U.S. patent application number 10/284062 was filed with the patent office on 2004-05-06 for family of multi-speed planetary transmission mechanisms having clutch input.
Invention is credited to Bucknor, Norman Kenneth, Lee, Chunhao J., Raghavan, Madhusudan, Usoro, Patrick Benedict.
Application Number | 20040087409 10/284062 |
Document ID | / |
Family ID | 32093515 |
Filed Date | 2004-05-06 |
United States Patent
Application |
20040087409 |
Kind Code |
A1 |
Lee, Chunhao J. ; et
al. |
May 6, 2004 |
FAMILY OF MULTI-SPEED PLANETARY TRANSMISSION MECHANISMS HAVING
CLUTCH INPUT
Abstract
A family of power transmissions having first, second, and third
planetary gearsets and six torque-transmitting mechanisms. The
first planetary gearset is continuously interconnected with a
member of the second planetary gearset and a member of the third
planetary gearset. The second planetary gearset is continuously
interconnected with a member of the third planetary gearset. The
six torque-transmitting mechanisms are selectively engaged in
combinations of two to establish at least seven forward speed
ratios and one reverse speed ratio within the planetary
gearsets.
Inventors: |
Lee, Chunhao J.; (Troy,
MI) ; Bucknor, Norman Kenneth; (Troy, MI) ;
Raghavan, Madhusudan; (West Bloomfield, CT) ; Usoro,
Patrick Benedict; (Troy, MI) |
Correspondence
Address: |
KATHRYN A MARRA
General Motors Corporation
Legal Staff, Mail Code 482-C23-B21
P.O. Box 300
Detroit
MI
48265-3000
US
|
Family ID: |
32093515 |
Appl. No.: |
10/284062 |
Filed: |
October 30, 2002 |
Current U.S.
Class: |
475/269 |
Current CPC
Class: |
F16H 3/66 20130101; F16H
3/666 20130101; F16H 2200/2046 20130101; F16H 2200/0056 20130101;
F16H 2200/2097 20130101; F16H 2003/445 20130101; F16H 2200/201
20130101 |
Class at
Publication: |
475/269 |
International
Class: |
F16H 003/44 |
Claims
1. A family of power transmissions wherein each family member
comprises: an input shaft; an output shaft; a transmission housing;
a first planetary gearset having first, second, and third members;
a second planetary gearset having first, second, and third members;
a third planetary gearset having first, second, and third members;
a first interconnecting member continuously interconnecting said
first member of said first planetary gearset with said first member
of said second planetary gearset; a second interconnecting member
continuously interconnecting said second member of said first
planetary gearset with said first member of said third planetary
gearset; a third interconnecting member continuously
interconnecting said second member of said second planetary gearset
with said second member of said third planetary gearset; said third
member of one of said planetary gearsets being continuously
interconnected with said transmission housing; said output shaft
being continuously interconnected with at least one member of one
of said planetary gearsets; said input shaft being only selectively
connectible with members of the planetary gearsets through
selectively engageable torque transmitting mechanisms; a first
torque-transmitting mechanism selectively interconnecting said
input shaft with at least one member of one of said planetary
gearsets; a second torque-transmitting mechanism selectively
interconnecting said input shaft with a member of a group
consisting of said first, second, and third members of said first,
second, and third planetary gearsets, said first interconnecting
member, said second interconnecting member, and said third
interconnecting member; a third torque-transmitting mechanism
selectively interconnecting a member of one of said planetary
gearsets or one of said interconnecting members with either said
input shaft, said output shaft, or another member of one of said
planetary gearsets; a fourth torque-transmitting mechanism
selectively interconnecting a member of one of said planetary
gearsets with either said input shaft, said output shaft, or
another member of said planetary gearsets; a fifth
torque-transmitting mechanism selectively interconnecting a member
of one of said planetary gearsets or one of said interconnecting
members with either another member of one of said planetary
gearsets or with said transmission housing; a sixth
torque-transmitting mechanism selectively interconnecting a member
of one of said planetary gearsets with either said output shaft,
another member of one of said planetary gearsets, or with said
transmission housing; said torque-transmitting mechanisms being
selectively engaged in combinations two to establish at least seven
forward speed ratios and one reverse speed ratio within said
planetary gearsets between said input shaft and said output
shaft.
