox arrangement  26 C is shown. The gearbox  26 C is similar to that shown in  FIG. 2A  and therefore like components are indicated by like reference numbers. However, in  FIG. 2C , the first clutch  58  is relocated and selectively connects the second node  50 B of the first planetary gear set  50  and the third node  52 C of the second planetary gear set  52  with the third node  50 C of the first planetary gear set  50 . 
     With reference to  FIG. 2D , an alternate gearbox arrangement  26 D is shown. The gearbox  26 D is similar to that shown in  FIG. 2A  and therefore like components are indicated by like reference numbers. However, in  FIG. 2D , the first clutch  58  is relocated and selectively connects the first node  50 A of the first planetary gear set  50  and the second node  52 B of the second planetary gear set  52  with the first node  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 2E , an alternate gearbox arrangement  26 E is shown. The gearbox  26 E is similar to that shown in  FIG. 2A  and therefore like components are indicated by like reference numbers. However, in  FIG. 2E , the first clutch  58  is relocated and selectively connects the second node  50 B of the first planetary gear set  50  and the third node  52 C of the second planetary gear set  52  with the first node  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 2F , an alternate gearbox arrangement  26 F is shown. The gearbox  26 F is similar to that shown in  FIG. 2A  and therefore like components are indicated by like reference numbers. However, in  FIG. 2F , the first clutch  58  is relocated and selectively connects the first node  52 A of the second planetary gear set  52  with the third node  50 C of the first planetary gear set  50 . 
     Turning now to  FIGS. 3A-F  stick diagrams present schematic layouts of embodiments of the gearbox  26 ,  26 B-F according to the present invention. In  FIGS. 3A-F  the numbering from the lever diagram of  FIGS. 2A-F  are carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers. 
     For example, the transfer gear set  23  includes a first gear  23 A meshed with a second gear  23 C while the gear sets  50  and  52  include a common planet carrier member  50 B/ 52 C, a ring gear member  50 A, a sun gear member  50 C, and a sun gear member  52 A. It should be appreciated that ring gear member  52 B is optional and not shown. The common planet carrier member  50 B/ 52 C rotatably supports a set of planet gears  50 D (only one of which is shown) and  52 D (only one of which is shown). The planet gears  50 D are each configured to intermesh with the ring gear member  50 A while the planet gears  52 D are long pinions that each intermesh with both the planet gears  50 D and the sun gear member  52 A. The sun gear member  50 C is connected for common rotation with a first shaft or interconnecting member  60 . The sun gear member  52 A is connected for common rotation with the second transfer member  34 . The planet carrier member  50 B/ 52 C is connected for common rotation with the transmission output shaft  22 . The ring gear member  50 A is connected for common rotation with a second shaft or interconnecting member  62 . 
     The torque-transmitting mechanisms or brakes  54 ,  56  and clutch  58  allow for selective interconnection of the shafts or interconnecting members, members of the planetary gear sets and the housing. The torque-transmitting mechanisms are friction, dog or synchronizer type mechanisms or the like. For example, the first brake  54  is selectively engageable to connect the second shaft or interconnecting member  62  with the transmission housing  14  in order to restrict relative rotation of the member  62  and therefore the ring gear member  50 A. The second brake  56  is selectively engageable to connect the first shaft or interconnecting member  60  with the transmission housing  14  in order to restrict relative rotation of the member  60  and therefore the sun gear member  50 C. In  FIG. 3A , the clutch  58  is selectively engageable to connect the ring gear member  50 A with the sun gear member  50 C. 
     Likewise,  FIGS. 3B-3F  illustrate stick diagrams of the corresponding gearbox arrangements  26 B- 26 F which alter the location of the clutch  58 , as described above. With reference to  FIG. 3B , an alternate gearbox arrangement  26 B is shown. The gearbox  26 B is similar to that shown in  FIG. 3A  and therefore like components are indicated by like reference numbers. However, in  FIG. 3B , the first clutch  58  is relocated and selectively connects the ring gear  50 A with the carrier member  50 B/ 52 C. 
     With reference to  FIG. 3C , an alternate gearbox arrangement  26 C is shown. The gearbox  26 C is similar to that shown in  FIG. 3A  and therefore like components are indicated by like reference numbers. However, in  FIG. 3C , the first clutch  58  is relocated and selectively connects the carrier member  50 B/ 52 C with the sun gear  50 C of the first planetary gear set  50 . 
