Patent Publication Number: US-6666788-B2

Title: Family of five-speed transmission mechanisms having three planetary gear sets and four torque-transmitting devices

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates to a family of power transmissions having three planetary gear sets and a stationary interconnecting member that are controlled by one brake and three clutches to provide at least five forward speed ratios and one reverse speed ratio. 
     2. Background Art 
     Passenger vehicles include a powertrain that is comprised of an engine, multi-speed transmission, and a differential or final drive. The multi-speed transmission increases the overall operating range of the vehicle by permitting the engine to operate through its torque range a number of times. The number of forward speed ratios that are available in the transmission determines the number of times the engine torque range is repeated. Early automatic transmissions had two speed ranges. This severely limited the overall speed range of the vehicle and therefore required a relatively large engine that could produce a wide speed and torque range. This resulted in the engine operating at a specific fuel consumption point during cruising, other than the most efficient point. Therefore, manually-shifted (countershaft transmissions) were the most popular. 
     With the advent of three- and four-speed automatic transmissions, the automatic shifting (planetary gear) transmission increased in popularity with the motoring public. These transmissions improved the operating performance and fuel economy of the vehicle. The increased number of speed ratios reduces the step size between ratios and therefore improves the shift quality of the transmission by making the ratio interchanges substantially imperceptible to the operator under normal vehicle acceleration. 
     It has been suggested that the number of forward speed ratios be increased to five and even six speeds. Five-speed transmissions are disclosed in U.S. Pat. Nos. 5,879,264; 5,984,825; 5,997,429; 6,007,450; and 6,056,665 issued to Raghavan, Hebbale and Usoro on Mar. 9, 1999; Nov. 16, 1999; Dec. 7, 1999; Dec. 28, 1999 and May 2, 2000, respectively; and U.S. Pat. No. 5,951,432 issued to Wehking, Hebbale, Raghavan and Usoro on Sep. 14, 1999. Six-speed transmissions are disclosed in U.S. Pat. No. 4,070,927 issued to Polak on Jan. 31, 1978; U.S. Pat. No. 6,071,208 issued to Koivunen on Jun. 6, 2000; U.S. Pat. No. 5,106,352 issued to Lepelletier on Apr. 21, 1992; and U.S. Pat. No. 5,599,251 issued to Beim and McCarrick on Feb. 4, 1997. 
     Five-speed transmissions offer several advantages over four speed transmissions, including improved vehicle acceleration and improved fuel economy. While many trucks employ power transmissions, such as Polak, having six or more forward gear ratios, passenger cars are still manufactured with three- and four-speed automatic transmissions and relatively few five or six-speed devices due to the size and complexity of these transmissions. The Raghavan, Hebbale, Usoro and Wehking patents employ two planetary gear sets, and five or six torque transmitting mechanisms to provide five forward speeds. 
     SUMMARY OF THE INVENTION 
     It is an object of the present invention to provide an improved family of transmissions having three planetary gear sets and four torque-transmitting mechanisms controlled to provide at least five forward speed ratios. 
     In one aspect of the present invention, the family of transmissions has three planetary gear sets, each of which includes a first, second and third member, which members may comprise a sun gear, a ring gear, or a planet carrier assembly member. 
     In another aspect of the present invention, each of the planetary gear sets may be of the single pinion-type or of the double pinion-type. 
     In yet another aspect of the present invention, the first members of the first and second planetary gear sets are continuously connected with each other through a first interconnecting member. 
     In still another aspect of the invention, a second interconnecting member continuously interconnects the second member of the second planetary gear set with the first member of the third planetary gear set. 
     In still another aspect of the invention, a second member of the first planetary gear set is continuously interconnected with the stationary transmission housing. 
     In yet a further aspect of the invention, each family member incorporates an input shaft which is continuously interconnected with a member of the first, second or third planetary gear sets and an output shaft which is continuously connected with another member of the first, second or third planetary gear sets. 
     In still a further aspect of the invention, a first brake selectively interconnects a member of the first, second or third planetary gear sets or one of the interconnecting members with the transmission housing. 
     In another aspect of the invention, a first clutch selectively interconnects a member of the first planetary gear set with the input shaft, the output shaft, or a member of the second or third planetary gear sets. 
     In a still further aspect of the invention, a second clutch selectively interconnects a member of the second planetary gear set with the input shaft, the output shaft, one of the fixed interconnections, or a member of the first or third planetary gear sets. 
     In a still further aspect of the invention, a third clutch selectively interconnects a member of the first, second, or third planetary gear sets with the input shaft, the output shaft, or another member of the first, second, or third planetary gear sets. 
     In still another aspect of the invention, the brake and three clutches are selectively engageable in combinations of two to yield at least five forward speed ratios and one reverse speed ratio. 
     The above objects and other objects, features, and advantages of the present invention are readily apparent from the following detailed description of the best modes for carrying out the invention when taken in connection with the accompanying drawings. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 a  is a schematic representation of a powertrain including a planetary transmission incorporating a family member of the present invention; 
     FIG. 1 b  is a truth table and chart of some of the operating characteristics of the powertrain shown in FIG. 1 a;    
     FIG. 2 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 2 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 2 a;    
     FIG. 3 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 3 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 3 a;    
     FIG. 4 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 4 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 4 a;    
     FIG. 5 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 5 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 5 a;    
     FIG. 6 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 6 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 6 a;    
     FIG. 7 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 7 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 7 a;    
     FIG. 8 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 8 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 8 a;    
     FIG. 9 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 9 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 9 a;    
     FIG. 10 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 10 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 10 a;    
     FIG. 11 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 11 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 11 a;    
     FIG. 12 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 12 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 12 a;    
     FIG. 13 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 13 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 13 a;    
     FIG. 14 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 14 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 14 a;    
     FIG. 15 a  is a schematic representation of a powertrain having a planetary transmission incorporating another family member of the present invention; 
     FIG. 15 b  is a truth table and chart depicting some of the operating characteristics of the powertrain shown in FIG. 15 a.   
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Referring to the drawings, wherein like characters represent the same or corresponding parts throughout the several views, there is shown in FIG. 1 a  a powertrain  10  having a conventional engine and torque converter  12 , a planetary transmission  14 , and a conventional final drive mechanism  16 . 
     The planetary transmission  14  includes an input shaft  17  continuously connected with the engine and torque converter  12 , a planetary gear arrangement  18 , and an output shaft  19  continuously connected with the final drive mechanism  16 . The planetary gear arrangement  18  includes three planetary gear sets  20 ,  30  and  40 . 
     The planetary gear set  20  includes a sun gear member  22 , a ring gear member  24 , and a planet carrier assembly  26 . The planet carrier assembly  26  includes a plurality of pinion gears  27  rotatably mounted on a carrier member  29  and disposed in meshing relationship with both the sun gear member  22  and the ring gear member  24 . 
     The planetary gear set  30  includes a sun gear member  32 , a ring gear member  34 , and a planet carrier assembly member  36 . The planet carrier assembly member  36  includes a plurality of pinion gears  37  rotatably mounted on a carrier member  39  and disposed in meshing relationship with both the sun gear member  32  and the ring gear member  34 . 
     The planetary gear set  40  includes a sun gear member  42 , a ring gear member  44 , and a planet carrier assembly member  46 . The planet carrier assembly member  46  includes a plurality of pinion gears  47  rotatably mounted on a carrier member  49  and disposed in meshing relationship with both the sun gear member  42  and the ring gear member  44 . 
     The planetary gear arrangement  18  also includes four torque transmitting mechanisms  50 ,  52 ,  54  and  56 . The torque transmitting mechanism  50  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  52 ,  54  and  56  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the planet carrier assembly member  46 , and the output shaft  19  is continuously connected with the planet carrier assembly member  36 . The sun gear member  22  is continuously connected with the ring gear member  34  through the interconnecting member  70 . The sun gear member  32  is continuously connected with the sun gear member  42  through the interconnecting member  72 . The planet carrier assembly member  26  is continuously connected to the transmission housing  60 . 
     The ring gear member  44  is selectively connectable with the transmission housing  60  through the brake  50 . The ring gear member  24  is selectively connectable with the planet carrier assembly member  36  through the clutch  52 . The ring gear member  34  is selectively connectable with the planet carrier assembly member  46  through the clutch  54 . The ring gear member  34  is selectively connectable with the ring gear member  44  through the clutch  56 . 
     As shown in FIG. 1 b , and in particular the truth table disclosed therein, the torque-transmitting mechanisms are selectively engaged in combinations of two to provide five forward speed ratios and a reverse speed ratio. It should also be noted in the truth table that the torque-transmitting mechanism  52  remains engaged through a neutral condition, thereby simplifying the forward/reverse interchange. 
     The reverse speed ratio is established with the engagement of the clutches  52  and  54 . The clutch  52  connects the ring gear member  24  to the planet carrier assembly member  36 . The clutch  54  connects the ring gear member  34  to the planet carrier assembly member  46 . Accordingly, the ring gear member  24  rotates at the same speed as the planet carrier assembly member  36  and the output shaft  19 . The sun gear member  22  rotates at the same speed as the ring gear member  34 , the planet carrier assembly member  46 , and the input shaft  17 . The planet carrier assembly member  26  does not rotate. The ring gear member  24  rotates at a speed determined by the speed of the sun gear member  22  and the ring gear/sun gear tooth ratio of the planetary gear set  20 . The overall numerical value of the reverse speed ratio is determined from the ring gear/sun gear tooth ratio of the planetary gear set  20 . 
