Patent Publication Number: US-2003224901-A1

Title: Family of six-speed planetary transmissions having three planetary gearsets and three input torque-transmitting mechanisms

Description:
TECHNICAL FIELD  
       [0001] The present invention relates to planetary transmissions and, more particularly, to a family of planetary transmissions providing at least six forward speed ratios and a reverse speed ratio utilizing three planetary gearsets and five torque-transmitting mechanisms.  
       BACKGROUND OF THE INVENTION  
       [0002] Passenger vehicles include a powertrain that is comprised of an engine, multi-speed transmission, and a differential or final drive mechanism. 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 as the transmission ratios are interchanged. The number of forward speed ratios that are available in a transmission determines the number of ratio interchanges that can occur and therefore the number of times the engine torque range can be repeated.  
       [0003] 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.  
       [0004] 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 improve 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.  
       [0005] It has been suggested that the number of forward speed ratios be increased to five and even six speeds. This has been accomplished in many heavy truck powertrains. 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; U.S. Pat. No. 5,599,251 issued to Beim and McCarrick on Feb. 4, 1997, U.S. Pat. No. 6,083,135 issued to Baldwin et al. on Jul. 4, 2000, and European Patent Application No. EP 1 033 510 A1 published Jun. 9, 2000.  
       [0006] Six speed transmissions offer several advantages over four and five speed transmissions, including improved vehicle acceleration and improved fuel economy. While many trucks employ six-speed transmissions, such as Polak, passenger cars are still manufactured, for the main part, 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 Polak transmission provides six forward speed ratios with three planetary gearsets, two clutches, and three brakes. The Koivunen and Beim patents utilize six torque transmitting devices including four brakes and two clutches to establish the six forward speed ratios and one reverse ratio. The Lepelletier and the EP publications each employ three planetary gearsets, three clutches and two brakes to provide six forward speed ratios and one reverse ratio. One of the planetary gearsets in each of these publications is positioned and operated to establish two fixed speed input members for the remaining two planetary gearsets.  
       SUMMARY OF THE INVENTION  
       [0007] It is an object of the present invention to provide an improved family of transmissions providing six forward speed ratios and one reverse speed ratio.  
       [0008] In one aspect of the present invention, each of the family members incorporates three planetary gearsets and five selectively engageable torque-transmitting mechanisms.  
       [0009] In another aspect of the present invention, each of the planetary gearsets has three planetary members with a first member of the first planetary gearset being continuously interconnected with a first member of the second planetary gearset, and a first member of the third planetary gearset.  
       [0010] In another aspect of the present invention, a second interconnecting member continuously interconnects a second member of the first planetary gearset with a second member of the second planetary gearset.  
       [0011] In still another aspect of the present invention, a second member of the third planetary gearset is continuously connected with a stationary member of the transmission, such as a transmission case or housing.  
       [0012] In yet still another aspect of the present invention, a transmission output shaft is continuously connected with at least one member of one of the planetary gearsets.  
       [0013] In another aspect of the present invention, an input shaft is selectively connectible with the planetary gearsets through three selectively engageable torque-transmitting mechanisms.  
       [0014] In a further aspect of the present invention, a first of the five torque-transmitting mechanisms selectively interconnects the input shaft with a member of the first or second planetary gearset.  
       [0015] In a yet further aspect of the present invention, a second of the torque-transmitting mechanisms selectively interconnects the input shaft with at least one member of one of the planetary gearsets.  
       [0016] In still a further aspect of the present invention, a third of the torque-transmitting mechanisms selectively interconnects the input shaft with at least one member of the first, second, or third planetary gearsets.  
       [0017] In yet still a further aspect of the present invention, a fourth of the torque-transmitting mechanisms provides either a selective connection between the transmission housing and at least one member of the planetary gearsets, or a selective interconnection between a member of one of the planetary gearsets with another member of one of the planetary gearsets.  
       [0018] In a further aspect of the present invention, a fifth of the torque-transmitting mechanisms selectively interconnects a member of one of the planetary gearsets with a stationary housing or transmission case.  
       [0019] In still a further aspect of the present invention, the five torque-transmitting mechanisms are selectively engageable in combinations of two to at least establish six forward speed ratios and one reverse speed ratio between the input shaft and the output shaft of the transmission. 
     
    
    
     DESCRIPTION OF THE DRAWINGS  
     [0020]FIG. 1 is a schematic representation of a powertrain incorporating one embodiment of the present invention.  
     [0021]FIG. 2 is a truth table and chart depicting some of the operating characteristics of the embodiment of the invention shown in FIG. 1.  
     [0022]FIG. 3 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0023]FIG. 4 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 3.  
     [0024]FIG. 5 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0025]FIG. 6 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 5.  
     [0026]FIG. 7 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0027]FIG. 8 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 7.  
     [0028]FIG. 9 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0029]FIG. 10 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 9.  
     [0030]FIG. 11 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0031]FIG. 12 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 11.  
     [0032]FIG. 13 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0033]FIG. 14 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 13.  
     [0034]FIG. 15 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0035]FIG. 16 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 15.  
     [0036]FIG. 17 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0037]FIG. 18 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 17.  
     [0038]FIG. 19 is a schematic representation of a powertrain incorporating another embodiment of the present invention.  
     [0039]FIG. 20 is a truth table and chart depicting some of the operating characteristics of the embodiment shown in FIG. 19.  
    
    
     DESCRIPTION OF THE EXEMPLARY EMBODIMENTS  
     [0040] Referring to the drawings, wherein like characters represent the same or corresponding parts throughout the several views, there is seen in FIG. 1 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 , a planetary gear arrangement  18 , and an output shaft  19 . The input shaft  17  is continuously connected with the engine and torque converter  12 , and the output shaft  19  is continuously connected with the final drive mechanism  16 .  
     [0041] The planetary gear arrangement  18  includes three planetary gearsets  20 ,  30 , and  40 , and five torque-transmitting mechanisms  50 ,  52 ,  54 ,  56 , and  58 . The torque-transmitting mechanisms  50 ,  52 , and  54  are conventional rotating type torque-transmitting mechanisms, commonly termed clutches. As is well known in the art, the rotating type torque-transmitting mechanisms or clutches are fluid-operated frictional mechanisms that incorporate a plurality of friction discs and at least one operating system. The torque-transmitting mechanisms  56  and  58  are stationary type torque-transmitting mechanisms, commonly termed brakes. As is well known, these torque-transmitting mechanisms are also fluid-operated friction devices that might be of either the band type or of the disc type.  
     [0042] The planetary gearset  20  includes a sun gear member  22 , a ring gear member  24 , and a planet carrier assembly member  26 . The planet carrier assembly member  26  includes a plurality of pinion gears  27  rotatably mounted on a planet carrier  29  and disposed in meshing relationship with both the sun gear member  22  and the ring gear member  24 . The schematic representation shows a single pinion gear member  27 , however, it is well known in the art that the planet carrier  29  is designed to incorporate three or four planetary pinion gears so as to distribute the torque transmission evenly through the planet carrier assembly member  26 .  
     [0043] The planetary gearset  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 planet carrier  39  and disposed in meshing relationship with both the sun gear member  32  and the ring gear member  34 . The schematic representation shows a single pinion gear member  37 , however, it is well known in the art that the planet carrier  39  is designed to incorporate three or four planetary pinion gears so as to distribute the torque transmission evenly through the planet carrier assembly member  36 .  
     [0044] The planetary gearset  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 planet carrier  49  and disposed in meshing relationship with both the sun gear member  42  and the ring gear member  44 . The schematic representation shows a single pinion gear member  47 , however, it is well known in the art that the planet carrier  49  is designed to incorporate three or four planetary pinion gears so as to distribute the torque transmission evenly through the planet carrier assembly member  46 .  
     [0045] Each of the planetary gearsets  20 ,  30 , and  40  are of the single pinion type. Those skilled in the art will recognize that when the planet carrier assembly member of such gearsets is held stationary and the sun gear member is rotated, the ring gear member will rotate in the opposite direction. This is opposed to a double pinion planet carrier assembly member wherein the ring gear member and the sun gear member rotate in the same direction when the planet carrier assembly member is held stationary.  