     With reference to  FIG. 3D , an alternate gearbox arrangement  26 D is shown. The gearbox  26 D is similar to that shown in  FIG. 3A  and therefore like components are indicated by like reference numbers. However, in  FIG. 3D , the first clutch  58  is relocated and selectively connects the ring gear  50 A with the sun gear  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 3E , an alternate gearbox arrangement  26 E is shown. The gearbox  26 E is similar to that shown in  FIG. 3A  and therefore like components are indicated by like reference numbers. However, in  FIG. 3E , the first clutch  58  is relocated and selectively connects the carrier member  50 B/ 52 C with the sun gear  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 3F , an alternate gearbox arrangement  26 F is shown. The gearbox  26 F is similar to that shown in  FIG. 3A  and therefore like components are indicated by like reference numbers. However, in  FIG. 3F , the first clutch  58  is relocated and selectively connects the sun gear  52 A of the second planetary gear set  52  with the sun gear  50 C of the first planetary gear set  50 . 
     Turning now to  FIGS. 4A-F  stick diagrams present schematic layouts of Ravigneaux type embodiments of the gearbox  26 ,  26 B-F according to the present invention. In  FIGS. 4A-F  the numbering from the lever diagram of  FIGS. 2A-F  are carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers. 
     For example, the planetary gear set  50  is configured as a simple planetary gear set while planetary gear set  52  is a compound planetary gear set. These gear sets are connected either as separate gear sets or as a single planetary gear set arrangement. The gear sets  50  and  52  include a common planet carrier member  50 B/ 52 C, a common ring gear member  50 A/ 52 B, a sun gear member  50 C, and a sun gear member  52 A. The common planet carrier member  50 B/ 52 C rotatably supports a set of planet gears  50 D (only one of which is shown) and  52 D (only one of which is shown). The planet gears  50 D are stepped pinions having a first stepped portion  51  and a second stepped portion  53 . The stepped portions  51  of the planet gears  50 D are each configured to intermesh with sun gears  50 C. The stepped portions  53  of the planet gears  50 D are each configured to intermesh with both the ring gear member  50 A/ 52 B and the non-stepped pinions  52 D. The planet gears  52 D each intermesh with both the stepped portions  53  of the planet gears  50 D and the sun gear member  52 A. The sun gear member  50 C is connected for common rotation with a first shaft or interconnecting member  60 . The sun gear member  52 A is connected for common rotation with the transfer member  34 . The planet carrier member  50 B/ 52 C is connected for common rotation with the transmission output shaft  22 . The ring gear member  50 A/ 52 B is connected for common rotation with a second shaft or interconnecting member  62 . 
     The first brake  54  is selectively engageable to connect the second shaft or interconnecting member  62  with the transmission housing  14  in order to restrict relative rotation of the member  62  and therefore the ring gear member  50 A/ 52 B. The second brake  56  is selectively engageable to connect the first shaft or interconnecting member  60  with the transmission housing  14  in order to restrict relative rotation of the member  60  and therefore the sun gear member  50 C. In  FIG. 4A , the clutch  58  is selectively engageable to connect the ring gear member  50 A/ 52 B with the sun gear member  50 C. 
     Likewise,  FIGS. 4B-4F  illustrate stick diagrams of the corresponding gearbox arrangements  26 B- 26 F which alter the location of the clutch  58 , as described above. With reference to  FIG. 4B , an alternate gearbox arrangement  26 B is shown. The gearbox  26 B is similar to that shown in  FIG. 4A  and therefore like components are indicated by like reference numbers. However, in  FIG. 4B , the first clutch  58  is relocated and selectively connects the ring gear  50 A/ 52 B with the carrier member  50 B/ 52 C. 
     With reference to  FIG. 4C , an alternate gearbox arrangement  26 C is shown. The gearbox  26 C is similar to that shown in  FIG. 4A  and therefore like components are indicated by like reference numbers. However, in  FIG. 4C , the first clutch  58  is relocated and selectively connects the carrier member  50 B/ 52 C with the sun gear  50 C of the first planetary gear set  50 . 