     The first forward speed ratio is established with the engagement of the brake  50  and the clutch  52 . The brake  50  connects the ring gear member  44  to the transmission housing  60 . The clutch  52  connects the ring gear member  24  to the planet carrier assembly member  36 . The ring gear member  24  rotates at the same speed as the planet carrier assembly member  36  and the output shaft  19 . The sun gear member  22  rotates at the same speed as the ring gear member  34 . The planet carrier assembly member  26  does not rotate. The sun gear member  32  rotates at the same speed as the sun gear member  42 . The planet carrier assembly member  36 , and therefore the output shaft  19 , rotates at a speed determined by the speed of the ring gear member  34 , the speed of the sun gear member  32 , and the ring gear/sun gear tooth ratio of the planetary gear set  30 . The ring gear  44  does not rotate. The planet carrier assembly member  46  rotates at the same speed as the input shaft  17 . The sun gear member  42  rotates at a speed determined by the speed of the planet carrier assembly member  46  and the ring gear/sun gear tooth ratio of the planetary gear set  40 . The overall numerical value of the first forward speed ratio is determined from the tooth ratios of the planetary gear sets  20 ,  30  and  40 . 
     The second forward speed ratio is established with the engagement of the clutches  52  and  56 . The clutch  52  connects the ring gear member  24  to the planet carrier assembly member  36 . The clutch  56  connects the ring gear member  34  to the ring gear member  44 . The planet carrier assembly member  26  does not rotate. The planet carrier assembly member  36  rotates at the same speed as the ring gear member  24  and the output shaft  19 . The ring gear member  34  rotates at the same speed as the sun gear member  22  and the ring gear member  44 . The sun gear member  32  rotates at the same speed as the sun gear member  42 . The planet carrier assembly member  36  rotates at a speed determined by the speed of the ring gear member  34 , the speed of the sun gear member  32 , and the ring gear/sun gear tooth ratio of the planetary gear set  30 . The planet carrier assembly member  46  rotates at the same speed as the input shaft  17 . The speed of the ring gear member  44  is determined from the speed of the planet carrier assembly member  46 , the speed of the sun gear member  42 , and the ring gear/sun gear tooth ratio of the planetary gear set  40 . The overall numerical value of the second forward speed ratio is determined from the tooth ratios of the planetary gear sets  20 ,  30  and  40 . 
     The third forward speed ratio is established with the engagement of the brake  50  and clutch  56 . The brake  50  connects the ring gear member  44  to the transmission housing  60 . The clutch  56  connects the ring gear member  34  to the ring gear member  44 . The planetary gear set  20  and ring gear members  34  and  44  do not rotate. The planet carrier assembly member  36  rotates at the same speed as the output shaft  19 . The sun gear member  32  rotates at the same speed as the sun gear member  42 . The speed of the planet carrier assembly member  36  is determined by the speed of the sun gear member  32  and the ring gear/sun gear tooth ratio of the planetary gear set  30 . The planet carrier assembly member  46  rotates at the same speed as the input shaft  17 . The sun gear member  42  rotates at a speed determined by the speed of the planet carrier assembly member  46  and the ring gear/sun gear tooth ratio of the planetary gear set  40 . The overall numerical value of the third forward speed ratio is determined from the tooth ratios of the planetary gear sets  30  and  40 . 
     The fourth forward speed ratio is established with the engagement of the clutches  54  and  56 . In this configuration, the input shaft  17  is directly connected to the output shaft  19 . The numerical value of the fourth forward speed ratio is 1. 
     The fifth forward speed ratio is established with the engagement of the brake  50  and the clutch  54 . The brake  50  connects the ring gear member  44  to the transmission housing  60 . The clutch  54  connects the ring gear member  34  to the planet carrier assembly member  46 . The planet carrier assembly member  26  does not rotate. The ring gear member  34  rotates at the same speed as the sun gear member  22 , the planet carrier assembly member  46 , and the input shaft  17 . The sun gear member  32  rotates at the same speed as the sun gear member  42 . The planet carrier assembly member  36  rotates at the same speed as the output shaft  19 . The speed of the planet carrier assembly member  36  is determined by the speed of the ring gear member  34 , the speed of the sun gear member  32 , and the ring gear/sun gear tooth ratio of the planetary gear set  30 . The ring gear member  44  does not rotate. The sun gear member  42  rotates at a speed determined by the speed of the planet carrier assembly member  46  and the ring gear/sun gear tooth ratio of the planetary gear set  40 . The overall numerical value of the fifth forward speed ratio is determined from the tooth ratios of the planetary gear sets  30  and  40 . 
     As set forth above, the engagement schedules for the torque-transmitting mechanisms are shown in the truth table of FIG. 1 b . This truth table also provides an example of speed ratios that are available utilizing the ring gear/sun gear tooth ratios given by way of example in FIG. 1 b . The R1/S1 value is the tooth ratio of the planetary gear set  20 ; the R2/S2 value is the tooth ratio of the planetary gear set  30 ; and the R3/S3 value is the tooth ratio of the planetary gear set  40 . Also, the chart of FIG. 1 b  describes the ratio steps that are attained utilizing the sample of tooth ratios given. For example, the step ratio between the first and second forward ratios is 1.67, while the step ratio between the reverse and first forward ratio is −0.65. It can also be readily determined from the truth table of FIG. 1 b  that all of the single step forward ratio interchanges are of the single transition variety, as are the double step forward ratio interchanges. 
     FIG. 2 a  shows a powertrain having a conventional engine and torque converter  12 , a planetary transmission  114 , and a conventional final drive mechanism  16 . 
     The planetary transmission  114  includes an input shaft  17  continuously connected with the engine and torque converter  12 , a planetary gear arrangement  118 , and an output shaft  19  continuously connected with the final drive mechanism  16 . The planetary gear arrangement  118  includes three planetary gear sets  120 ,  130  and  140 . 
     The planetary gear set  120  includes a sun gear member  122 , a ring gear member  124 , and a planet carrier assembly  126 . The planet carrier assembly  126  includes a plurality of pinion gears  127  rotatably mounted on a carrier member  129  and disposed in meshing relationship with both the sun gear member  122  and the ring gear member  124 . 
     The planetary gear set  130  includes a sun gear member  132 , a ring gear member  134 , and a planet carrier assembly member  136 . The planet carrier assembly member  136  includes a plurality of pinion gears  137  rotatably mounted on a carrier member  139  and disposed in meshing relationship with both the sun gear member  132  and the ring gear member  134 . 
     The planetary gear set  140  includes a sun gear member  142 , a ring gear member  144 , and a planet carrier assembly member  146 . The planet carrier assembly member  146  includes a plurality of pinion gears  147  rotatably mounted on a carrier member  149  and disposed in meshing relationship with both the sun gear member  142  and the ring gear member  144 . 
     The planetary gear arrangement  118  also includes four torque transmitting mechanisms  150 ,  152 ,  154  and  156 . The torque transmitting mechanism  150  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  152 ,  154  and  156  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the planet carrier assembly member  146 , and the output shaft  19  is continuously connected with the planet carrier assembly member  136 . The ring gear member  124  is continuously connected with the planet carrier assembly member  136  through the interconnecting member  170 . The sun gear member  132  is continuously connected with the sun gear member  142  through the interconnecting member  172 . The planet carrier assembly member  126  is continuously connected to the transmission housing  160 . 
     The ring gear member  144  is selectively connectable with the transmission housing  160  through the brake  150 . The sun gear member  122  is selectively connectable with the ring gear member  134  through the clutch  152 . The ring gear member  134  is selectively connectable with the planet carrier assembly member  146  through the clutch  154 . The ring gear member  134  is selectively connectable with the ring gear member  144  through the clutch  156 . 
     The truth table of FIG. 2 b  describes the engagement sequence utilized to provide five forward speed ratios and a reverse speed ratio in the planetary gear arrangement  118  shown in FIG. 2 a.    
     To establish the reverse speed ratio, the clutches  152  and  154  are engaged. The clutch  152  connects the sun gear member  122  to the ring gear member  134 . The clutch  154  connects the ring gear member  134  to the planet carrier assembly member  146 . The planet carrier assembly member  126  is connected to the transmission housing  160 , and not rotating. The ring gear member  124  rotates at the same speed as the planet carrier assembly member  136  and the output shaft  19 . The sun gear member  122  rotates at the same speed as the ring gear member  134 , the planet carrier assembly member  146 , and the input shaft  17 . The speed of the ring gear member  124  is determined from the speed of the sun gear member  122  and the ring gear/sun gear tooth ratio of the planetary gear set  120 . The overall numerical value of the reverse speed ratio is determined from the ring gear/sun gear tooth ratio of the planetary gear set  120 . 