     [0046] As seen in FIG. 2, the torque-transmitting mechanisms  50 ,  52 ,  54 ,  56 , and  58  are selectively engaged in combinations of two to establish a reverse speed ratio and six forward speed ratios through the planetary gear arrangement  18  between the input shaft  17  and the output shaft  19 . The truth table of FIG. 2 also provides an example of numerical values that are attainable with the planetary gear arrangement  18  when the ring gear/sun gear tooth ratios of the planetary gearsets  20 ,  30 , and  40  are given as shown in FIG. 2 as R1/S1, R2/S2, and R3/S3, respectively. Also shown in FIG. 2 is an example of the ratio steps between adjacent forward speed ratios as well as between the reverse and first forward speed ratio that are present when the given speed ratios are employed. It can be further ascertained from FIG. 2 that each of the single step forward interchanges as well as the double step forward interchanges are of the single transition variety. That is, the interchange from first to second or from first to third requires merely the swapping of a single torque-transmitting mechanism while the other torque-transmitting mechanism remains engaged through this interchange.  
     [0047] The ring gear member  24 , the sun gear member  32 , and the planet carrier assembly member  46  are continuously interconnected by interconnecting member  70 . The planet carrier assembly member  26  and the planet carrier assembly member  36  are continuously interconnected by an interconnecting member  72 . The ring gear member  34  is continuously connected with the output shaft  19 .  
     [0048] The input shaft  17  is selectively connectible with the interconnecting member  72  through the torque-transmitting mechanism  50 , selectively connectible with sun gear member  22  through the torque-transmitting mechanism  52 , and selectively connectible with the sun gear member  42  through the torque-transmitting mechanism  54 . The ring gear member  44  is continuously connected with a transmission housing  60 . The interconnecting member  72  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  56 . The interconnecting member  70  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  58 . It will be noted by those skilled in the art that the sun gear members  22  and  42  are not otherwise continuously interconnected with members of the other planetary gearsets except through the selective operation of the respective torque-transmitting mechanisms  52  and  54 .  
     [0049] As shown in the truth table in FIG. 2, the reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  54  and  58 . During the reverse speed ratio, the planet carrier assembly member  46  and sun gear member  32  are rotated at a speed determined by the speed of the sun gear member  42  and the ring gear/sun gear tooth ratio of the planetary gearset  40 . The ring gear member  34  and therefore output shaft  19  are rotated at a speed determined by the speed of the sun gear member  32  and the ring gear/sun gear tooth ratio of the planetary gearset  30 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  30  and  40 .  
     [0050] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  52  and  58 . During the first forward speed ratio, the ring gear member  24  and sun gear member  32  are rotated at a speed determined by the speed of the sun gear member  22  and the ring gear/sun gear tooth ratio of the planetary gearset  20 . The ring gear member  34  and therefore output shaft  19  are rotated at a speed determined by the speed of the sun gear member  32  and the ring gear/sun gear tooth ratio of the planetary gearset  30 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  20  and  30 .  
     [0051] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  52  and  56 . During the second forward speed ratio, the planet carrier assembly member  26  and planet carrier assembly member  36  are driven at a speed determined by the speed of the sun gear member  22  and the ring gear/sun gear tooth ratio of the planetary gearset  20 . The ring gear member  34  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  36  and the ring gear/sun gear tooth ratio of the planetary gearset  30 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  20  and  30 .  
     [0052] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  52  and  54 . During the third forward speed ratio, the planet carrier assembly member  46 , sun gear member  32 , and the ring gear member  24  are driven at a speed determined by the speed of the sun gear member  42  and the ring gear/sun gear tooth ratio of the planetary gearset  40 . The planet carrier assembly members  26  and  36  are driven at a speed determined by the speed of the sun gear member  22 , the speed of the ring gear member  24 , and the ring gear/sun gear tooth ratio of the planetary gearset  20 . The ring gear member  34  and therefore output shaft  19  are driven at a speed determined by the speed of the sun gear member  32 , the speed of the planet carrier assembly member  36 , and the ring gear/sun gear tooth ratio of the planetary gearset  30 . The numerical value of the third forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  20 ,  30 , and  40 .  
     [0053] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  50  and  52 . This combination of engagements causes the planetary gearset  20 , the planetary gearset  30 , and therefore the output shaft  19  to rotate in unison with the input shaft  17 . The fourth forward speed ratio is therefore a direct drive having a numerical of one.  
     [0054] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  50  and  54 . During the fifth forward speed ratio, the planet carrier assembly member  46 , the sun gear member  32 , and the ring gear member  34  are driven at a speed determined by the speed of the sun gear member  42  and the ring gear/sun gear tooth ratio of the planetary gearset  40 . The ring gear member  34  and therefore output shaft  19  are driven at a speed determined by the speed of the sun gear member  32 , the speed of the planet carrier assembly member  36 , and the ring gear/sun gear tooth ratio of the planetary gearset  30 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  30  and  40 .  
     [0055] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  50  and  56 . During the sixth forward speed ratio, the ring gear member  34  and therefore output shaft  19  are driven at a speed determined by the speed of the planet carrier assembly member  36  and the ring gear/sun gear tooth ratio of the planetary gearset  30 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  30 .  
     [0056] A powertrain  110 , shown in FIG. 3, includes the engine and torque converter  12 , a planetary transmission  114 , and the final drive mechanism  16 . The planetary transmission  114  includes the input shaft  17 , a planetary gear arrangement  118 , and the output shaft  19 . The planetary gear arrangement  118  includes three planetary gearsets  120 ,  130 , and  140 , and five torque-transmitting mechanisms  150 ,  152 ,  154 ,  156 , and  158 . The torque-transmitting mechanisms  150 ,  152 , and  154  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanisms  156  and  158  are stationary type torque-transmitting mechanisms.  
     [0057] The planetary gearset  120  includes a sun gear member  122 , a ring gear member  124 , and a planet carrier assembly member  126 . The planet carrier assembly member  126  includes a plurality of pinion gears  127  rotatably mounted on a planet carrier  129  and disposed in meshing relationship with both the sun gear member  122  and the ring gear member  124 .  
     [0058] The planetary gearset  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 planet carrier  139  and disposed in meshing relationship with both the sun gear member  132  and the ring gear member  134 .  
     [0059] The planetary gearset  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 planet carrier  149  and disposed in meshing relationship with both the sun gear member  142  and the ring gear member  144 .  
     [0060] The sun gear member  122 , the ring gear member  134 , and the planet carrier assembly member  146  are continuously interconnected through an interconnecting member  170  which is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  156 . The planet carrier assembly member  126  and the planet carrier assembly member  136  are continuously interconnected by an interconnecting member  172  which is selectively connectible with the input shaft  17  through the torque-transmitting mechanism  150 , and selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  158 . The sun gear member  142  is continuously connected with the transmission housing  60 . The ring gear member  124  is continuously connected with the output shaft  19 .  
     [0061] The input shaft  17  is selectively connectible with the sun gear member  132  through the torque-transmitting mechanism  152 , and selectively connectible with the ring gear member  144  through the torque-transmitting mechanism  154 . It will be noted that the sun gear member  132  and the ring gear member  144  are not otherwise continuously interconnected with members of the planetary transmission  114  except through the selectively engageable torque-transmitting mechanisms  152  and  154 , respectively.  
     [0062] As seen in the truth table of FIG. 4, the torque-transmitting mechanisms are selectively engaged in combinations of two to provide six forward speed ratios and one reverse speed ratio. The truth table indicates that the single step forward interchanges as well as the double step forward interchanges are of the single transition variety. Also given in FIG. 4 is a numerical example of the speed ratios that are available with the planetary gear arrangement  118  when the ring gear/sun gear tooth ratios of the planetary gearsets  120 ,  130 , and  140  have the values given as R1/S1, R2/S2, and R3/S3, respectively. FIG. 4 also describes the numerical value of ratio steps between adjacent forward speed ratios as well as between the reverse and first forward speed ratio when the given numerical speed values are employed.  
     [0063] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  154  and  158 . During the reverse speed ratio, the planet carrier assembly member  146 , ring gear member  134 , and sun gear member  122  are rotated at a speed determined by the speed of the ring gear member  144  and the ring gear/sun gear tooth ratio of the planetary gearset  140 . The ring gear member  124  and the output shaft  19  are rotated at a speed determined by the speed of the sun gear member  122  and the ring gear/sun gear tooth ratio of the planetary gearset  120 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  120  and  140 .  
     [0064] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  152  and  158 . During the first forward speed ratio, the ring gear member  134  and sun gear member  122  are rotated at a speed determined by the speed of the sun gear member  132  and the ring gear/sun gear tooth ratio of the planetary gearset  130 . The ring gear member  124  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  122  and the ring gear/sun gear tooth ratio of the planetary gearset  120 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  120  and  130 .  