     With reference to  FIG. 4D , an alternate gearbox arrangement  26 D is shown. The gearbox  26 D is similar to that shown in  FIG. 4A  and therefore like components are indicated by like reference numbers. However, in  FIG. 4D , the first clutch  58  is relocated and selectively connects the ring gear  50 A/ 52 B with the sun gear  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 4E , an alternate gearbox arrangement  26 E is shown. The gearbox  26 E is similar to that shown in  FIG. 4A  and therefore like components are indicated by like reference numbers. However, in  FIG. 4E , the first clutch  58  is relocated and selectively connects the carrier member  50 B/ 52 C with the sun gear  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 4F , an alternate gearbox arrangement  26 F is shown. The gearbox  26 F is similar to that shown in  FIG. 4A  and therefore like components are indicated by like reference numbers. However, in  FIG. 4F , the first clutch  58  is relocated and selectively connects the sun gear  52 A of the second planetary gear set  52  with the sun gear  50 C of the first planetary gear set  50 . 
     Turning now to  FIGS. 5A-F  stick diagrams present schematic layouts of embodiments of the gearbox  26 ,  26 B-F according to the present invention. In  FIGS. 5A-F  the numbering from the lever diagram of  FIGS. 2A-F  are carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers. 
     For example, the planetary gear set  50  includes a sun gear member  50 C, a ring gear member  50 A, and a planet carrier member  50 B that rotatable supports a set of planet gears  50 D (only one of which is shown). The planet gears  50 D are each configured to intermesh with both the sun gear member  50 C and the ring gear member  50 A. The sun gear member  50 C is connected for common rotation with the first shaft or interconnecting member  60 . The ring gear member  50 A is connected for common rotation with the second shaft or interconnecting member  62 . The planet carrier member  50 B is connected for common rotation with the transmission output shaft  22 . 
     The planetary gear set  52  includes a sun gear member  52 A, a ring gear member  52 C, and a planet carrier member  52 B that rotatable supports a set of planet gears  52 D (only one of which is shown). The planet gears  52 D are each configured to intermesh with both the sun gear member  52 A and the ring gear member  52 C. The sun gear member  52 A is connected for common rotation with the transfer member  34 . The ring gear member  52 C is connected for common rotation with the transmission output member  22 . The planet carrier member  52 B is connected for common rotation with the second interconnecting member  62 . 
     The first brake  54  is selectively engageable to connect the second shaft or interconnecting member  62  with the transmission housing  14  in order to restrict relative rotation of the member  62  and therefore the ring gear member  50 A and the carrier member  52 B. The second brake  56  is selectively engageable to connect the first shaft or interconnecting member  60  with the transmission housing  14  in order to restrict relative rotation of the member  60  and therefore the sun gear member  50 C. In  FIG. 5A , the clutch  58  is selectively engageable to connect the ring gear member  50 A and the carrier member  52 B with the sun gear member  50 C. 
     Likewise,  FIGS. 5B-4F  illustrate stick diagrams of the corresponding gearbox arrangements  26 B- 26 F which alter the location of the clutch  58 , as described above. With reference to  FIG. 5B , an alternate gearbox arrangement  26 B is shown. The gearbox  26 B is similar to that shown in  FIG. 5A  and therefore like components are indicated by like reference numbers. However, in  FIG. 5B , the first clutch  58  is relocated and selectively connects the ring gear  50 A and carrier member  52 B with the carrier member  50 B and the ring gear  52 C. 
     With reference to  FIG. 5C , an alternate gearbox arrangement  26 C is shown. The gearbox  26 C is similar to that shown in  FIG. 5A  and therefore like components are indicated by like reference numbers. However, in  FIG. 5C , the first clutch  58  is relocated and selectively connects the carrier member  50 B and the ring gear  52 C with the sun gear  50 C of the first planetary gear set  50 . 
     With reference to  FIG. 5D , an alternate gearbox arrangement  26 D is shown. The gearbox  26 D is similar to that shown in  FIG. 5A  and therefore like components are indicated by like reference numbers. However, in  FIG. 5D , the first clutch  58  is relocated and selectively connects the ring gear  50 A and the carrier member  52 B with the sun gear  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 5E , an alternate gearbox arrangement  26 E is shown. The gearbox  26 E is similar to that shown in  FIG. 5A  and therefore like components are indicated by like reference numbers. However, in  FIG. 5E , the first clutch  58  is relocated and selectively connects the carrier member  50 B and ring gear  52 C with the sun gear  52 A of the second planetary gear set  52 . 