     The first forward speed ratio is established with the engagement of the brake  150  and the clutch  152 . The brake  150  connects the ring gear member  144  to the transmission housing  160 , and the clutch  152  connects the sun gear member  122  to the ring gear member  134 . The planet carrier assembly member  126  is connected to the transmission housing  160  and not rotating. The ring gear member  124  rotates at the same speed as the output shaft  19  and the planet carrier assembly member  136 . The sun gear member  122  rotates at the same speed as the ring gear member  134 . The speed of the ring gear member  124  is determined from the speed of the sun gear member  122  and the ring gear/sun gear tooth ratio of the planetary gear set  120 . The sun gear member  132  rotates at the same speed as the sun gear member  142 . The planet carrier assembly member  136  rotates at a speed determined by the speed of the ring gear member  134 , the speed of the sun gear member  132 , and the ring gear/sun gear tooth ratio of the planetary gear set  130 . The ring gear member  144  does not rotate. The planet carrier assembly member  146  rotates at the same speed as the input shaft  17 . The speed of the sun gear member  142  is determined from the speed of the planet carrier assembly member  146  and the ring gear/sun gear tooth ratio of the planetary gear set  140 . The overall numerical value of the first forward speed ratio is determined from the tooth ratios of the planetary gear sets  120 ,  130  and  140 . 
     The second forward speed ratio is established with the engagement of the clutches  152  and  156 . The clutch  152  connects the sun gear member  122  to the ring gear member  134 , and the clutch  156  connects the ring gear member  134  to the ring gear member  144 . The planet carrier assembly member  126  does not rotate. The ring gear member  124  rotates at the same speed as the output shaft  19  and the planet carrier assembly member  136 . The sun gear member  122  rotates at the same speed as the ring gear members  134  and  144 . The speed of the ring gear member  124 , and therefore the output shaft  19 , is determined from the speed of the sun gear member  122  and the ring gear/sun gear tooth ratio of the planetary gear set  120 . The sun gear member  132  rotates at the same speed as the sun gear member  142 . The speed of the planet carrier assembly member  136  is determined from the speed of the ring gear member  134 , the speed of the sun gear member  132 , and the ring gear/sun gear tooth ratio of the planetary gear set  130 . The planet carrier assembly member  146  rotates at the same speed as the input shaft  17 . The speed of the sun gear member  142  is determined from the speed of the planet carrier assembly member  146 , the speed of the ring gear member  144 , and the ring gear/sun gear tooth ratio of the planetary gear set  140 . The overall numerical value of the second forward speed ratio is determined from the tooth ratios of the planetary gear sets  120 ,  130  and  140 . 
     The third forward speed ratio is established with the engagement of the brake  150  and the clutch  156 . The brake  150  connects the ring gear member  144  to the transmission housing  160 , and the clutch  156  connects the ring gear member  134  to the ring gear member  144 . The planet carrier assembly member  126  is fixed to the transmission housing and not rotating. The planet carrier assembly member  136  rotates at the same speed as the sun gear member  124  and the output shaft  19 . The ring gear members  134  and  144  do not rotate. The sun gear member  132  rotates at the same speed as the sun gear member  142 . The planet carrier assembly member  136  rotates at a speed determined by the speed of the sun gear member  132  and the ring gear/sun gear tooth ratio of the planetary gear set  130 . The planet carrier assembly member  146  rotates at the same speed as the input shaft  17 . The sun gear member  142  rotates at a speed determined by the speed of the planet carrier assembly member  146  and the ring gear/sun gear tooth ratio of the planetary gear set  140 . The overall numerical value of the third forward speed ratio is determined from the tooth ratios of the planetary gear sets  130  and  140 . 
     The fourth forward speed ratio is established with the engagement of the clutches  154  and  156 . In this configuration, the input shaft is directly connected to the output shaft. The numerical value of the fourth forward speed ratio is 1. 
     The fifth forward speed ratio is established with the engagement of the brake  150  and the clutch  154 . The brake  150  connects the ring gear member  144  to the transmission housing  160 . The clutch  154  connects the ring gear member  134  to the planet carrier assembly member  146 . The planet carrier assembly member  126  does not rotate. The planet carrier assembly member  136  rotates at the same speed as the ring gear member  124  and the output shaft  19 . The ring gear member  134  rotates at the same speed as the planet carrier assembly member  146  and the input shaft  17 . The sun gear member  132  rotates at the same speed as the sun gear member  142 . The planet carrier assembly member  136  rotates at a speed determined by the speed of the ring gear member  134 , the speed of the sun gear member  132 , and the ring gear/sun gear tooth ratio of the planetary gear set  130 . The ring gear member  144  does not rotate. The sun gear member  142  rotates at a speed determined by the speed of the planet carrier assembly member  146  and the ring gear/sun gear tooth ratio of the planetary gear set  140 . The overall numerical value of the fifth forward speed ratio is determined from the ring gear/sun gear tooth ratios of the planetary gear sets  130  and  140 . 
     As set forth above, the truth table of FIG. 2 b  describes the engagement sequence of the torque transmitting mechanisms utilized to provide a reverse drive ratio and five forward speed ratios. It can be readily determined from the truth table that all the single step forward interchanges are of the single transition type, as are the double step forward interchanges. The truth table also provides an example of the ratios that can be attained with the family members shown in FIG. 2 a  utilizing the sample tooth ratios given in FIG. 2 b . The R1/S1 value is the tooth ratio of the planetary gear set  120 ; the R2/S2 value is the tooth ratio of the planetary gear set  130 ; and the R3/S3 value is the tooth ratio of the planetary gear set  140 . Also shown in FIG. 2 b  are the ratio steps between single step ratios in the forward direction as well as the reverse to first ratio step. For example, the first to second step ratio is 1.56. 
     Turning to FIG. 3 a , a powertrain  210  includes the engine and torque converter  12 , a planetary transmission  214 , and a final drive mechanism  16 . The planetary transmission  214  includes an input shaft  17  continuously connected with the engine and torque converter  12 , a planetary gear arrangement  218 , and an output shaft  19  continuously connected with the final drive mechanism  16 . The planetary gear arrangement  218  includes three planetary gear sets  220 ,  230  and  240 . 
     The planetary gear set  220  includes a sun gear member  222 , a ring gear member  224 , and a planet carrier assembly  226 . The planet carrier assembly  226  includes a plurality of pinion gears  227  rotatably mounted on a carrier member  229  and disposed in meshing relationship with both the sun gear member  222  and the ring gear member  224 . 
     The planetary gear set  230  includes a sun gear member  232 , a ring gear member  234 , and a planet carrier assembly member  236 . The planet carrier assembly member  236  includes a plurality of pinion gears  237  rotatably mounted on a carrier member  239  and disposed in meshing relationship with both the sun gear member  232  and the ring gear member  234 . 
     The planetary gear set  240  includes a sun gear member  242 , a ring gear member  244 , and a planet carrier assembly member  246 . The planet carrier assembly member  246  includes a plurality of pinion gears  247  rotatably mounted on a carrier member  249  and disposed in meshing relationship with both the sun gear member  242  and the ring gear member  244 . 
     The planetary gear arrangement  218  also includes four torque transmitting mechanisms  250 ,  252 ,  254  and  256 . The torque transmitting mechanism  250  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  252 ,  254  and  256  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the ring gear member  244 , and the output shaft  19  is continuously connected with the planet carrier assembly member  246 . The sun gear member  222  is continuously connected with the planet carrier assembly member  236  through the interconnecting member  270 . The sun gear member  232  is continuously connected with the sun gear member  242  through the interconnecting member  272 . The planet carrier assembly member  226  is continuously connected to the transmission housing  260 . 
     The ring gear member  234  is selectively connectable with the transmission housing  260  through the brake  250 . The ring gear member  224  is selectively connectable with the planet carrier assembly member  246  through the clutch  252 . The planet carrier assembly member  236  is selectively connectable with the ring gear member  234  through the clutch  254 . The planet carrier assembly member  236  is selectively connectable with the ring gear member  244  through the clutch  256 . 
     As shown in the truth table in FIG. 3 b , the torque transmitting mechanisms are engaged in combinations of two to establish five forward speed ratios and one reverse ratio. It should be also noted that the torque transmitting mechanism  252  can remain engaged through the neutral condition, thereby simplifying the forward/reverse interchange. 
     The reverse speed ratio is established with the engagement of the clutches  252  and  256 . The clutch  252  connects the ring gear member  224  to the planet carrier assembly member  246 , and the clutch  256  connects the planet carrier assembly member  236  to the ring gear member  244 . The planet carrier assembly member  226  does not rotate. The sun gear member  222  rotates at the same speed as the planet carrier assembly member  236 , the ring gear member  244 , and the input shaft  17 . The ring gear member  224  rotates at the same speed as the planet carrier assembly member  246  and the output shaft  19 . The speed of the ring gear member  224 , and therefore the output shaft, is determined from the speed of the sun gear member  222  and the ring gear/sun gear tooth ratio of the planetary gear set  220 . The overall numerical value of the reverse speed ratio is determined from the ring gear/sun gear tooth ratio of the planetary gear set  220 . 
     The first forward speed ratio is established with the engagement of the brake  250  and the clutch  252 . The brake  250  connects the ring gear member  234  to the transmission housing  260 , and the clutch  252  connects the ring gear member  224  to the planet carrier assembly member  246 . The planet carrier assembly member  226  does not rotate. The ring gear member  224  rotates at the same speed as the planet carrier assembly member  246  and the output shaft  19 . The sun gear member  222  rotates at the same speed as the planet carrier assembly member  236 . The ring gear  224  rotates at a speed determined by the speed of the sun gear member  222  and the ring gear/sun gear tooth ratio of the planetary gear set  220 . The ring gear member  234  does not rotate. The sun gear member  232  rotates at the same speed as the sun gear member  242 . The planet carrier assembly member  236  rotates at a speed determined by the speed of the sun gear member  232  and the ring gear/sun gear tooth ratio of the planetary gear set  230 . The ring gear member  244  rotates at the same speed as the input shaft  17 . The planet carrier assembly member  246  rotates at a speed determined by the speed of the ring gear member  244 , the speed of the sun gear member  242 , and the ring gear/sun gear tooth ratio of the planetary gear set  240 . The overall numerical value of the first forward speed ratio is determined from the tooth ratios of the planetary gear sets  220 ,  230  and  240 . 