     [0065] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  152  and  156 . During the second forward speed ratio, the planet carrier assembly members  136  and  126  are rotated at a speed determined by the speed of the sun gear member  132  and the ring gear/sun gear tooth ratio of the planetary gearset  130 . The ring gear member  124  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  126  and the ring gear/sun gear tooth ratio of the planetary gearset  120 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  120  and  130 .  
     [0066] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  152  and  154 . During the third forward speed ratio, the planet carrier assembly member  146 , the ring gear member  134 , and the sun gear member  122  are driven at a speed determined by the speed of the ring gear member  144  and the ring gear/sun gear tooth ratio of the planetary gearset  140 . The planet carrier assembly members  126  and  136  are rotated at a speed determined by the speed of the sun gear member  132 , the speed of the ring gear member  134 , and the ring gear/sun gear tooth ratio of the planetary gearset  130 . The ring gear member  124  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  122 , the speed of the planet carrier assembly member  126 , and the ring gear/sun gear tooth ratio of the planetary gearset  120 . The numerical value of the third forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  120 ,  130 , and  140 .  
     [0067] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  150  and  152 . During the fourth forward speed ratio, the planetary gearsets  130  and  120 , and therefore output shaft  19 , are rotated in unison with the input shaft  17 . The fourth forward speed ratio is a direct drive having a numerical value of one.  
     [0068] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  150  and  154 . During the fifth forward speed ratio, the planet carrier assembly member  146 , the ring gear member  134 , and sun gear member  122  are rotated at a speed determined by the speed of the ring gear member  144  and the ring gear/sun gear tooth ratio of the planetary gearset  140 . The ring gear member  124  is rotated at a speed determined by the speed of the sun gear member  122 , the speed of the planet carrier assembly member  126 , and the ring gear/sun gear tooth ratio of the planetary gearset  120 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  140  and  120 .  
     [0069] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  150  and  156 . During the sixth forward speed ratio, the planet carrier assembly member  126  is rotated by the input shaft  17 . The ring gear member  124  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  126  and the ring gear/sun gear tooth ratio of the planetary gearset  120 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  120 .  
     [0070] A powertrain  210 , shown in FIG. 5, includes the engine and torque converter  12 , a planetary transmission  214 , and the final drive mechanism  16 . The planetary transmission  214  includes the input shaft  17 , a planetary gear arrangement  218 , and the output shaft  19 . The planetary gear arrangement  218  includes three planetary gearsets  220 ,  230 , and  240 , and five torque-transmitting mechanisms  250 ,  252 ,  254 ,  256 , and  258 . The torque-transmitting mechanisms  250 ,  252 , and  254  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanisms  256  and  258  are stationary type torque-transmitting mechanisms.  
     [0071] The planetary gearset  220  includes a sun gear member  222 , a ring gear member  224 , and a planet carrier assembly member  226 . The planet carrier assembly member  226  includes a plurality of pinion gears  227  rotatably mounted on a planet carrier  229  and disposed in meshing relationship with both the sun gear member  222  and the ring gear member  224 .  
     [0072] The planetary gearset  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 planet carrier  239  and disposed in meshing relationship with both the sun gear member  232  and the ring gear member  234 .  
     [0073] The planetary gearset  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 planet carrier  249  and disposed in meshing relationship with both the sun gear member  242  and the ring gear member  244 .  
     [0074] The sun gear member  222 , the ring gear member  234 , and the planet carrier assembly member  246  are continuously interconnected by an interconnecting member  270 . The planet carrier assembly member  226  and planet carrier assembly member  236  are continuously interconnected by an interconnecting member  272  that is selectively connectible with the input shaft  17  through the torque-transmitting mechanism  250 , and selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  256 . The ring gear member  224  is continuously connected with the output shaft  19 . The sun gear member  242  is continuously connected with the transmission housing  60 . The input shaft  17  is selectively connectible with the sun gear member  232  through the torque-transmitting mechanism  252 , and selectively connectible with ring gear member  244  through the torque-transmitting mechanism  254 . The ring gear member  254  is also selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  258 .  
     [0075] As seen in FIG. 6, the torque-transmitting mechanisms are selectively engaged in combinations of two to provide six forward speed ratios and one reverse speed ratio between the input shaft  17  and the output shaft  19  through the planetary gear arrangement  218 . The single step forward interchanges as well as the double step forward interchanges are each of the single transition variety. Also given in FIG. 16 is a numerical example of speed ratios that is attainable with the planetary gear arrangement  218  when the ring gear/sun gear tooth ratios of the planetary gearsets  220 ,  230 , and  240  have the numerical values given as R1/S1, R2/S2, and R3/S3, respectively. Further information in FIG. 6 shows these numerical values for the ratio steps between adjacent forward speed ratios as well as between the reverse speed ratio and the first forward speed ratio.  
     [0076] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  254  and  256 . During the reverse speed ratio, the planet carrier assembly member  246  and the sun gear member  222  are rotated at a speed determined by the speed of the ring gear member  244  and the ring gear/sun gear tooth ratio of the planetary gearset  240 . The ring gear member  224  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  222  and the ring gear/sun gear tooth ratio of the planetary gearset  220 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  220  and  240 .  
     [0077] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  252  and  256 . During the first forward speed ratio, the ring gear member  234  and sun gear member  222  are rotated at a speed determined by the speed of the sun gear member  232  and the ring gear/sun gear tooth ratio of the planetary gearset  230 . The ring gear member  224  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  222  and the ring gear/sun gear tooth ratio of the planetary gearset  220 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  220  and  230 .  
     [0078] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  252  and  258 . During the second forward speed ratio, the planet carrier assembly members  226  and  236  are rotated at a speed determined by the speed of the of the sun gear member  232  and the ring gear/sun gear tooth ratio of the planetary gearset  230 . The ring gear member  224  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  226  and the ring gear/sun gear tooth ratio of the planetary gearset  220 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  220  and  230 .  
     [0079] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  252  and  254 . During the third forward speed ratio, the planet carrier assembly member  246 , the ring gear member  234 , and the sun gear member  222  are rotated at a speed determined by the speed of the ring gear member  244  and the ring gear/sun gear tooth ratio of the planetary gearset  240 . The planet carrier assembly member  236  and planet carrier assembly member  226  are rotated at a speed determined by the speed of the sun gear member  232 , the speed of the ring gear member  234 , and the ring gear/sun gear tooth ratio of the planetary gearset  230 . The ring gear member  224  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  222 , the speed of the planet carrier assembly member  226 , and the ring gear/sun gear tooth ratio of the planetary gearset  220 . The numerical value of the third forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  220 ,  230 , and  240 .  
     [0080] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  250  and  252 . This combination of engagements causes the planetary gearsets  230  and  220 , as well as output shaft  19 , to rotate in unison with the input shaft  17  such that the fourth forward speed ratio is a direct drive having a numerical value of one.  
     [0081] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  250  and  254 . During the fifth forward speed ratio, the planet carrier assembly member  246 , ring gear member  234 , and the sun gear member  222  are rotated at a speed determined by the speed of the ring gear member  244  and the ring gear/sun gear tooth ratio of the planetary gearset  240 . The ring gear member  224  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  226 , the speed of the sun gear member  222 , and the ring gear/sun gear tooth ratio of the planetary gearset  220 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  220  and  240 .  
     [0082] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  250  and  258 . During the sixth forward speed ratio, the planet carrier assembly member  226  is rotated by the input shaft  17 . The ring gear member  224  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  226  and the ring gear/sun gear tooth ratio of the planetary gearset  220 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  220 .  
     [0083] A powertrain  310 , shown in FIG. 7, includes the engine and torque converter  12 , a planetary transmission  314 , and the final drive mechanism  16 . The planetary transmission  314  includes the input shaft  17 , a planetary gear arrangement  318 , and the output shaft  19 . The planetary gear arrangement  318  includes three planetary gearsets  320 ,  330 , and  340 , and five torque-transmitting mechanisms  350 ,  352 ,  354 ,  356 , and  358 . The torque-transmitting mechanisms  350 ,  352 , and  354  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanisms  356  and  358  are stationary type torque-transmitting mechanisms.  
     [0084] The planetary gearset  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 planet carrier  329  and disposed in meshing relationship with both the sun gear member  322  and the ring gear member  324 .  
     [0085] The planetary gearset  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 planet carrier  339  and disposed in meshing relationship with both the sun gear member  332  and the ring gear member  334 .  