     With reference to  FIG. 5F , an alternate gearbox arrangement  26 F is shown. The gearbox  26 F is similar to that shown in  FIG. 5A  and therefore like components are indicated by like reference numbers. However, in  FIG. 5F , the first clutch  58  is relocated and selectively connects the sun gear  52 A of the second planetary gear set  52  with the sun gear  50 C of the first planetary gear set  50 . 
     Turning now to  FIGS. 6A-F , another set of configurations of the gearbox  26  are shown in lever diagram format. The gearboxes illustrated in  FIGS. 6A-F  include specific types of transmissions known as stacked planetary gear sets, as will be described below. For example, the gearbox  26 G includes a first planetary gear set  70  and a second planetary gear set  72 . The first planetary gear set  70  has three nodes: a first node  70 A, a second node  70 B and a third node  70 C. The second planetary gear set  72  has three nodes: a first node  72 A, a second node  72 B and a third node  72 C. 
     The transfer member  34  is continuously coupled to the third node  70 C of the first planetary gear set  70  or to the third node  72 C of the second planetary gear set  72 . The transmission output member  22  is coupled to the first node  72 A of the second planetary gear set  72 . The second node  70 B of the first planetary gear set  70  is coupled to the second node  72 B of the second planetary gear set  72 . The third node  70 C of the first planetary gear set  70  is coupled to the third node  72 C of the second planetary gear set  72 . 
     A first brake  74  selectively connects the second node  70 B of the first planetary gear set  70  and the second node  72 B of the second planetary gear set  72  with a stationary member or transmission housing  14 . A second brake  76  selectively connects the first node  70 A of the first planetary gear set  70  with the stationary member or transmission housing  14 . A first clutch  78  selectively connects the third node  70 C of the first planetary gear set  70  and the third node  72 C of the second planetary gear set  72  with the first node  72 A of the second planetary gear set  72  and the transmission output member  22 . 
     With reference to  FIG. 6B , an alternate gearbox arrangement  26 H is shown. The gearbox  26 H is similar to that shown in  FIG. 6A  and therefore like components are indicated by like reference numbers. However, in  FIG. 6B , the first clutch  78  is relocated and selectively connects the second node  70 B of the first planetary gear set  70  and the second node  72 B of the second planetary gear set  72  with the first node  72 A of the second planetary gear set  72  and the transmission output member  22   
     With reference to  FIG. 6C , an alternate gearbox arrangement  26 I is shown. The gearbox  26 I is similar to that shown in  FIG. 6A  and therefore like components are indicated by like reference numbers. However, in  FIG. 6C , the first clutch  78  is relocated and selectively the second node  70 B of the first planetary gear set  70  and the second node  72 B of the second planetary gear set  72  with the third node  70 C of the first planetary gear set  70  and the third node  72 C of the second planetary gear set  72 . 
     With reference to  FIG. 6D , an alternate gearbox arrangement  26 J is shown. The gearbox  26 J is similar to that shown in  FIG. 6A  and therefore like components are indicated by like reference numbers. However, in  FIG. 6D , the first clutch  78  is relocated and selectively connects the second node  70 B of the first planetary gear set  70  and the second node  72 B of the second planetary gear set  72  with the first node  70 A of the first planetary gear set  70 . 
     With reference to  FIG. 6E , an alternate gearbox arrangement  26 K is shown. The gearbox  26 K is similar to that shown in  FIG. 6A  and therefore like components are indicated by like reference numbers. However, in  FIG. 6E , the first clutch  78  is relocated and selectively connects first node  70 A of the first planetary gear set  70  with the first node  72 A of the second planetary gear set  72 . 
     With reference to  FIG. 6F , an alternate gearbox arrangement  26 L is shown. The gearbox  26 L is similar to that shown in  FIG. 6A  and therefore like components are indicated by like reference numbers. However, in  FIG. 6F , the first clutch  78  is relocated and selectively connects the first node  70 A of the first planetary gear set  70  with the third node  70 C of the first planetary gear set and the third node  72 C of the second planetary gear set  72 . 
     Turning now to  FIGS. 7A-F , stick diagrams present schematic layouts of embodiments of the gearbox  26 G-L according to the present invention. In  FIGS. 7A-F  the numbering from the lever diagram of  FIGS. 6A-F  are carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers. 