     The second forward speed ratio is established with the engagement of the clutches  252  and  254 . The clutch  252  connects the ring gear member  224  to the planet carrier assembly member  246 , and the clutch  254  connects the sun gear member  222  to the ring gear member  234 . The planet carrier assembly member  226  does not rotate. The ring gear member  224  rotates at the same speed as the planet carrier assembly member  246  and the output shaft  19 . The sun gear member  222  rotates at the same speed as the planet carrier assembly member  236  and the ring gear member  234 . The ring gear member  224  rotates at a speed determined by the speed of the sun gear member  222  and the ring gear/sun gear tooth ratio of the planetary gear set  220 . The ring gear member  244  rotates at the same speed as the input shaft  17 . The planet carrier assembly member  246  rotates at a speed determined by the speed of the ring gear member  244 , the speed of the sun gear member  242 , which is the same as the speed of the sun gear member  232 , and the ring gear/sun gear tooth ratio of the planetary gear set  240 . The overall numerical value of the second forward speed ratio is determined from the tooth ratios of the planetary gear sets  220  and  240 . 
     The third forward speed ratio is established with the engagement of the brake  250  and the clutch  254 . The brake  250  connects the ring gear member  234  to the transmission housing  260 , and the clutch  254  connects the planet carrier assembly member  236  to the ring gear member  234 . The planetary gear sets  220  and  230  and sun gear member  242  do not rotate. The ring gear member  244  rotates at the same speed as the input shaft  17 . The planet carrier assembly member  246  rotates at the same speed as the output shaft  19 . The speed of the planet carrier assembly member  246  is determined from the speed of the ring gear member  244  and the ring gear/sun gear tooth ratio of the planetary gear set  240 . The overall numerical value of the third forward speed ratio is determined from the tooth ratio of the planetary gear set  240 . 
     The fourth forward speed ratio is established with the engagement of the clutches  254  and  256 . In this configuration, the input shaft  17  is directly connected to the output shaft  19 . The numerical value of the fourth forward speed ratio is 1. 
     The fifth forward speed ratio is established with the engagement of the brake  250  and the clutch  256 . The brake  250  connects the ring gear member  234  to the transmission housing  260 , and the clutch  256  connects the planet carrier assembly member  236  to the ring gear member  244 . The planet carrier assembly member  226  does not rotate. The sun gear member  222  rotates at the same speed as the planet carrier assembly member  236 , the ring gear member  244 , and the input shaft  17 . The ring gear member  234  does not rotate. The sun gear member  232  rotates at the same speed as the sun gear member  242 . The planet carrier assembly member  236  rotates at a speed determined from the speed of the sun gear member  232  and the ring gear/sun gear tooth ratio of the planetary gear set  230 . The planet carrier assembly member  246  rotates at the same speed as the output shaft  19 . The speed of the planet carrier assembly member  246  is determined from the speed of the ring gear member  244 , the speed of the sun gear member  242 , and the ring gear/sun gear tooth ratio of the planetary gear set  240 . The overall numerical value of the fifth forward speed ratio is determined from the tooth ratios of the planetary gear sets  230  and  240 . 
     As previously set forth, the truth table of FIG. 3 b  describes the combinations of engagements utilized for the five forward speed ratios and reverse ratio. The truth table also provides an example of speed ratios that are available with the family member described above. These examples of speed ratios are determined utilizing the tooth ratios given in FIG. 3 b . The R1/S1 value is the tooth ratio of the planetary gear set  220 ; the R2/S2 value is the tooth ratio of the planetary gear set  230 ; and the R3/S3 value is the tooth ratio of the planetary gear set  240 . Also depicted in FIG. 3 b  is a chart representing the ratio steps between adjacent forward speed ratios and the reverse speed ratio. For example, the first to second ratio interchange has a step of 1.6. It can also be readily determined from the truth table of FIG. 3 b  that all of the single step forward ratio interchanges are of the single transition variety, as are all of the double step forward interchanges. 
     A powertrain  310 , shown in FIG. 4 a , includes the engine and torque converter  12 , a planetary transmission  314 , and the final drive mechanism  16 . The planetary transmission  314  includes an input shaft  17  continuously connected with the engine and torque converter  12 , a planetary gear arrangement  318 , and output shaft  19  continuously connected with the final drive mechanism  16 . The planetary gear arrangement  318  includes three planetary gear sets  320 ,  330  and  340 . 
     The planetary gear set  320  includes a sun gear member  322 , a ring gear member  324 , and a planet carrier assembly member  326 . The planet carrier assembly member  326  includes a plurality of pinion gears  327  rotatably mounted on a carrier member  329  and disposed in meshing relationship with both the sun gear member  322  and the ring gear member  324 . 
     The planetary gear set  330  includes a sun gear member  332 , a ring gear member  334 , and a planet carrier assembly member  336 . The planet carrier assembly member  336  includes a plurality of pinion gears  337  rotatably mounted on a carrier member  339  and disposed in meshing relationship with both the sun gear member  332  and the ring gear member  334 . 
     The planetary gear set  340  includes a sun gear member  342 , a ring gear member  344 , and a planet carrier assembly member  346 . The planet carrier assembly member  346  includes a plurality of pinion gears  347  rotatably mounted on a carrier member  349  and disposed in meshing relationship with both the sun gear member  342  and the ring gear member  344 . 
     The planetary gear arrangement  318  also includes four torque transmitting mechanisms  350 ,  352 ,  354  and  356 . The torque transmitting mechanism  350  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  352 ,  354  and  356  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  342 , and the output shaft  19  is continuously connected with the ring gear member  334 . The sun gear member  322  is continuously connected with the sun gear member  332  through the interconnecting member  370 . The planet carrier assembly member  336  is continuously connected with the ring gear member  344  through the interconnecting member  372 . The planet carrier assembly member  326  is continuously connected to the transmission housing  360 . 
     The ring gear member  324  is selectively connectable with the transmission housing  360  through the brake  350 . The ring gear member  324  is selectively connectable with the planet carrier assembly member  346  through the clutch  352 . The planet carrier assembly member  346  is selectively connectable with the ring gear member  334  through the clutch  354 . The planet carrier assembly member  346  is selectively connectable with the sun gear member  342  through the clutch  356 . 
     The truth tables given in FIGS. 4 b ,  5   b ,  6   b ,  7   b ,  8   b ,  9   b ,  10   b ,  11   b ,  12   b ,  13   b ,  14   b  and  15   b  show the engagement sequence for the torque transmitting mechanisms to provide at least five forward speed ratios and one reverse ratio. As shown and described for the configurations in FIGS. 1 a ,  2   a  and  3   a , those skilled in the art will understand from the respective truth tables how the speed ratios are established through the planetary gear sets identified in the written description. 
     The truth table shown in FIG. 4 b  describes the engagement combination and the engagement sequence necessary to provide the reverse drive ratio and the five forward speed ratios. A sample of the numerical values for the ratios is also provided in the truth table of FIG. 4 b . These values are determined utilizing the ring gear/sun gear tooth ratios also given in FIG. 4 b . The R1/S1 value is the tooth ratio for the planetary gear set  320 ; the R2/S2 value is the tooth ratio for the planetary gear set  330 ; and the R3/S3 value is the tooth ratio for the planetary gear set  340 . Also given in FIG. 4 b  is a chart describing the step ratios between the adjacent forward speed ratios and the reverse to first forward speed ratio. For example, the first to second forward speed ratio step is 1.64. It can be readily determined from the truth table of FIG. 4 b  that each of the forward single step ratio interchanges is a single transition shift, as are the double step interchanges. The chart also shows that the torque transmitting mechanism  352  can be engaged through the neutral condition to simplify the forward/reverse interchange. 
     One skilled in the art will recognize that the numerical values of the reverse and second forward speed ratios are determined from the ring gear/sun gear tooth ratios of the planetary gear sets  330  and  340 . The numerical value of the first forward speed ratio is determined from the tooth ratios of the planetary gear sets  320 ,  330  and  340 . The numerical value of the third forward speed ratio is 1. The numerical value of the fourth forward speed ratio is determined from the tooth ratio of the planetary gear set  330 . The numerical value of the fifth forward speed ratio is determined from the tooth ratios of the planetary gear sets  320  and  330 . 
     A powertrain  410 , shown in FIG. 5 a , includes the engine and torque converter  12 , a planetary transmission  414  and the final drive mechanism  16 . The planetary transmission  414  includes a planetary gear arrangement  418 , input shaft  17  and output shaft  19 . The planetary gear arrangement  418  includes three simple planetary gear sets  420 ,  430  and  440 . 
     The planetary gear set  420  includes a sun gear member  422 , a ring gear member  424 , and a planet carrier assembly  426 . The planet carrier assembly  426  includes a plurality of pinion gears  427  rotatably mounted on a carrier member  429  and disposed in meshing relationship with both the sun gear member  422  and the ring gear member  424 . 