     [0086] The planetary gearset  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 planet carrier  349  and disposed in meshing relationship with both the sun gear member  342  and the ring gear member  344 .  
     [0087] The planet carrier assembly member  326 , planet carrier assembly member  336 , and the ring gear member  344  are continuously interconnected by an interconnecting member  370  which is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  356 . The sun gear member  322  and ring gear member  334  are continuously interconnected by an interconnecting member  372 , which is selectively connectible with the input shaft  17  through the torque-transmitting mechanism  350 , and selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  358 . The sun gear member  342  is continuously connected with the transmission housing  60 . The ring gear member  324  is continuously connected with the output shaft  19 . The input shaft  17  is selectively connectible with the planet carrier assembly member  346  through the torque-transmitting mechanism  354 , and with the sun gear member  332  through the torque-transmitting mechanism  352 . The sun gear member  332  and planet carrier assembly member  346  are not otherwise continuously interconnected with other members of the planetary gearsets except through the selectively engageable torque-transmitting mechanisms  352  and  354 , respectively.  
     [0088] As seen in FIG. 8, the torque-transmitting mechanisms are selectively engaged in combinations of two to establish six forward speed ratios and one reverse speed ratio between the input shaft  17  and the output shaft  19  through planetary gear arrangement  318 . The truth table of FIG. 8 also provides a numerical example of the speed ratios that are available in the planetary gear arrangement  318  when the ring gear/sun gear tooth ratios of the planetary gearsets  320 ,  330 , and  340  have the numerical values given as R1/S1, R2/S2, and R3/S3, respectively. The chart of FIG. 8 provides a numerical example of the ratio steps between adjacent forward speed ratios as well as between the reverse and first forward speed ratio. These numerical values are separated from the speed ratios given in the truth table.  
     [0089] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  350  and  356 . During the reverse speed ratio, the sun gear member  322  is driven by the input shaft  17 . The planet carrier assembly member  326  is held stationary by the torque-transmitting mechanism  356 , and the ring gear member  324  is driven at a speed determined by the speed of the sun gear member  322  and the ring gear/sun gear tooth ratio of the planetary gearset  320 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  320 .  
     [0090] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  352  and  35 . During the first forward speed ratio, the ring gear member  334  and sun gear member  322  are rotated at a speed determined by the speed of the sun gear member  332  and the ring gear/sun gear tooth ratio of the planetary gearset  330 . The ring gear member  324  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  322  and the ring gear/sun gear tooth ratio of the planetary gearset  320 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearset  320  and  330 .  
     [0091] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  352  and  358 . During the second forward speed ratio, the planet carrier assembly member  336  and planet carrier assembly member  326  are rotated at a speed determined by the speed of the sun gear member  332  and the ring gear/sun gear tooth ratio of the planetary gearset  330 . The ring gear member  324  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  326  and the ring gear/sun gear tooth ratio of the planetary gearset  320 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  320  and  330 .  
     [0092] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  350  and  352 . During the third forward speed ratio, the planetary gearsets  320  and  330 , as well as output shaft  19 , are driven in unison with the input shaft  17  such that the third forward speed ratio is a direct drive having a numerical value of one.  
     [0093] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  352  and  354 . During the fourth forward speed ratio, the ring gear member  344 , the planet carrier assembly member  336 , and the planet carrier assembly member  326  are rotated at a speed determined by the speed of the planet carrier assembly member  346  and the ring gear/sun gear tooth ratio of the planetary gearset  340 . The ring gear member  334  and sun gear member  322  are rotated at a speed determined by the speed of the sun gear member  332 , the speed of the planet carrier assembly member  336 , and the ring gear/sun gear tooth ratio of the planetary gearset  330 . The ring gear member  324  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  322 , the speed of the planet carrier assembly member  326 , and the ring gear/sun gear tooth ratio of the planetary gearset  320 . The numerical value of the fourth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  320 ,  330 , and  340 .  
     [0094] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  350  and  354 . During the fifth forward speed ratio, both the planet carrier assembly member  346  and the sun gear member  322  are driven directly by the input shaft  17 . The ring gear member  344  and planet carrier assembly member  326  are rotated at a speed determined by the speed of the planet carrier assembly member  346  and the ring gear/sun gear tooth ratio of the planetary gearset  340 . The ring gear member  324  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  322 , the speed of the planet carrier assembly member  326 , and the ring gear/sun gear tooth ratio of the planetary gearset  320 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  320  and  340 .  
     [0095] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  354  and  358 . During the sixth forward speed ratio, the ring gear member  344  and planet carrier assembly member  326  are rotated at a speed determined by the speed of the planet carrier assembly member  346  and the ring gear/sun gear tooth ratio of the planetary gearset  340 . The ring gear member  324  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  326  and the ring gear/sun gear tooth ratio of the planetary gearset  320 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  320  and  340 .  
     [0096] A powertrain  410 , shown in FIG. 9, includes the engine and torque converter  12 , a planetary transmission  414 , and the final drive mechanism  16 . The planetary transmission  414  includes the input shaft  17 , a planetary gear arrangement  418 , and the output shaft  19 . The planetary gear arrangement  418  includes three planetary gearsets  420 ,  430 , and  440 , and five torque-transmitting mechanisms  450 ,  452 ,  454 ,  456 , and  458 . The torque-transmitting mechanisms  450 ,  452 , and  454  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanisms  456  and  458  are stationary type torque-transmitting mechanisms.  
     [0097] The planetary gearset  420  includes a sun gear member  422 , a ring gear member  424 , and a planet carrier assembly member  426 . The planet carrier assembly member  426  includes a plurality of pinion gears  427  rotatably mounted on a planet carrier  429  and disposed in meshing relationship with both the sun gear member  422  and the ring gear member  424 .  
     [0098] The planetary gearset  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 planet carrier  439  and disposed in meshing relationship with both the sun gear member  432  and the ring gear member  434 .  
     [0099] The planetary gearset  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 planet carrier  449  and disposed in meshing relationship with both the sun gear member  442  and the ring gear member  444 .  
     [0100] The planet carrier assembly member  426 , the planet carrier assembly member  436 , and the ring gear member  444  are continuously interconnected by the interconnecting member  470 . The sun gear member  422  and ring gear member  434  are continuously interconnected by an interconnecting member  472 , which is selectively connectible with the input shaft  17  through the torque-transmitting mechanism  450 , and selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  456 . The sun gear member  442  is continuously connected with the transmission housing  60  and the ring gear member  424  is continuously connected with the output shaft  19 .  
     [0101] The input shaft  17  is selectively connectible with the sun gear member  432  through the torque-transmitting mechanism  452 , and selectively connectible with the planet carrier assembly member  446  through the torque-transmitting mechanism  454 . The planet carrier assembly member  446  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  458 . Both the sun gear member  432  and planet carrier assembly member  446  are not continuously interconnected with other members of the planetary gearsets except by way of the torque-transmitting mechanisms connected therewith.  
     [0102] The torque-transmitting mechanisms are engaged in combinations of two to establish six forward speed ratios and one reverse speed ratio between the input shaft  17  and the output shaft  19  as shown in the truth table of FIG. 10. Also described in the truth table is the numerical example of the speed ratios that are available in the planetary gear arrangement  418  when the numerical values of the ring gear/sun gear tooth ratios of the planetary gearsets  420 ,  430 , and  440  are as given in R1/S1, R2/S2, and R3/S3, respectively. Also provided in FIG. 10 is the numerical value of the ratio steps between adjacent forward speed ratios and between the reverse and first forward speed ratio. It is also evident from the truth table, as with the other family members previously described, that each of the single step forward interchanges and the double step forward interchanges are of the single transition variety.  
     [0103] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  450  and  458 . During the reverse speed ratio, the sun gear member  422  is driven by the input shaft  17 , and the planet carrier assembly member  426  is held stationary. The ring gear member  424  is rotated at a speed determined by the speed of the sun gear member  422  and the ring gear/sun gear tooth ratio of the planetary gearset  420 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  420 .  
     [0104] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  452  and  458 . During the first forward speed ratio, the ring gear member  434  and sun gear member  422  are driven at a speed determined by the speed of the sun gear member  432  and the ring gear/sun gear tooth ratio of the planetary gearset  430 . The ring gear member  424  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  422  and the ring gear/sun gear tooth ratio of the planetary gearset  420 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  420  and  430 .  