     For example, the planetary gear set  70  and the planetary gear set  72  are configured as a stacked planetary gear set wherein the first planetary gear set  70  is nested radially inward of the second planetary gear set  72 . The planetary gear set  70  includes a sun gear member  70 A, a ring gear member  70 C, and a planet carrier member  70 B that rotatably supports a set of planet gears  70 D (only one of which is shown). The planet gears  70 D are each configured to intermesh with both the sun gear member  70 A and the ring gear member  70 C. The sun gear member  70 A is connected for common rotation with a first shaft or interconnecting member  80 . The ring gear member  70 C is connected for common rotation with the transfer member  34 . The planet carrier member  70 B is connected for common rotation with a second shaft or interconnecting member  82 . 
     The planetary gear set  72  includes a sun gear member  72 C, a ring gear member  72 A, and a planet carrier member  72 B that rotatably supports a set of planet gears  72 D (only one of which is shown). The planet gears  72 D are each configured to intermesh with both the sun gear member  72 C and the ring gear member  72 A. The sun gear member  72 C is connected for common rotation with the first shaft or interconnecting member  34 . The ring gear member  72 A is connected for common rotation with the transmission output member  22 . The planet carrier member  72 B is connected for common rotation with the second shaft or interconnecting member  82 . It should be appreciated that the ring gear member  70 C of the first planetary gear set  70  and the sun gear member  72 C of the second planetary gear set  72  may be formed from a single unitary member having inner and outer gear teeth or from separate gears connected together for rotation. 
     The torque-transmitting mechanisms or brakes  74 ,  76  and clutch  78  allow for selective interconnection of the shafts or interconnecting members, members of the planetary gear sets and the housing. The torque-transmitting mechanisms are friction, dog or synchronizer type mechanisms or the like. For example, the first brake  74  is selectively engageable to connect the second shaft or interconnecting member  82  with the transmission housing  14  in order to restrict relative rotation of the member  82  and therefore the carrier member  70 B of the first planetary gear set  70  and the carrier member  72 B of the second planetary gear set  72 . The second brake  76  is selectively engageable to connect the first shaft or interconnecting member  80  with the transmission housing  14  in order to restrict relative rotation of the member  80  and therefore the sun gear member  70 A. In  FIG. 7A , the clutch  78  is selectively engageable to connect the ring gear member  72 A and the transmission output shaft  22  with the transfer shaft  34  and the ring gear member  70 C and sun gear member  72 C. 
     Likewise,  FIGS. 7B-3F  illustrate stick diagrams of the corresponding gearbox arrangements  26 H- 26 L which alter the location of the clutch  78 , as described above. With reference to  FIG. 7B , an alternate gearbox arrangement  26 H is shown. The gearbox  26 H is similar to that shown in  FIG. 7A  and therefore like components are indicated by like reference numbers. However, in  FIG. 7B , the first clutch  78  is relocated and selectively connects the carrier member  70 B of the first planetary gear set  70  and the carrier member  72 B of the second planetary gear set  72  with the ring gear  72 A of the second planetary gear set  72  and the transmission output member  22   
     With reference to  FIG. 7C , an alternate gearbox arrangement  26 I is shown. The gearbox  26 I is similar to that shown in  FIG. 7A  and therefore like components are indicated by like reference numbers. However, in  FIG. 7C , the first clutch  78  is relocated and selectively connects the carrier member  70 B of the first planetary gear set  70  and the carrier member  72 B of the second planetary gear set  72  with the ring gear  70 C of the first planetary gear set  70  and the sun gear  72 C of the second planetary gear set  72 . 
     With reference to  FIG. 7D , an alternate gearbox arrangement  26 J is shown. The gearbox  26 J is similar to that shown in  FIG. 7A  and therefore like components are indicated by like reference numbers. However, in  FIG. 7D , the first clutch  78  is relocated and selectively connects the carrier member  70 B of the first planetary gear set  70  and the carrier member  72 B of the second planetary gear set  72  with the sun gear  70 A of the first planetary gear set  70 . 
     With reference to  FIG. 7E , an alternate gearbox arrangement  26 K is shown. The gearbox  26 K is similar to that shown in  FIG. 7A  and therefore like components are indicated by like reference numbers. However, in  FIG. 7E , the first clutch  78  is relocated and selectively connects sun gear  70 A of the first planetary gear set  70  with the ring gear  72 A of the second planetary gear set  72 . 