     The planetary gear set  430  includes a sun gear member  432 , a ring gear member  434 , and a planet carrier assembly member  436 . The planet carrier assembly member  436  includes a plurality of pinion gears  437  rotatably mounted on a carrier member  439  and disposed in meshing relationship with both the sun gear member  432  and the ring gear member  434 . 
     The planetary gear set  440  includes a sun gear member  442 , a ring gear member  444 , and a planet carrier assembly member  446 . The planet carrier assembly member  446  includes a plurality of pinion gears  447  rotatably mounted on a carrier member  449  and disposed in meshing relationship with both the sun gear member  442  and the ring gear member  444 . 
     The planetary gear arrangement  418  also includes four torque transmitting mechanisms  450 ,  452 ,  454  and  456 . The torque transmitting mechanism  450  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  452 ,  454  and  456  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  422 , and the output shaft  19  is continuously connected with the planet carrier assembly member  436 . The sun gear member  422  is continuously connected with the sun gear member  434  through the interconnecting member  470 . The sun gear member  432  is continuously connected with the ring gear member  444  through the interconnecting member  472 . The planet carrier assembly member  426  is continuously connected to the transmission housing  460 . 
     The sun gear member  442  is selectively connectable with the transmission housing  460  through the brake  450 . The planet carrier assembly member  446  is selectively connectable with the ring gear member  424  through the brake  452 . The planet carrier assembly member  446  is selectively connectable with the ring gear member  444  through the clutch  454 . The planet carrier assembly member  436  is selectively connectable with the planet carrier assembly member  446  through the clutch  456 . 
     The truth table shown in FIG. 5 b  describes the engagement combination and sequence of the torque transmitting mechanisms  450 ,  452 ,  454  and  456  that are employed to provide the reverse drive ratio and the five forward speed ratios. It should be noted that the torque transmitting mechanism  452  is engaged through the neutral condition to simplify the forward/reverse interchange. 
     Also given in the truth table of FIG. 5 b  is a set of numerical values that are attainable with the present invention utilizing the ring gear/sun gear tooth ratios shown. The R1/S1 value is the tooth ratio of the planetary gear set  420 ; the R2/S2 value is the tooth ratio of the planetary gear set  430 ; and the R3/S3 value is the tooth ratio of the planetary gear set  440 . As can also be determined from the truth table of FIG. 5 b , the single step forward interchanges are single transition shifts, as are the double step interchanges in the forward direction. 
     FIG. 5 b  also provides a chart of the ratio steps between adjacent forward ratios and between the reverse and first forward ratio. For example, the ratio step between the first and second forward ratios is 1.42. 
     One skilled in the art will recognize that the numerical value of the reverse speed ratio is determined from the ring gear/sun gear tooth ratio of the planetary gear set  420 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  420 ,  430  and  440 . The numerical value of the second forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  420  and  430 . The numerical value of the third forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  430 . The numerical value of the fourth forward speed ratio is 1. The numerical value of the fifth forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  430  and  440 . 
     A powertrain  510 , shown in FIG. 6 a , includes an engine and torque converter  12 , a planetary gear transmission  514  and the final drive mechanism  16 . The planetary transmission  514  includes the input shaft  17 , a planetary gear arrangement  518  and the output shaft  19 . The planetary gear arrangement  518  includes three planetary gear sets  520 ,  530  and  540 . 
     The planetary gear set  520  includes a sun gear member  522 , a ring gear member  524 , and a planet carrier assembly  526 . The planet carrier assembly  526  includes a plurality of pinion gears  527  rotatably mounted on a carrier member  529  and disposed in meshing relationship with both the sun gear member  522  and the ring gear member  524 . 
     The planetary gear set  530  includes a sun gear member  532 , a ring gear member  534 , and a planet carrier assembly member  536 . The planet carrier assembly member  536  includes a plurality of pinion gears  537  rotatably mounted on a carrier member  539  and disposed in meshing relationship with both the sun gear member  532  and the ring gear member  534 . 
     The planetary gear set  540  includes a sun gear member  542 , a ring gear member  544 , and a planet carrier assembly member  546 . The planet carrier assembly member  546  includes a plurality of pinion gears  547  rotatably mounted on a carrier member  549  and disposed in meshing relationship with both the sun gear member  542  and the ring gear member  544 . 
     The planetary gear arrangement  518  also includes four torque transmitting mechanisms  550 ,  552 ,  554  and  556 . The torque transmitting mechanism  550  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  552 ,  554  and  556  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  532 , and the output shaft  19  is continuously connected with the sun gear member  542 . The planet carrier assembly member  526  is continuously connected with the ring gear member  534  through the interconnecting member  570 . The planet carrier assembly member  536  is continuously connected with the ring gear member  544  through the interconnecting member  572 . The sun gear member  522  is continuously connected to the transmission housing  560 . 
     The ring gear member  524  is selectively connectable with the transmission housing  560  through the brake  550 . The planet carrier assembly member  546  is selectively connectable with the ring gear member  524  through the clutch  552 . The sun gear member  532  is selectively connectable with the planet carrier assembly member  546  through the clutch  554 . The sun gear member  542  is selectively connectable with the planet carrier assembly member  546  through the clutch  556 . 
     The truth table shown in FIG. 6 b  describes the engagement sequence and combination of the torque transmitting mechanisms to provide the reverse speed ratio and five forward speed ratios. It should be noted that the torque transmitting mechanism  550  can remain engaged through the neutral condition, thereby simplifying the forward/reverse interchange. It can also be determined from the truth table of FIG. 6 b  that all of the single step forward ratio interchanges are of the single transition variety, as are all of the double step forward interchanges. The chart of FIG. 6 b  describes the ratio steps between adjacent forward speed ratios and the ratio step between the reverse and first forward speed ratio. 
     One skilled in the art will recognize that the overall numerical values of the reverse and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  530  and  540 . The overall numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  530 . The overall numerical value of the second forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  520  and  530 . The numerical value of the third forward speed ratio is 1. The numerical value of the fourth forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  520 ,  530  and  540 . 
     The sample speed ratios given in the truth table are determined utilizing the tooth ratio values also given in FIG. 6 b . The R1/S1 value is the tooth ratio of the planetary gear set  520 ; the R2/S2 value is the tooth ratio of the planetary gear set  530 ; and the R3/S3 value is the tooth ratio of the planetary gear set  540 . 
     A powertrain  610 , shown in FIG. 7 a , has the engine and torque converter  12 , a planetary transmission  614  and the final drive mechanism  16 . The planetary transmission  614  includes the input shaft  17 , a planetary gear arrangement  618  and the output shaft  19 . The planetary gear arrangement  618  includes three planetary gear sets  620 ,  630  and  640 . 
     The planetary gear set  620  includes a sun gear member  622 , a ring gear member  624 , and a planet carrier assembly  626 . The planet carrier assembly  626  includes a plurality of pinion gears  627  rotatably mounted on a carrier member  629  and disposed in meshing relationship with both the sun gear member  622  and the ring gear member  624 . 
     The planetary gear set  630  includes a sun gear member  632 , a ring gear member  634 , and a planet carrier assembly member  636 . The planet carrier assembly member  636  includes a plurality of pinion gears  637  rotatably mounted on a carrier member  639  and disposed in meshing relationship with both the sun gear member  632  and the ring gear member  634 . 
     The planetary gear set  640  includes a sun gear member  642 , a ring gear member  644 , and a planet carrier assembly member  646 . The planet carrier assembly member  646  includes a plurality of pinion gears  647  rotatably mounted on a carrier member  649  and disposed in meshing relationship with both the sun gear member  642  and the ring gear member  644 . 
     The planetary gear arrangement  618  also includes four torque transmitting mechanisms  650 ,  652 ,  654  and  656 . The torque transmitting mechanism  650  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  652 ,  654  and  656  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  642 , and the output shaft  19  is continuously connected with the ring gear member  644 . The planet carrier assembly member  626  is continuously connected with the sun gear member  632  through the interconnecting member  670 . The ring gear member  634  is continuously connected with the planet carrier assembly member  646  through the interconnecting member  672 . The sun gear member  622  is continuously connected to the transmission housing  660 . 
     The ring gear member  624  is selectively connectable with the transmission housing  660  through the brake  650 . The ring gear member  624  is selectively connectable with the planet carrier assembly member  636  through the clutch  652 . The planet carrier assembly member  636  is selectively connectable with the sun gear member  642  through the clutch  654 . The planet carrier assembly member  636  is selectively connectable with the ring gear member  644  through the clutch  656 . 
     The truth table shown in FIG. 7 b  describes the combination of torque transmitting mechanism engagements that will provide the reverse drive ratio and the five forward speed ratios, as well as the sequence of these engagements and interchanges. The torque transmitting mechanism  650  can be engaged through the neutral condition, thereby simplifying the forward/reverse interchange. It can be noted from the truth table that each of the single step forward interchanges are single transition ratio changes, and the double step forward interchanges are also single transition ratio changes. 
     The ratio values given are by way of example and are established utilizing the ring gear/sun gear tooth ratios given in FIG. 7 b . For example, the R1/S1 value is the tooth ratio of the planetary gear set  620 ; the R2/S2 value is the tooth ratio of the planetary gear set  630 ; and the R3/S3 value is the tooth ratio of the planetary gear set  640 . The ratio steps between adjacent forward ratios and the reverse to first ratio are also given in FIG. 7 b.    