     [0105] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  452  and  456 . During the second forward speed ratio, the sun gear member  432  is driven by the input shaft  17 . The planet carrier assembly member  436  and planet carrier assembly member  426  are rotated at a speed determined by the speed of the sun gear member  432  and the ring gear/sun gear tooth ratio of the planetary gearset  430 . The ring gear member  424  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  426  and the ring gear/sun gear tooth ratio of the planetary gearset  420 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  420  and  430 .  
     [0106] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  450  and  452 . This combination of engagements causes the planetary gearsets  420  and  430  as well as output shaft  19  to rotate in unison with the input shaft  17  thereby creating a 1:1 speed ratio or direct drive.  
     [0107] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  452  and  454 . During the fourth forward speed ratio, the ring gear member  444 , planet carrier assembly member  436 , and planet carrier assembly member  426  are rotated at a speed determined by the speed of the planet carrier assembly member  446  and the ring gear/sun gear tooth ratio of the planetary gearset  440 . The ring gear member  434  and sun gear member  422  are rotated at a speed determined by the speed of the of the sun gear member  432 , the speed of the planet carrier assembly member  436 , and the ring gear/sun gear tooth ratio of the planetary gearset  430 . The ring gear member  424  and therefore output shaft  19  are rotated at a speed determined by the speed of the sun gear member  422 , the speed of the planet carrier assembly member  426 , and the ring gear/sun gear tooth ratio of the planetary gearset  420 . The numerical value of the fourth forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  420 ,  430 , and  440 .  
     [0108] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  450  and  454 . During the fifth forward speed ratio, the ring gear member  444 , the planet carrier assembly member  436 , and the planet carrier assembly member  426  are driven at a speed determined by the speed of the planet carrier assembly member  446  and the ring gear/sun gear tooth ratio of the planetary gearset  440 . The ring gear member  424  and therefore output shaft  19  are rotated at a speed determined by the speed of the sun gear member  422 , the speed of the planet carrier assembly member  426 , and the ring gear/sun gear tooth ratio of the planetary gearset  420 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  420  and  440 .  
     [0109] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  454  and  456 . During the sixth forward speed ratio, the ring gear member  444 , planet carrier assembly member  436 , and planet carrier assembly member  426  are driven at a speed determined by the speed of the planet carrier assembly member  446  and the ring gear/sun gear tooth ratio of the planetary gearset  440 . The ring gear member  424  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  426  and the ring gear/sun gear tooth ratio of the planetary gearset  420 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  420  and  440 .  
     [0110] A powertrain  510 , shown in FIG. 11, includes the engine and torque converter  12 , a planetary 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 gearsets  520 ,  530 , and  540 , and five torque-transmitting mechanisms  550 ,  552 ,  554 ,  556 , and  558 . The torque-transmitting mechanisms  550 ,  552 ,  554 , and  556  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanism  558  is a stationary type torque-transmitting mechanism.  
     [0111] The planetary gearset  520  includes a sun gear member  522 , a ring gear member  524 , and a planet carrier assembly member  526 . The planet carrier assembly member  526  includes a plurality of pinion gears  527  rotatably mounted on a planet carrier  529  and disposed in meshing relationship with both the sun gear member  522  and the ring gear member  524 .  
     [0112] The planetary gearset  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 planet carrier  539  and disposed in meshing relationship with both the sun gear member  532  and the ring gear member  534 .  
     [0113] The planetary gearset  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 planet carrier  549  and disposed in meshing relationship with both the sun gear member  542  and the ring gear member  544 .  
     [0114] The sun gear member  522 , the ring gear member  534 , and the planet carrier assembly member  546  are continuously interconnected by an interconnecting member  570 . The planet carrier assembly member  526  and planet carrier assembly member  536  are continuously interconnected by an interconnecting member  572 . The sun gear member  542  is continuously connected with the transmission housing  60 . The ring gear member  524  is continuously connected with the output shaft  19 .  
     [0115] The input shaft  17  is selectively connectible with the interconnecting member  572  through the torque-transmitting mechanism  550 , selectively connectible with the sun gear member  532  through the torque-transmitting mechanism  552 , and selectively connectible with the ring gear member  544  through the torque-transmitting mechanism  554 . The ring gear member  544  is selectively connectible with the interconnecting member  570  through the torque-transmitting mechanism  556 . The interconnecting member  572  is selectively connectible with ground or the transmission housing  60  through the torque-transmitting mechanism  558 . It should be noted that the torque-transmitting mechanism  556  interconnects the ring gear member  544  and planet carrier assembly member  546  such that the planetary gearset  540  will be held stationary due to the fact that the sun gear member  542  is held stationary. In this arrangement, the torque-transmitting mechanism  556  essentially operates as a brake and holds the interconnecting member  570  stationary.  
     [0116] The torque-transmitting mechanisms are selectively engaged in combinations of two to establish six forward speed ratios and one reverse speed ratio as shown in the truth table of FIG. 12. Also given in FIG. 12 is a numerical example of the speed ratios that are available with the planetary gear arrangement  518  when the ring gear/sun gear tooth ratios of the planetary gearsets  520 ,  530 , and  540  have these values given as R1/S1, R2/S2, and R3/S3, respectively. FIG. 12 also provides an example of the ratio steps available between adjacent forward speed ratios as well as between the reverse and first forward speed ratio when the numerical speed ratios of the truth table are employed. The truth table further indicates that each of the single step forward interchanges as well as the double step forward interchanges are of the single transition variety.  
     [0117] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  554  and  558 . During the reverse speed ratio, the planet carrier assembly member  546 , the ring gear member  534 , and the sun gear member  522  are rotated at a speed determined by the speed of the ring gear member  544  and the ring gear/sun gear tooth ratio of the planetary gearset  540 . The ring gear member  524  and therefore output shaft  19  are rotated at a speed determined by the speed of the sun gear member  522  and the ring gear/sun gear tooth ratio of the planetary gearset  520 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  540  and  520 .  
     [0118] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  552  and  558 . During the first forward speed ratio, the ring gear member  534  and sun gear member  522  are rotated at a speed determined by the speed of the sun gear member  532  and the ring gear/sun gear tooth ratio of the planetary gearset  530 . The ring gear member  524  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  522  and the ring gear/sun gear tooth ratio of the planetary gearset  520 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  520  and  530 .  
     [0119] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  552  and  556 . As previously mentioned, the torque-transmitting mechanism  556  is effective to hold the interconnecting member  570  stationary. The planet carrier assembly member  536  and planet carrier assembly member  526  are rotated at a speed determined by the speed of the sun gear member  532  and the ring gear/sun gear tooth ratio of the planetary gearset  530 . The ring gear member  524  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  522  and the ring gear/sun gear tooth ratio of the planetary gearset  520 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  520  and  530 .  
     [0120] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  552  and  554 . During the third forward speed ratio, the ring gear member  544  and the sun gear member  532  are driven by the input shaft  17 . The planet carrier assembly member  546 , the ring gear member  534 , and the sun gear member  522  are rotated at a speed determined by the speed of the ring gear member  544  and the ring gear/sun gear tooth ratio of the planetary gearset  540 . The planet carrier assembly member  536  and planet carrier assembly member  526  are rotated at a speed determined by the speed of the sun gear member  532 , the speed of the ring gear member  534  and the ring gear/sun gear tooth ratio of the planetary gearset  530 . The ring gear member  524  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  522 , the speed of the planet carrier assembly member  526 , and the ring gear/sun gear tooth ratio of the planetary gearset  520 . The numerical value of the third forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  520 ,  530 , and  540 .  
     [0121] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  550  and  552 . This combination of engagements causes the planetary gearset  530 , the planetary gearset  520 , and the output shaft  19  to rotate as a single unit. The speed of these units is equal to the speed of the input shaft  17  such that the fourth forward speed ratio is a direct drive having a 1:1 ratio.  
     [0122] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  550  and  554 . During the fifth forward speed ratio, the planet carrier assembly member  546 , the ring gear member  534 , and the sun gear member  522  are rotated at a speed determined by the speed of the ring gear member  544  and the ring gear/sun gear tooth ratio of the planetary gearset  540 . The ring gear member  524  and therefore output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  526 , the speed of the sun gear member  522 , and the ring gear/sun gear tooth ratio of the planetary gearset  520 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  520  and  540 .  
     [0123] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  550  and  556 . During the sixth forward speed ratio, the ring gear member  524  and therefore output shaft  19  are driven at a speed determined by the speed of the planet carrier assembly member  526  and the ring gear/sun gear tooth ratio of the planetary gearset  520 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  520 .  