     With reference to  FIG. 7F , an alternate gearbox arrangement  26 L is shown. The gearbox  26 L is similar to that shown in  FIG. 7A  and therefore like components are indicated by like reference numbers. However, in  FIG. 7F , the first clutch  78  is relocated and selectively connects the sun gear  70 A of the first planetary gear set  70  with the ring gear  70 C of the first planetary gear set and the sun gear  72 C of the second planetary gear set  72 . 
     Turning now to  FIGS. 8A-F , another set of configurations of the gearbox  26  are shown in lever diagram format. The gearboxes illustrated in  FIGS. 8A-F  include specific types of transmissions known as Simpson planetary gear sets, as will be described below. For example, the gearbox  26 M includes a first planetary gear set  90  and a second planetary gear set  92 . The first planetary gear set  90  has three nodes: a first node  90 A, a second node  90 B and a third node  90 C. The second planetary gear set  92  has three nodes: a first node  92 A, a second node  92 B and a third node  92 C. 
     The transfer member  34  is continuously coupled to the third node  90 C of the first planetary gear set  90 . The transmission output member  22  is coupled to the second node  92 B of the second planetary gear set  92 . The first node  90 A of the first planetary gear set  90  is coupled to the first node  92 A of the second planetary gear set  92 . The second node  90 B of the first planetary gear set  90  is coupled to the third node  92 C of the second planetary gear set  92 . 
     A first brake  94  selectively connects the second node  90 B of the first planetary gear set  90  and the third node  92 C of the second planetary gear set  92  with a stationary member or transmission housing  14 . A second brake  96  selectively connects the first node  90 A of the first planetary gear set  90  and the first node  92 A of the second planetary gear set with the stationary member or transmission housing  14 . A first clutch  98  selectively connects the first node  90 A of the first planetary gear set  90  and the first node  92 A of the second planetary gear set  92  with the second node  90 B of the first planetary gear set  90  and the third node  92 C of the second planetary gear set  92 . 
     With reference to  FIG. 8B , an alternate gearbox arrangement  26 N is shown. The gearbox  26 N is similar to that shown in  FIG. 8A  and therefore like components are indicated by like reference numbers. However, in  FIG. 8B , the first clutch  98  is relocated and selectively connects the first node  90 A of the first planetary gear set  90  and the first node  92 A of the second planetary gear set  92  with the second node  92 B of the second planetary gear set  92 . 
     With reference to  FIG. 8C , an alternate gearbox arrangement  26 O is shown. The gearbox  26 O is similar to that shown in  FIG. 8A  and therefore like components are indicated by like reference numbers. However, in  FIG. 8C , the first clutch  98  is relocated and selectively connects the second node  90 B of the first planetary gear set  90  and the third node  92 C of the second planetary gear set  92  with the second node  92 B of the second planetary gear set  92 . 
     With reference to  FIG. 8D , an alternate gearbox arrangement  26 P is shown. The gearbox  26 P is similar to that shown in  FIG. 8A  and therefore like components are indicated by like reference numbers. However, in  FIG. 8D , the first clutch  98  is relocated and selectively connects the second node  90 B of the first planetary gear set  90  and the third node  92 C of the second planetary gear set  92  with the third node  90 C of the first planetary gear set  90 . 
     With reference to  FIG. 8E , an alternate gearbox arrangement  26 Q is shown. The gearbox  26 Q is similar to that shown in  FIG. 8A  and therefore like components are indicated by like reference numbers. However, in  FIG. 8E , the first clutch  98  is relocated and selectively connects the first node  90 A of the first planetary gear set  90  and the first node  92 A of the second planetary gear set  92  with the third node  90 C of the first planetary gear set  90 . 
     With reference to  FIG. 8F , an alternate gearbox arrangement  26 R is shown. The gearbox  26 R is similar to that shown in  FIG. 8A  and therefore like components are indicated by like reference numbers. However, in  FIG. 8F , the first clutch  98  is relocated and selectively connects the third node  90 C of the first planetary gear set  90  with the second node  92 B of the second planetary gear set  92 . 
     Turning now to  FIGS. 9A-F , stick diagrams present schematic layouts of embodiments of the gearbox  26 M-R according to the present invention. In  FIGS. 9A-F  the numbering from the lever diagram of  FIGS. 8A-F  are carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers. 