     Those skilled in the art will, upon reviewing the truth table of FIG. 7 b , recognize that the reverse speed ratio has a numerical value determined by the ring gear/sun gear tooth ratio of the planetary gear set  640 . The numerical values of the first and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  630  and  640 . The numerical values of the second and fourth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  620 ,  630  and  640 . The numerical value of the third forward speed ratio is 1. 
     A powertrain  710 , shown in FIG. 8 a , has the conventional engine and torque converter  12 , a planetary transmission  714 , and the conventional final drive mechanism  16 . The engine and torque converter  12  are drivingly connected with the planetary transmission  714  through the input shaft  17 . The planetary transmission  714  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  714  includes a planetary gear arrangement  718  that has a first planetary gear set  720 , a second planetary gear set  730 , and a third planetary gear set  740 . 
     The planetary gear set  720  includes a sun gear member  722 , a ring gear member  724 , and a planet carrier assembly  726 . The planet carrier assembly  726  includes a plurality of pinion gears  727  rotatably mounted on a carrier member  729  and disposed in meshing relationship with both the sun gear member  722  and the ring gear member  724 . 
     The planetary gear set  730  includes a sun gear member  732 , a ring gear member  734 , and a planet carrier assembly member  736 . The planet carrier assembly member  736  includes a plurality of pinion gears  737  rotatably mounted on a carrier member  739  and disposed in meshing relationship with both the sun gear member  732  and the ring gear member  734 . 
     The planetary gear set  740  includes a sun gear member  742 , a ring gear member  744 , and a planet carrier assembly member  746 . The planet carrier assembly member  746  includes a plurality of pinion gears  747  rotatably mounted on a carrier member  749  and disposed in meshing relationship with both the sun gear member  742  and the ring gear member  744 . 
     The planetary gear arrangement  718  also includes four torque transmitting mechanisms  750 ,  752 ,  754  and  756 . The torque transmitting mechanism  750  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  752 ,  754  and  756  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  742 , and the output shaft  19  is continuously connected with the planet carrier assembly member  736 . The ring gear member  724  is continuously connected with the sun gear member  732  through the interconnecting member  770 . The planet carrier assembly member  736  is continuously connected with the ring gear member  744  through the interconnecting member  772 . The sun gear member  722  is continuously connected to the transmission housing  760 . 
     The sun gear member  732  is selectively connectable with the transmission housing  760  through the brake  750 . The planet carrier assembly member  726  is selectively connectable with the planet carrier assembly member  746  through the clutch  752 . The ring gear member  734  is selectively connectable with the sun gear member  742  through the clutch  754 . The ring gear member  734  is selectively connectable with the planet carrier assembly member  746  through the clutch  756 . 
     The truth table of FIG. 8 b  defines the torque transmitting mechanism engagement sequence utilized for each of the forward speed ratios and the reverse speed ratio. Also given in the truth table is a set of numerical values that are attainable with the present invention utilizing the ring gear/sun gear tooth ratios given in FIG. 8 b . The R1/S1 value is the tooth ratio of the planetary gear set  720 ; the R2/S2 value is the tooth ratio of the planetary gear set  730 ; and the R3/S3 value is the tooth ratio of the planetary gear set  740 . As can also be determined from the truth table of FIG. 8 b , the single step forward interchanges are single transition shifts, as are the double step interchanges in the forward direction. 
     FIG. 8 b  also provides a chart of the ratio steps between adjacent forward ratios and between the reverse and first forward ratio. For example, the ratio step between the first and second forward ratios is 1.61. Those skilled in the art will recognize that the numerical value of the reverse speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  740 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  730  and  740 . The numerical value of the second forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  730 . The numerical value of the third forward speed ratio is 1. The numerical values of the fourth and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  720 ,  730  and  740 . 
     A powertrain  810 , shown in FIG. 9 a , has the conventional engine and torque converter  12 , a planetary transmission  814 , and the final drive mechanism  16 . The engine and torque converter  12  are drivingly connected with the planetary transmission  814  through the input shaft  17 . The planetary transmission  814  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  814  includes a planetary gear arrangement  818  that has a first planetary gear set  820 , a second planetary gear set  830 , and a third planetary gear set  840 . 
     The planetary gear set  820  includes a sun gear member  822 , a ring gear member  824 , and a planet carrier assembly  826 . The planet carrier assembly  826  includes a plurality of pinion gears  827  rotatably mounted on a carrier member  829  and disposed in meshing relationship with both the sun gear member  822  and the ring gear member  824 . 
     The planetary gear set  830  includes a sun gear member  832 , a ring gear member  834 , and a planet carrier assembly member  836 . The planet carrier assembly member  836  includes a plurality of pinion gears  837  rotatably mounted on a carrier member  839  and disposed in meshing relationship with both the sun gear member  832  and the ring gear member  834 . 
     The planetary gear set  840  includes a sun gear member  842 , a ring gear member  844 , and a planet carrier assembly member  846 . The planet carrier assembly member  846  includes a plurality of pinion gears  847  rotatably mounted on a carrier member  849  and disposed in meshing relationship with both the sun gear member  842  and the ring gear member  844 . 
     The planetary gear arrangement  818  also includes four torque transmitting mechanisms  850 ,  852 ,  854  and  856 . The torque transmitting mechanism  850  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  852 ,  854  and  856  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  842 , and the output shaft  19  is continuously connected with the ring gear member  844 . The ring gear member  824  is continuously connected with the planet carrier assembly member  836  through the interconnecting member  870 . The ring gear member  834  is continuously connected with the planet carrier assembly member  846  through the interconnecting member  872 . The sun gear member  822  is continuously connected to the transmission housing  860 . 
     The sun gear member  832  is selectively connectable with the transmission housing  860  through the brake  850 . The planet carrier assembly member  826  is selectively connectable with the sun gear member  832  through the clutch  852 . The planet carrier assembly member  836  is selectively connectable with the sun gear member  842  through the clutch  854 . The planet carrier assembly member  836  is selectively connectable with the ring gear member  844  through the clutch  856 . 
     The truth table shown in FIG. 9 b  defines the torque transmitting mechanism engagement sequence that provides the reverse ratio and five forward speed ratios shown in the truth table and available with the planetary gear arrangement  818 . The truth table indicates that the torque transmitting mechanism  850  can remain engaged through the neutral condition, thereby simplifying the forward/reverse interchange. A sample of numerical values for the individual ratios is also given in the truth table of FIG. 9 b . These numerical values have been calculated utilizing the ring gear/sun gear tooth ratios also given by way of example in FIG. 9 b . The R1/S1 value is the tooth ratio of the planetary gear set  820 ; the R2/S2 value is the tooth ratio of the planetary gear set  830 ; and the R3/S3 value is the tooth ratio of the planetary gear set  840 . It can be readily recognized from the truth table that all of the single and double step forward interchanges are single transition ratio interchanges. FIG. 9 b  also describes the ratio steps between adjacent forward ratios and between the reverse and first forward ratio. For example, the ratio step between the first and second forward ratios is 1.62. 
     Those skilled in the art of planetary transmissions will recognize that the numerical value of the reverse speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  840 . The numerical values of the first and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  830  and  840 . The numerical values of the second and fourth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  820 ,  830  and  840 . The numerical value of the third forward speed ratio is 1. 
     The powertrain  910 , shown in FIG. 10 a , includes the conventional engine and torque converter  12 , a planetary transmission  914 , and the conventional final drive mechanism  16 . The engine and torque converter  12  are drivingly connected with the planetary transmission  914  through the input shaft  17 . The planetary transmission  914  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  914  includes a planetary gear arrangement  918  that has a first planetary gear set  920 , a second planetary gear set  930 , and a third planetary gear set  940 . 
     The planetary gear set  920  includes a sun gear member  922 , a ring gear member  924 , and a planet carrier assembly  926 . The planet carrier assembly  926  includes a plurality of intermeshing pinion gears  927  that are rotatably mounted on a carrier member  929  and disposed in meshing relationship with the sun gear member  922  and the ring gear member  924 , respectively. 
     The planetary gear set  930  includes a sun gear member  932 , a ring gear member  934 , and a planet carrier assembly member  936 . The planet carrier assembly member  936  includes a plurality of pinion gears  937  rotatably mounted on a carrier member  939  and disposed in meshing relationship with both the sun gear member  932  and the ring gear member  934 . 
     The planetary gear set  940  includes a sun gear member  942 , a ring gear member  944 , and a planet carrier assembly member  946 . The planet carrier assembly member  946  includes a plurality of pinion gears  947  rotatably mounted on a carrier member  949  and disposed in meshing relationship with both the sun gear member  942  and the ring gear member  944 . 
     The planetary gear arrangement  918  also includes four torque transmitting mechanisms  950 ,  952 ,  954  and  956 . The torque transmitting mechanism  950  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  952 ,  954  and  956  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  942 , and the output shaft  19  is continuously connected with the planet carrier assembly member  936 . The ring gear member  924  is continuously connected with the sun gear member  932  through the interconnecting member  970 . The ring gear member  934  is continuously connected with the sun gear member  942  through the interconnecting member  972 . The sun gear member  922  is continuously connected to the transmission housing  960 . 
     The planet carrier assembly member  946  is selectively connectable with the transmission housing  960  through the brake  950 . The planet carrier assembly member  926  is selectively connectable with the ring gear member  944  through the clutch  952 . The sun gear member  932  is selectively connectable with the ring gear member  944  through the clutch  954 . The planet carrier assembly member  936  is selectively connectable with the ring gear member  944  through the clutch  956 . 