     [0124] A powertrain  610 , shown in FIG. 13, includes 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 gearsets  620 ,  630 , and  640 , and five torque-transmitting mechanisms  650 ,  652 ,  654 ,  656 , and  658 . The torque-transmitting mechanisms  650 ,  652 ,  654 , and  656  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanism  658  is a stationary type torque-transmitting mechanism.  
     [0125] The planetary gearset  620  includes a sun gear member  622 , a ring gear member  624 , and a planet carrier assembly member  626 . The planet carrier assembly member  626  includes a plurality of pinion gears  627  rotatably mounted on a planet carrier  629  and disposed in meshing relationship with both the sun gear member  622  and the ring gear member  624 .  
     [0126] The planetary gearset  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 planet carrier  639  and disposed in meshing relationship with both the sun gear member  632  and the ring gear member  634 .  
     [0127] The planetary gearset  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 planet carrier  649  and disposed in meshing relationship with both the sun gear member  642  and the ring gear member  644 .  
     [0128] The planet carrier assembly member  626 , the planet carrier assembly member  636 , and the ring gear member  644  are continuously interconnected by an interconnecting member  670 . The sun gear member  622  and the ring gear member  634  are continuously interconnected by an interconnecting member  672 . The sun gear member  642  is continuously connected with the transmission housing  60 . The output shaft  19  is continuously connected with the ring gear member  624 .  
     [0129] The input shaft  17  is selectively connectible with the interconnecting member  672  through the torque-transmitting mechanism  650 , selectively connectible with the sun gear member  632  through the torque-transmitting mechanism  652 , and selectively connectible with the planet carrier assembly member  646  through the torque-transmitting mechanism  654 . The planet carrier assembly member  654  is selectively connectible with the interconnecting member  670 . As with the previous family member, the engagement of the torque-transmitting mechanism  656  will hold the planetary gearset  640  as well as the interconnecting member  670  stationary. The interconnecting member  672  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  658 .  
     [0130] As seen in the truth table of FIG. 14, the torque-transmitting mechanisms are selectively engaged in combinations of two to provide six forward speed ratios and one reverse speed ratio through the planetary gear arrangement  618  between the input shaft  17  and the output shaft  19 . A numerical example of available speed ratios with the planetary gear arrangement  618  are given in FIG. 14. These numerical values are determined utilizing the ring gear/sun gear tooth ratios of the planetary gearsets  620 ,  630 , and  640 . These numerical values are determined when values of the ring gear/sun gear tooth ratios of the planetary gearsets  620 ,  630 , and  640  are equal to R1/S1, R2/S2, and R3/S3, respectively. Also given in FIG. 14 is a chart of the ratio steps between adjacent forward speed ratios as well as between the reverse and first forward speed ratio. A review of the truth table of FIG. 14 will show that each of the single step forward ratio interchanges as well as the double step forward ratio interchanges are of the single transition variety.  
     [0131] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  650  and  656 . This combination of engagements will hold the planet carrier assembly member  626  stationary and connect the sun gear member  622  with the input shaft  17 . The ring gear member  624  is rotated at a speed determined by the speed of the sun gear member  622  and the ring gear/sun gear tooth ratio of the planetary gearset  620 . The numerical of the reverse speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  620 .  
     [0132] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  652  and  656 . During the first forward speed ratio, the ring gear member  634  and sun gear member  622  are rotated at a speed determined by the speed of the sun gear member  632  and the ring gear/sun gear tooth ratio of the planetary gearset  630 . The ring gear member  624  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  622  and the ring gear/sun gear tooth ratio of the planetary gearset  620 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  620  and  630 .  
     [0133] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  652  and  658 . During the second forward speed ratio, the planet carrier assembly member  636  and planet carrier assembly member  626  are rotated at a speed determined by the speed of the sun gear member  632  and the ring gear/sun gear tooth ratio of the planetary gearset  630 . The ring gear member  624  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  626  and the ring gear/sun gear tooth ratio of the planetary gearset  620 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  620  and  630 .  
     [0134] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  650  and  652 . This combination of engagements will cause the planetary gearset  630 , the planetary gearset  620 , and the output shaft  19  to rotate as a single unit and in unison with the input shaft  17  thereby creating a direct drive having a 1:1 ratio.  
     [0135] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  652  and  654 . During the fourth forward speed ratio, the ring gear member  644 , the planet carrier assembly member  636 , and the planet carrier assembly member  626  are rotated at a speed determined by the speed of the planet carrier assembly member  646  and the ring gear/sun gear tooth ratio of the planetary gearset  640 . The ring gear member  634  and sun gear member  622  are rotated at a speed determined by the speed of the sun gear member  632 , the speed of the planet carrier assembly member  636 , and the ring gear/sun gear tooth ratio of the planetary gearset  630 . The ring gear member  624  and therefore output shaft  19  are rotated at a speed determined by the speed of the sun gear member  622 , the speed of the planet carrier assembly member  626 , and the ring gear/sun gear tooth ratio of the planetary gearset  620 . The numerical value of the fourth forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  620 ,  630 , and  640 .  
     [0136] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  650  and  654 . During the fifth forward speed ratio, the ring gear member  644  and planet carrier assembly member  626  are rotated at a speed determined by the speed of the planet carrier assembly member  646  and the ring gear/sun gear tooth ratio of planetary gearset  640 . The ring gear member  624  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  626 , the speed of the sun gear member  622 , and the ring gear/sun gear tooth ratio of the planetary gearset  620 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  620  and  640 .  
     [0137] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  654  and  658 . During the sixth forward speed ratio, the ring gear member  644  and planet carrier assembly member  626  are rotated at a speed determined by the speed of the planet carrier assembly member  646  and the ring gear/sun gear tooth ratio of the planetary gearset  640 . The ring gear member  624  and therefore output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  626  and the ring gear/sun gear tooth ratio of the planetary gearset  620 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  620  and  640 .  
     [0138] A powertrain  710 , shown in FIG. 15, includes the engine and torque converter  12 , a planetary transmission  714 , and the final drive mechanism  16 . The planetary transmission  714  includes the input shaft  17 , a planetary gear arrangement  718 , and the output shaft  19 . The planetary gear arrangement  718  includes three planetary gearsets  720 ,  730 , and  740 , and five torque-transmitting mechanisms  750 ,  752 ,  754 ,  756 , and  758 . The torque-transmitting mechanisms  750 ,  752 ,  754  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanisms  756  and  758  are stationary type torque-transmitting mechanisms.  
     [0139] The planetary gearset  720  includes a sun gear member  722 , a ring gear member  724 , and a planet carrier assembly member  726 . The planet carrier assembly member  726  includes a plurality of pinion gears  727  rotatably mounted on a planet carrier  729  and disposed in meshing relationship with both the sun gear member  722  and the ring gear member  724 .  
     [0140] The planetary gearset  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 planet carrier  739  and disposed in meshing relationship with both the sun gear member  732  and the ring gear member  734 .  
     [0141] The planetary gearset  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 pairs of intermeshing pinion gears  747  and  748  that are rotatably mounted on a planet carrier  749  and disposed in meshing relationship with the sun gear member  742  and the ring gear member  744 , respectively. The planetary gearset  740  is an example of a double pinion planetary gearset.  
     [0142] The sun gear member  722 , the ring gear member  734 , and the ring gear member  744  are continuously interconnected by an interconnecting member  770 . The planet carrier assembly member  726  and the planet carrier assembly member  736  are continuously interconnected by an interconnecting member  772 . The sun gear member  742  is continuously connected with the transmission housing  60 . The ring gear member  724  is continuously connected with the output shaft  19 .  
     [0143] The input shaft  17  is selectively connectible with the interconnecting member  772  through the torque-transmitting mechanism  750 , selectively connectible with the sun gear member  732  through the torque-transmitting mechanism  752 , and selectively connectible with the planet carrier assembly member  746  through the torque-transmitting mechanism  754 . The interconnecting member  770  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  756 . The interconnecting member  772  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  758 . As with other family members, two of the members in this family; namely, the sun gear member  732  and planet carrier assembly member  746  are not continuously connected with other members of the planetary gear arrangement  718  and are only interconnectible therewith through the respective torque-transmitting mechanisms  752  and  754 .  