     For example, the planetary gear set  90  includes a sun gear member  90 A, a ring gear member  90 C, and a planet carrier member  90 B that rotatably supports a set of planet gears  90 D (only one of which is shown). The planet gears  90 D are each configured to intermesh with both the sun gear member  90 A and the ring gear member  90 C. The sun gear member  90 A is connected for common rotation with a first shaft or interconnecting member  100 . The ring gear member  90 C is connected for common rotation with the transfer member  34 . The planet carrier member  90 B is connected for common rotation with a second shaft or interconnecting member  102 . 
     The planetary gear set  92  includes a sun gear member  92 A, a ring gear member  92 C, and a planet carrier member  92 B that rotatably supports a set of planet gears  92 D (only one of which is shown). The planet gears  92 D are each configured to intermesh with both the sun gear member  92 A and the ring gear member  92 C. The sun gear member  92 A is connected for common rotation with the first shaft or interconnecting member  100 . The ring gear member  92 C is connected for common rotation with the second shaft or interconnecting member  102 . The planet carrier member  92 B is connected for common rotation with the transmission output shaft  22 . 
     The torque-transmitting mechanisms or brakes  94 ,  96  and clutch  98  allow for selective interconnection of the shafts or interconnecting members, members of the planetary gear sets and the housing. The torque-transmitting mechanisms are friction, dog or synchronizer type mechanisms or the like. For example, the first brake  94  is selectively engageable to connect the second shaft or interconnecting member  102  with the transmission housing  14  in order to restrict relative rotation of the member  102  and therefore the carrier member  90 B of the first planetary gear set  90  and the ring gear member  92 C of the second planetary gear set  92 . The second brake  96  is selectively engageable to connect the first shaft or interconnecting member  100  with the transmission housing  14  in order to restrict relative rotation of the member  100  and therefore the sun gear member  90 A and sun gear member  92 A. In  FIG. 9A , the clutch  98  is selectively engageable to connect the ring gear member  92 C and the carrier member  90 B with the sun gear member  90 A and the sun gear member  92 A. 
     Likewise,  FIGS. 9B-3F  illustrate stick diagrams of the corresponding gearbox arrangements  26 M- 26 R which alter the location of the clutch  98 , as described above. With reference to  FIG. 9B , an alternate gearbox arrangement  26 N is shown. The gearbox  26 N is similar to that shown in  FIG. 9A  and therefore like components are indicated by like reference numbers. However, in  FIG. 9B , the first clutch  98  is relocated and selectively connects the sun gear  90 A of the first planetary gear set  90  and the sun gear  92 A of the second planetary gear set  92  with the carrier member  92 B of the second planetary gear set  92 . 
     With reference to  FIG. 9C , an alternate gearbox arrangement  26 O is shown. The gearbox  26 O is similar to that shown in  FIG. 9A  and therefore like components are indicated by like reference numbers. However, in  FIG. 9C , the first clutch  98  is relocated and selectively connects the carrier member  90 B of the first planetary gear set  90  and the ring gear  92 C of the second planetary gear set  92  with the carrier member  92 B of the second planetary gear set  92 . 
     With reference to  FIG. 9D , an alternate gearbox arrangement  26 P is shown. The gearbox  26 P is similar to that shown in  FIG. 9A  and therefore like components are indicated by like reference numbers. However, in  FIG. 9D , the first clutch  98  is relocated and selectively connects the carrier member  90 B of the first planetary gear set  90  and the ring gear  92 C of the second planetary gear set  92  with the ring gear  90 C of the first planetary gear set  90  and the second transfer member  34 . 
     With reference to  FIG. 9E , an alternate gearbox arrangement  26 Q is shown. The gearbox  26 Q is similar to that shown in  FIG. 9A  and therefore like components are indicated by like reference numbers. However, in  FIG. 9E , the first clutch  98  is relocated and selectively connects the sun gear  90 A of the first planetary gear set  90  and the sun gear  92 A of the second planetary gear set  92  with the ring gear  90 C of the first planetary gear set  90 . 
     With reference to  FIG. 9F , an alternate gearbox arrangement  26 R is shown. The gearbox  26 R is similar to that shown in  FIG. 9A  and therefore like components are indicated by like reference numbers. However, in  FIG. 9F , the first clutch  98  is relocated and selectively connects the ring gear  90 C of the first planetary gear set  90  with the carrier member  92 B of the second planetary gear set  92 . 
     The description of the invention is merely exemplary in nature and variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.