     The truth table of FIG. 10 b  describes the torque transmitting mechanism engagement sequence utilized to provide the reverse speed ratio and five forward speed ratios. The truth table also provides a set of examples for the ratios for each of the reverse and forward speed ratios. These numerical values have been determined utilizing the ring gear/sun gear tooth ratios given in FIG. 10 b . The R1/S1 value is the tooth ratio of the planetary gear set  920 ; the R2/S2 value is the tooth ratio of the planetary gear set  930 ; and the R3/S3 value is the tooth ratio of the planetary gear set  940 . It can also be determined from the truth table of FIG. 10 b  that each of the forward single step and double step ratio interchanges are of the single transition variety. 
     Those skilled in the art, upon reviewing the engagement combinations, will recognize that the numerical value of the reverse speed ratio is determined utilizing the tooth ratio of the planetary gear set  940 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  920 ,  930  and  940 . The numerical value of the second forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  930  and  940 . The numerical value of the third forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  930 . The numerical value of the fourth forward speed ratio is 1. The numerical value of the fifth forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  920  and  930 . 
     A powertrain  1010 , shown in FIG. 11 a , includes the conventional engine and torque converter  12 , a planetary transmission  1014 , and the conventional final drive mechanism  16 . The engine and torque converter are drivingly connected with the planetary transmission  1014  through the input shaft  17 . The planetary transmission  1014  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  1014  includes a planetary gear arrangement  1018  that has a first planetary gear set  1020 , a second planetary gear set  1030 , and a third planetary gear set  1040 . 
     The planetary gear set  1020  includes a sun gear member  1022 , a ring gear member  1024 , and a planet carrier assembly  1026 . The planet carrier assembly  1026  includes a plurality of pinion gears  1027  rotatably mounted on a carrier member  1029  and disposed in meshing relationship with both the sun gear member  1022  and the ring gear member  1024 . 
     The planetary gear set  1030  includes a sun gear member  1032 , a ring gear member  1034 , and a planet carrier assembly member  1036 . The planet carrier assembly member  1036  includes a plurality of pinion gears  1037  rotatably mounted on a carrier member  1039  and disposed in meshing relationship with both the sun gear member  1032  and the ring gear member  1034 . 
     The planetary gear set  1040  includes a sun gear member  1042 , a ring gear member  1044 , and a planet carrier assembly member  1046 . The planet carrier assembly member  1046  includes a plurality of pinion gears  1047  rotatably mounted on a carrier member  1049  and disposed in meshing relationship with both the sun gear member  1042  and the ring gear member  1044 . 
     The planetary gear arrangement  1018  also includes four torque transmitting mechanisms  1050 ,  1052 ,  1054  and  1056 . The torque transmitting mechanism  1050  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  1052 ,  1054  and  1056  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  1022 , and the output shaft  19  is continuously connected with the ring gear member  1044 . The planet carrier assembly member  1026  is continuously connected with the planet carrier assembly member  1036  through the interconnecting member  1070 . The ring gear member  1034  is continuously connected with the sun gear member  1042  through the interconnecting member  1072 . The ring gear member  1024  is continuously connected to the transmission housing  1060 . 
     The sun gear member  1032  is selectively connectable with the transmission housing  1060  through the brake  1050 . The planet carrier assembly member  1046  is selectively connectable with the sun gear member  1022  through the clutch  1052 . The planet carrier assembly member  1046  is selectively connectable with the sun gear member  1042  through the clutch  1054 . The sun gear member  1032  is selectively connectable with the planet carrier assembly member  1046  through the clutch  1056 . 
     The truth table shown in FIG. 11 b  describes the engagement combinations and the engagement sequence necessary to provide the reverse drive ratio and the five forward speed ratios. A sample of the numerical values for the ratios is also provided in the truth table of FIG. 11 b . These values are determined utilizing the ring gear/sun gear tooth ratios also given in FIG. 11 b . The R1/S1 value is the tooth ratio for the planetary gear set  1020 ; the R2/S2 value is the tooth ratio for the planetary gear set  1030 ; and the R3/S3 value is the tooth ratio for the planetary gear set  1040 . Also given in FIG. 11 b  is a chart describing the step ratios between the adjacent forward speed ratios and the reverse to first forward speed ratio. 
     Those skilled in the art will recognize that the numerical values of the reverse, fourth and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1020 ,  1030  and  1040 . The numerical values of the first and second forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1020  and  1030 . The numerical value of the third forward speed ratio is 1. 
     A powertrain  1110 , shown in FIG. 12 a , includes the conventional engine and torque converter  12 , a planetary transmission  1114 , and the conventional final drive mechanism  16 . The engine and torque converter are drivingly connected with the planetary transmission  1114  through the input shaft  17 . The planetary transmission  1114  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  1114  includes a planetary gear arrangement  1118  that has a first planetary gear set  1120 , a second planetary gear set  1130 , and a third planetary gear set  1140 . 
     The planetary gear set  1120  includes a sun gear member  1122 , a ring gear member  1124 , and a planet carrier assembly  1126 . The planet carrier assembly  1126  includes a plurality of pinion gears  1127  rotatably mounted on a carrier member  1129  and disposed in meshing relationship with both the sun gear member  1122  and the ring gear member  1124 . 
     The planetary gear set  1130  includes a sun gear member  1132 , a ring gear member  1134 , and a planet carrier assembly member  1136 . The planet carrier assembly member  1136  includes a plurality of pinion gears  1137  rotatably mounted on a carrier member  1139  and disposed in meshing relationship with both the sun gear member  1132  and the ring gear member  1134 . 
     The planetary gear set  1140  includes a sun gear member  1142 , a ring gear member  1144 , and a planet carrier assembly member  1146 . The planet carrier assembly member  1146  includes a plurality of pinion gears  1147  rotatably mounted on a carrier member  1149  and disposed in meshing relationship with both the sun gear member  1142  and the ring gear member  1144 . 
     The planetary gear arrangement  1118  also includes four torque transmitting mechanisms  1150 ,  1152 ,  1154  and  1156 . The torque transmitting mechanism  1150  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  1152 ,  1154  and  1156  are rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the ring gear member  1144 , and the output shaft  19  is continuously connected with the planet carrier assembly member  1146 . The ring gear member  1124  is continuously connected with the planet carrier assembly member  1136  through the interconnecting member  1170 . The ring gear member  1134  is continuously connected with the sun gear member  1142  through the interconnecting member  1172 . The planet carrier assembly member  1126  is continuously connected to the transmission housing  1160 . 
     The sun gear member  1132  is selectively connectable with the transmission housing  1160  through the brake  1150 . The sun gear member  1122  is selectively connectable with the ring gear member  1144  through the clutch  1152 . The planet carrier assembly member  1136  is selectively connectable with the ring gear member  1134  through the clutch  1154 . The planet carrier assembly member  1136  is selectively connectable with the planet carrier assembly member  1146  through the clutch  1156 . 
     The truth table shown in FIG. 12 b  describes the engagement combinations and the engagement sequence necessary to provide the reverse drive ratio and the five forward speed ratios. A sample of the numerical values for the ratios is also provided in the truth table of FIG. 12 b . These values are determined utilizing the ring gear/sun gear tooth ratios also given in FIG. 12 b . The R1/S1 value is the tooth ratio for the planetary gear set  1120 ; the R2/S2 value is the tooth ratio for the planetary gear set  1130 ; and the R3/S3 value is the tooth ratio for the planetary gear set  1140 . Also given in FIG. 12 b  is a chart describing the step ratios between the adjacent forward speed ratios and the reverse to first forward speed ratio. 
     One skilled in the art will recognize that the numerical value of the reverse speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  1120 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1120 ,  1130  and  1140 . The numerical value of the second forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1120  and  1140 . The numerical value of the third forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  1140 . The numerical value of the fourth forward speed ratio is 1. The numerical value of the fifth forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1130  and  1140 . 
     A powertrain  1210 , shown in FIG. 13 a , includes the conventional engine and torque converter  12 , a planetary transmission  1214 , and the conventional final drive mechanism  16 . The engine and torque converter are drivingly connected with the planetary transmission  1214  through the input shaft  17 . The planetary transmission  1214  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  1214  includes a planetary gear arrangement  1218  that has a first planetary gear set  1220 , a second planetary gear set  1230 , and a third planetary gear set  1240 . 
     The planetary gear set  1220  includes a sun gear member  1222 , a ring gear member  1224 , and a planet carrier assembly  1226 . The planet carrier assembly  1226  includes a plurality of pinion gears  1227  and  1228  rotatably mounted on a carrier member  1229  and disposed in meshing relationship with both the sun gear member  1222  and the ring gear member  1224 . 
     The planetary gear set  1230  includes a sun gear member  1232 , a ring gear member  1234 , and a planet carrier assembly member  1236 . The planet carrier assembly member  1236  includes a plurality of pinion gears  1237  rotatably mounted on a carrier member  1239  and disposed in meshing relationship with both the sun gear member  1232  and the ring gear member  1234 . 
     The planetary gear set  1240  includes a sun gear member  1242 , a ring gear member  1244 , and a planet carrier assembly member  1246 . The planet carrier assembly member  1246  includes a plurality of pinion gears  1247  rotatably mounted on a carrier member  1249  and disposed in meshing relationship with both the sun gear member  1242  and the ring gear member  1244 . 