     [0144] As seen in truth table of FIG. 16, the torque-transmitting mechanisms are selectively engaged in combinations of two to provide six forward speed ratios and one reverse speed ratio through the planetary gear arrangement  718  between the input shaft  17  and the output shaft  19 . As noted therein, the single step forward interchanges as well as the double step forward interchanges are all of the single transition variety. Also given in the truth table is a numerical example of the ring gear/sun gear tooth ratios that can be obtained in the planetary gear arrangement  718  and the ring gear/sun gear tooth ratio values of the planetary gearsets  720 ,  730 , and  740  are as given as R1/S1, R2/S2, and R3/S3, respectively. Also seen in FIG. 16 is a chart of ratio steps between adjacent forward speed ratios and between the reverse and first forward speed ratio. As previously mentioned with other family members, this numerical value is determined from the numerical value of the speed ratios given in the truth table.  
     [0145] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  754  and  758 . During the reverse speed ratio, the ring gear member  744 , the ring gear member  734 , and sun gear member  722  are rotated at a speed determined by the speed of the planet carrier assembly member  746  and the ring gear/sun gear tooth ratio of the planetary gearset  740 . The ring gear member  724  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  722  and the ring gear/sun gear tooth ratio of the planetary gearset  720 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  720  and  740 .  
     [0146] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  752  and  758 . During the first forward speed ratio, the ring gear member  734  and sun gear member  722  are rotated at a speed determined by the speed of the sun gear member  732  and the ring gear/sun gear tooth ratio of the planetary gearset  730 . The ring gear member  724  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  722  and the ring gear/sun gear tooth ratio of the planetary gearset  720 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  730  and  720 .  
     [0147] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  752  and  756 . During the second forward speed ratio, the planet carrier assembly members  736  and  726  are rotated at a speed determined by the speed of the sun gear member  732  and the ring gear/sun gear tooth ratio of the planetary gearset  730 . The ring gear member  724  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  726  and the ring gear/sun gear tooth ratio of the planetary gearset  720 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  730  and  720 .  
     [0148] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  752  and  754 . During the third forward speed ratio, the ring gear member  744 , the ring gear member  734 , and the sun gear member  722  are rotated at a speed determined by the speed of the planet carrier assembly member  746  and the ring gear/sun gear tooth ratio of the planetary gearset  740 . The planet carrier assembly member  736  and planet carrier assembly member  726  are rotated at a speed determined by the speed of the sun gear member  732 , the speed of the ring gear member  734 , and the ring gear/sun gear tooth ratio of the planetary gearset  730 . The ring gear member  724  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  722 , the speed of the planet carrier assembly member  726 , and the ring gear/sun gear tooth ratio of the planetary gearset  720 . The numerical value of the third forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  720 ,  730 , and  740 .  
     [0149] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  750  and  752 . This combination of engagements causes the planetary gearset  730 , the planetary gearset  720 , and the output shaft  19  to rotate in unison with the input shaft  17 . Thus, the fourth forward speed ratio is a direct drive having a numerical value of one.  
     [0150] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  750  and  754 . During the fifth forward speed ratio, the ring gear member  744 , the ring gear member  734 , and the sun gear member  722  are rotated at a speed determined by the speed of the planet carrier assembly member  746  and the ring gear/sun gear tooth ratio of the planetary gearset  740 . The ring gear member  724  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  722 , the speed of the planet carrier assembly member  726 , and the ring gear/sun gear tooth ratio of the planetary gearset  720 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  720  and  740 .  
     [0151] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  750  and  756 . During the sixth forward speed ratio, the planet carrier assembly member  726  is driven by the input shaft  17 . The ring gear member  724  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  726  and the ring gear/sun gear tooth ratio of the planetary gearset  720 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  720 .  
     [0152] A powertrain  810 , shown in FIG. 17, includes the engine and torque converter  12 , a planetary transmission  814 , and the final drive mechanism  16 . The planetary transmission  814  includes the input shaft  17 , a planetary gear arrangement  818 , and the output shaft  19 . The planetary gear arrangement  818  includes three planetary gearsets  820 ,  830 , and  840 , and five torque-transmitting mechanisms  850 ,  852 ,  854 ,  856 , and  858 . The torque-transmitting mechanisms  850 ,  852 , and  854  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanisms  856  and  858  are stationary type torque-transmitting mechanisms.  
     [0153] The planetary gearset  820  includes a sun gear member  822 , a ring gear member  824 , and a planet carrier assembly member  826 . The planet carrier assembly member  826  includes a plurality of pinion gears  827  rotatably mounted on a planet carrier  829  and disposed in meshing relationship with both the sun gear member  822  and the ring gear member  824 .  
     [0154] The planetary gearset  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 pairs of intermeshing pinion gears  837  and  838  that are rotatably mounted on planet carrier  839  and disposed in meshing relationship with the sun gear member  832  and the ring gear member  834 , respectively.  
     [0155] The planetary gearset  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 planet carrier  849  and disposed in meshing relationship with both the sun gear member  842  and the ring gear member  844 .  
     [0156] The planet carrier assembly member  826 , the ring gear member  834 , and the ring gear member  844  are continuously interconnected by an interconnecting member  870 . The sun gear member  822  and planet carrier assembly member  836  are continuously interconnected by an interconnecting member  872 . The sun gear member  842  is continuously connected with the transmission housing  60 . The ring gear member  824  is continuously connected with the output shaft  19 .  
     [0157] The input shaft  17  is selectively connectible with the interconnecting member  872  through the torque-transmitting mechanism  850 , selectively connectible with the sun gear member  832  through the torque-transmitting mechanism  852 , and selectively connectible with the planet carrier assembly member  846  through the torque-transmitting mechanism  854 . The interconnecting member  870  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  856 . The interconnecting member  872  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  858 . As with the other family members described above, the sun gear member  832  and planet carrier assembly member  846  are noncontinuously connected with any other of the elements of the planetary gear arrangement  818  except through the respective torque-transmitting mechanisms  852  and  854 .  
     [0158] As seen in the truth table of FIG. 18, the torque-transmitting mechanisms are selectively engaged in combinations of two to provide six forward speed ratios and one reverse speed ratio between the input shaft  17  and the output shaft  19  through the planetary gear arrangement  818 .  
     [0159] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  850  and  856 . During the reverse speed ratio, the sun gear member  822  is driven by the input shaft  17  and the planet carrier assembly member  826  is held stationary. The ring gear member  824  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  822  and the ring gear/sun gear tooth ratio of the planetary gearset  820 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  820 .  
     [0160] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  852  and  856 . During the first forward speed ratio, the sun gear member  832  is driven by the input shaft  17 , and the ring gear member  834  and planet carrier assembly member  826  are held stationary. The planet carrier assembly member  836  and sun gear member  822  are rotated at a speed determined by the speed of the sun gear member  832  and the ring gear/sun gear tooth ratio of the planetary gearset  830 . The ring gear member  824  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  822  and the ring gear/sun gear tooth ratio of the planetary gearset  820 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  820  and  830 .  
     [0161] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  852  and  858 . During the second forward speed ratio, the ring gear member  834  and planet carrier assembly member  826  are rotated at a speed determined by the speed of the sun gear member  832  and the ring gear/sun gear tooth ratio of the planetary gearset  830 . The ring gear member  824  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  826  and the ring gear/sun gear tooth ratio of the planetary gearset  820 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  820  and  830 .  
     [0162] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  850  and  852 . During the third forward speed ratio, the planetary gearset  830 , the planetary gearset  820 , and the output shaft  19 , are driven in unison with the input shaft  17 . The third forward speed ratio is a direct drive having a numerical value of one.  
     [0163] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  852  and  854 . During the fourth forward speed ratio, the ring gear member  844 , the ring gear member  834 , and the planet carrier assembly member  826  are rotated at a speed determined by the speed of the planet carrier assembly member  846  and the ring gear/sun gear tooth ratio of the planetary gearset  840 . The planet carrier assembly member  836  and sun gear member  822  are rotated at a speed determined by the speed of the sun gear member  832 , the speed of the ring gear member  834 , and the ring gear/sun gear tooth ratio of the planetary gearset  830 . The ring gear member  824  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  822 , the speed of the planet carrier assembly member  826 , and the ring gear/sun gear tooth ratio of the planetary gearset  820 . The numerical value of the fourth forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  820 ,  830 , and  840 .  
     [0164] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  850  and  854 . During the fifth forward speed ratio, the ring gear member  844  and planet carrier assembly member  826  are rotated at a speed determined by the speed of the planet carrier assembly member  846  and the ring gear/sun gear tooth ratio of the planetary gearset  840 . The ring gear member  824  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  822 , the speed of the planet carrier assembly member  826 , and the ring gear/sun gear tooth ratio of the planetary gearset  820 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  820  and  840 .  