     The planetary gear arrangement  1218  also includes four torque transmitting mechanisms  1250 ,  1252 ,  1254  and  1256 . The torque transmitting mechanism  1250  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  1252 ,  1254  and  1256  are of the rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  1222 , and the output shaft  19  is continuously connected with the planet carrier assembly member  1246 . The ring gear member  1224  is continuously connected with the ring gear member  1234  through the interconnecting member  1270 . The sun gear member  1232  is continuously connected with the ring gear member  1244  through the interconnecting member  1272 . The planet carrier assembly member  1226  is continuously connected to the transmission housing  1260 . 
     The sun gear member  1242  is selectively connectable with the transmission housing  1260  through the brake  1250 . The sun gear member  1222  is selectively connectable with the planet carrier assembly member  1236  through the clutch  1252 . The planet carrier assembly member  1236  is selectively connectable with the planet carrier assembly member  1246  through the clutch  1254 . The planet carrier assembly member  1236  is selectively connectable with the sun gear member  1242  through the clutch  1256 . 
     The truth table shown in FIG. 13 b  describes the engagement combinations and the engagement sequence necessary to provide the reverse drive ratio and the five forward speed ratios. A sample of the numerical values for the ratios is also provided in the truth table of FIG. 13 b . These values are determined utilizing the ring gear/sun gear tooth ratios also given in FIG. 13 b . The R1/S1 value is the tooth ratio for the planetary gear set  1220 ; the R2/S2 value is the tooth ratio for the planetary gear set  1230 ; and the R3/S3 value is the tooth ratio for the planetary gear set  1240 . Also given in FIG. 13 b  is a chart describing the step ratios between the adjacent forward speed ratios and the reverse to first forward speed ratio. 
     One skilled in the art will recognize that the numerical values of the reverse, second, fourth and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1220 ,  1230  and  1240 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  1120 . The numerical value of the third forward speed ratio is 1. 
     A powertrain  1310 , shown in FIG. 14 a , includes the conventional engine and torque converter  12 , a planetary transmission  1314 , and the conventional final drive mechanism  16 . The engine and torque converter are drivingly connected with the planetary transmission  1314  through the input shaft  17 . The planetary transmission  1314  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  1314  includes a planetary gear arrangement  1318  that has a first planetary gear set  1320 , a second planetary gear set  1330 , and a third planetary gear set  1340 . 
     The planetary gear set  1320  includes a sun gear member  1322 , a ring gear member  1324 , and a planet carrier assembly  1326 . The planet carrier assembly  1326  includes a plurality of pinion gears  1327  rotatably mounted on a carrier member  1329  and disposed in meshing relationship with both the sun gear member  1322  and the ring gear member  1324 . 
     The planetary gear set  1330  includes a sun gear member  1332 , a ring gear member  1334 , and a planet carrier assembly member  1336 . The planet carrier assembly member  1336  includes a plurality of pinion gears  1337  rotatably mounted on a carrier member  1339  and disposed in meshing relationship with both the sun gear member  1332  and the ring gear member  1334 . 
     The planetary gear set  1340  includes a sun gear member  1342 , a ring gear member  1344 , and a planet carrier assembly member  1346 . The planet carrier assembly member  1346  includes a plurality of pinion gears  1347  rotatably mounted on a carrier member  1349  and disposed in meshing relationship with both the sun gear member  1342  and the ring gear member  1344 . 
     The planetary gear arrangement  1318  also includes four torque transmitting mechanisms  1350 ,  1352 ,  1354  and  1356 . The torque transmitting mechanism  1350  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  1352 ,  1354  and  1356  are of the rotating-type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  1342 , and the output shaft  19  is continuously connected with the ring gear member  1344 . The ring gear member  1324  is continuously connected with the planet carrier assembly member  1336  through the interconnecting member  1370 . The ring gear member  1334  is continuously connected with the planet carrier assembly member  1346  through the interconnecting member  1372 . The sun gear member  1322  is continuously connected to the transmission housing  1360 . 
     The sun gear member  1332  is selectively connectable with the transmission housing  1360  through the brake  1350 . The planet carrier assembly member  1326  is selectively connectable with the ring gear member  1344  through the clutch  1352 . The planet carrier assembly member  1336  is selectively connectable with the sun gear member  1332  through the clutch  1354 . The planet carrier assembly member  1336  is selectively connectable with the sun gear member  1342  through the clutch  1356 . 
     The truth table shown in FIG. 14 b  describes the engagement combinations and the engagement sequence necessary to provide the reverse drive ratio and the five forward speed ratios. A sample of the numerical values for the ratios is also provided in the truth table of FIG. 14 b . These values are determined utilizing the ring gear/sun gear tooth ratios also given in FIG. 14 b . The R1/S1 value is the tooth ratio for the planetary gear set  1320 ; the R2/S2 value is the tooth ratio for the planetary gear set  1330 ; and the R3/S3 value is the tooth ratio for the planetary gear set  1340 . Also given in FIG. 14 b  is a chart describing the step ratios between the adjacent forward speed ratios and the reverse to first forward speed ratio. 
     One skilled in the art will recognize that the numerical value of the reverse speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  1340 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1320 ,  1330  and  1340 . The numerical value of the second forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1320  and  1340 . The numerical value of the third forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  1320 . The numerical value of the fourth forward speed ratio is 1. The numerical value of the fifth forward speed ratio is determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1330  and  1340 . 
     A powertrain  1410 , shown in FIG. 15 a , includes the conventional engine and torque converter  12 , a planetary transmission  1414 , and the conventional final drive mechanism  16 . The engine and torque converter are drivingly connected with the planetary transmission  1414  through the input shaft  17 . The planetary transmission  1414  is drivingly connected with the final drive mechanism  16  through the output shaft  19 . The planetary transmission  1414  includes a planetary gear arrangement  1418  that has a first planetary gear set  1420 , a second planetary gear set  1430 , and a third planetary gear set  1440 . 
     The planetary gear set  1420  includes a sun gear member  1422 , a ring gear member  1424 , and a planet carrier assembly  1426 . The planet carrier assembly  1426  includes a plurality of pinion gears  1427  rotatably mounted on a carrier member  1429  and disposed in meshing relationship with both the sun gear member  1422  and the ring gear member  1424 . 
     The planetary gear set  1430  includes a sun gear member  1432 , a ring gear member  1434 , and a planet carrier assembly member  1436 . The planet carrier assembly member  1436  includes a plurality of pinion gears  1437  rotatably mounted on a carrier member  1439  and disposed in meshing relationship with both the sun gear member  1432  and the ring gear member  1434 . 
     The planetary gear set  1440  includes a sun gear member  1442 , a ring gear member  1444 , and a planet carrier assembly member  1446 . The planet carrier assembly member  1446  includes a plurality of pinion gears  1447  rotatably mounted on a carrier member  1449  and disposed in meshing relationship with both the sun gear member  1442  and the ring gear member  1444 . 
     The planetary gear arrangement  1418  also includes four torque transmitting mechanisms  1450 ,  1452 ,  1454  and  1456 . The torque transmitting mechanism  1450  is a stationary type torque transmitting mechanism, commonly termed a brake or reaction clutch. The torque transmitting mechanisms  1452 ,  1454  and  1456  are of the rotating type torque transmitting mechanisms, commonly termed clutches. 
     The input shaft  17  is continuously connected with the sun gear member  1442 , and the output shaft  19  is continuously connected with the sun gear member  1432 . The ring gear member  1424  is continuously connected with the planet carrier assembly member  1436  through the interconnecting member  1470 . The ring gear member  1434  is continuously connected with the planet carrier assembly member  1446  through the interconnecting member  1472 . The sun gear member  1422  is continuously connected to the transmission housing  1460 . 
     The ring gear member  1444  is selectively connectable with the transmission housing  1460  through the brake  1450 . The planet carrier assembly member  1426  is selectively connectable with the ring gear member  1444  through the clutch  1452 . The planet carrier assembly member  1436  is selectively connectable with the ring gear member  1434  through the clutch  1454 . The planet carrier assembly member  1436  is selectively connectable with the sun gear member  1442  through the clutch  1456 . 
     The truth table shown in FIG. 15 b  describes the engagement combinations and the engagement sequence necessary to provide the reverse drive ratio and the five forward speed ratios. A sample of the numerical values for the ratios is also provided in the truth table of FIG. 15 b . These values are determined utilizing the ring gear/sun gear tooth ratios also given in FIG. 15 b . The R1/S1 value is the tooth ratio for the planetary gear set  1420 ; the R2/S2 value is the tooth ratio for the planetary gear set  1430 ; and the R3/S3 value is the tooth ratio for the planetary gear set  1440 . Also given in FIG. 15 b  is a chart describing the step ratios between the adjacent forward speed ratios and the reverse to first forward speed ratio. 
     One skilled in the art will recognize that the numerical values of the reverse and fifth forward speed ratios are determined utilizing the ring gear/sun gear tooth ratios of the planetary gear sets  1430  and  1440 . The numerical value of the first forward speed ratio is determined utilizing the ring gear/sun gear tooth ratio of the planetary gear set  1440 . The numerical values of the second and fourth forward speed ratios are determined utilizing the tooth ratios of the planetary gear sets  1420  and  1440 . The numerical value of the third forward speed ratio is 1. 
     While the best modes for carrying out the invention have been described in detail, those familiar with the art to which this invention relates will recognize various alternative designs and embodiments for practicing the invention within the scope of the appended claims.