     [0165] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  854  and  858 . During the sixth forward speed ratio, the ring gear member  844  and planet carrier assembly member  826  are rotated at a speed determined by the speed of the planet carrier assembly member  846  and the ring gear/sun gear tooth ratio of the planetary gearset  840 . The ring gear member  824  and output shaft  19  are rotated at a speed determined by the speed of the planet carrier assembly member  826  and the ring gear/sun gear tooth ratio of the planetary gearset  820 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  820  and  840 .  
     [0166] A powertrain  910 , shown in FIG. 19, includes the engine and torque converter  12 , a planetary transmission  914 , and the final drive mechanism  16 . The planetary transmission  914  includes the input shaft  17 , a planetary gear arrangement  918 , and the output shaft  19 . The planetary gear arrangement  918  includes three planetary gearsets  920 ,  930 , and  940 , and five torque-transmitting mechanisms  950 ,  952 ,  954 ,  956 , and  958 . The torque-transmitting mechanisms  950 ,  952 ,  954 , and  956  are rotating type torque-transmitting mechanisms and the torque-transmitting mechanism  958  is a stationary type torque-transmitting mechanism.  
     [0167] The planetary gearset  920  includes a sun gear member  922 , a ring gear member  924 , and a planet carrier assembly member  926 . The planet carrier assembly member  926  includes a plurality of pairs of intermeshing pinion gears  927  and  928  that are rotatably disposed on a planet carrier  929  and meshing with the sun gear member  922  and the ring gear member  924 , respectively.  
     [0168] The planetary gearset  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 planet carrier  939  and disposed in meshing relationship with both the sun gear member  932  and the ring gear member  934 .  
     [0169] The planetary gearset  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 planet carrier  949  and disposed in meshing relationship with both the sun gear member  942  and the ring gear member  944 .  
     [0170] The sun gear member  922 , the ring gear member  934 , and planet carrier assembly member  946  are continuously interconnected by an interconnecting member  970 . The ring gear member  924  and planet carrier assembly member  936  are continuously interconnected by an interconnecting member  972 . The sun gear member  942  is continuously connected with the transmission housing  60 . The planet carrier assembly member  926  is continuously connected with the output shaft  19 .  
     [0171] The input shaft  17  is selectively connectible with the interconnecting member  972  through the torque-transmitting mechanism  950 , selectively connectible with the sun gear member  932  through the torque-transmitting mechanism  952 , and selectively connectible with the ring gear member  944  through the torque-transmitting mechanism  954 . The ring gear member  944  is selectively connectible with the interconnecting member  972  through the torque-transmitting mechanism  956 . The interconnecting member  970  is selectively connectible with the transmission housing  60  through the torque-transmitting mechanism  958 . It will be noted that the engagement of the torque-transmitting mechanism  956  will cause the planetary gearset  940  as well as the interconnecting member  970  to remain stationary with the transmission housing  60 .  
     [0172] As seen in the truth table of FIG. 20, the torque-transmitting mechanisms are engaged in combinations of two to provide six forward speed ratios and one reverse speed ratio between the input shaft  17  and output shaft  19  through planetary gear arrangement  918 . The truth table also provides an example of numerical values for the speed ratios. These numerical values are determined utilizing the values of the ring gear/sun gear tooth ratios for the planetary gearsets  920 ,  930 , and  940  as given in FIG. 20 as R1/S1, R2/S2, and R3/S3, respectively. Also provided in FIG. 20 is a chart depicting the ratio steps between adjacent forward speed ratios as well as the ratio step between reverse and the first forward speed ratio. As with the previous members described above, all of the single step and double step forward interchanges are of the single transition variety.  
     [0173] The reverse speed ratio is established with the engagement of the torque-transmitting mechanisms  954  and  958 . During the reverse speed ratio, the planet carrier assembly member  946  and sun gear member  922  are rotated at a speed determined by the speed of the ring gear member  944  and the ring gear/sun gear tooth ratio of the planetary gearset  940 . The planet carrier assembly member  926  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  922  and the ring gear/sun gear tooth ratio of the planetary gearset  920 . The numerical value of the reverse speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  920  and  940 .  
     [0174] The first forward speed ratio is established with the engagement of the torque-transmitting mechanisms  952  and  958 . During the first forward speed ratio, the ring gear member  934  and sun gear member  922  are rotated at a speed determined by the speed of the sun gear member  932  and the ring gear/sun gear tooth ratio of the planetary gearset  930 . The planet carrier assembly member  926  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  922  and the ring gear/sun gear tooth ratio of the planetary gearset  920 . The numerical value of the first forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  920  and  930 .  
     [0175] The second forward speed ratio is established with the engagement of the torque-transmitting mechanisms  952  and  956 . During the second forward speed ratio, the planet carrier assembly member  936  and ring gear member  924  are rotated at a speed determined by the speed of the sun gear member  932  and the ring gear/sun gear tooth ratio of the planetary gearset  930 . The planet carrier assembly member  926  and output shaft  19  are rotated at a speed determined by the speed of the ring gear member  924  and the ring gear/sun gear tooth ratio of the planetary gearset  920 . The numerical value of the second forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  920  and  930 .  
     [0176] The third forward speed ratio is established with the engagement of the torque-transmitting mechanisms  952  and  954 . During the third forward speed ratio, the ring gear member  944  and the sun gear member  932  are both driven by the input shaft  17 . The planet carrier assembly member  946 , the ring gear member  934 , and the sun gear member  922  are rotated at a speed determined by the speed of the ring gear member  944  and the ring gear/sun gear tooth ratio of the planetary gearset  940 . The planet carrier assembly member  936  and ring gear member  924  are rotated at a speed determined by the speed of the sun gear member  932 , the speed of the ring gear member  934 , and the ring gear/sun gear tooth ratio of the planetary gearset  930 . The planet carrier assembly member  926  and output shaft  19  are rotated at a speed determined by the speed of the sun gear member  922 , the speed of the ring gear member  924 , and the ring gear/sun gear tooth ratio of the planetary gearset  920 . The numerical value of the third forward speed ratio is determined by the ring gear/sun gear tooth ratios of all three planetary gearsets  920 ,  930 , and  940 .  
     [0177] The fourth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  950  and  952 . The fourth forward speed ratio is a direct drive having a numerical value of one.  
     [0178] The fifth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  950  and  954 . During the fifth forward speed ratio, the planet carrier assembly member  946  and ring gear member  922  are rotated at a speed determined by the speed of the ring gear member  944  and the ring gear/sun gear tooth ratio of the planetary gearset  940 . The planet carrier assembly member  926  and output shaft  19  are rotated at a speed determined by the speed of the ring gear member  924 , the speed of the sun gear member  922 , and the ring gear/sun gear tooth ratio of the planetary gearset  920 . The numerical value of the fifth forward speed ratio is determined by the ring gear/sun gear tooth ratios of the planetary gearsets  920  and  940 .  
     [0179] The sixth forward speed ratio is established with the engagement of the torque-transmitting mechanisms  950  and  956 . During the sixth forward speed ratio, the ring gear member  924  is driven by the input shaft  17 . The planet carrier assembly member  926  and therefore output shaft  19  are rotated at a speed determined by the speed of the ring gear member  924  and the ring gear/sun gear tooth ratio of the planetary gearset  920 . The numerical value of the sixth forward speed ratio is determined by the ring gear/sun gear tooth ratio of the planetary gearset  920 .  
     [0180] From the foregoing description, it will be appreciated that each of the family members has the following characteristics in common. Each family member has two planetary gearsets with three members each. The first members of each of the planetary gearsets are continuously interconnected by a first interconnecting member. The second members of the first and second planetary gearsets are continuously interconnected by an interconnecting member. The second member of the third planetary gearset is continuously connected with a transmission housing. The output shaft is continuously connected with at least one of the planetary gear members.  
     [0181] Each family member includes five torque-transmitting mechanisms three of which are selectively connectible between the input shaft and members of the planetary gearset. The remaining two torque-transmitting mechanisms act either as brakes or one of the torque-transmitting mechanisms can operate as a rotating type, however, it effectively applies a retarding force to members of the planetary gearset.  
     [0182] Also in each of the transmission family members, there are at least two planetary members that are not continuously interconnected with other members of the planetary gear arrangements except through selectively engageable torque-transmitting mechanisms.