2. The family power transmissions defined in claim 1 further
comprising: said first members of said first, second, and third
planetary gearsets being a member selected from a first group
consisting of a sun gear member, a ring gear member, and a planet
carrier assembly member; said second members of said first, second,
and third planetary gearsets being a member of a first group
consisting of a sun gear member, a ring gear member, and a planet
carrier assembly member not selected as said first member; and said
third members of said first, second, and third planetary gearsets
being a member of a first group consisting of a sun gear member, a
ring gear member, and a planet carrier assembly member not selected
as either said first member or said second member.
3. A family of power transmissions wherein each family member
comprises: an input shaft; an output shaft; a transmission housing;
a first planetary gearset having first, second, and third members;
a second planetary gearset having first, second, and third members;
a third planetary gearset having first, second, and third members;
a first interconnecting member continuously interconnecting said
first member of said first planetary gearset with said first member
of said second planetary gearset; a second interconnecting member
continuously interconnecting said second member of said first
planetary gearset with said first member of said third planetary
gearset; a third interconnecting member continuously
interconnecting said second member of said second planetary gearset
with said second member of said third planetary gearset; said
transmission housing being continuously interconnected with a
member of a group consisting of said third members of said first,
second, and third planetary gearsets; said output shaft being
continuously interconnected with a member of a group consisting of
said second interconnecting member, said third interconnecting
member, and said third member of said first, second, and third
planetary gearsets that are not connected with said housing; said
input shaft being only selectively connectible with members of the
planetary gearsets through selectively engageable torque
transmitting mechanisms; and six selectively engageable torque
transmitting mechanisms being selectively engaged in combinations
of two to establish at least seven forward speed ratios and one
reverse speed ratio between said input shaft and said output shaft,
a first of said torque transmitting mechanisms selectively
interconnecting said input shaft with a member of a group
consisting of said third members of said first, second, and third
planetary gearsets, said first interconnecting member, and said
second interconnecting member, and a second of said torque
transmitting mechanisms selectively interconnecting said input
shaft with a member of a group consisting of said second
interconnecting member, said third interconnecting member, and said
third members of said first, second, and third planetary
gearsets.
4. The family of power transmissions defined in claim 3 further
comprising: a third of said torque transmitting mechanisms
selectively interconnecting one of said input shaft and said output
shaft with a member of a group consisting of said first
interconnecting member, said second interconnecting member, said
third interconnecting member, said third member of said second
planetary gearset, and said third member of said third planetary
gearset; a fourth of said torque transmitting mechanisms
selectively interconnecting a member of a group consisting of said
third members of said first, second, and third planetary gearsets,
said second interconnecting member, and said third interconnecting
member with a member of a group consisting of said input shaft,
said output shaft, said first interconnecting member, said second
interconnecting member, said third interconnecting member; a fifth
of said torque transmitting mechanisms selectively interconnecting
a member of a group consisting of said transmission housing, said
third member of said first planetary gearset, said first
interconnecting member, said second interconnecting member, and
said third interconnecting member with a member of a group
consisting of said third member of said second planetary gearset,
said third member of said third planetary gearset, said first
interconnecting member, said second interconnecting member, said
third interconnecting member, and said output shaft; and a sixth of
said torque transmitting mechanisms selectively interconnecting a
member of a group consisting of said transmission housing, said
third member of said second planetary gearset, and said output
shaft with a member of a group consisting of said third member of
said first planetary gearset, said third member of said third
planetary gearset, said first interconnecting member, said second
interconnecting member, and said third interconnecting member.
5. The family power transmissions defined in claim 4 further
comprising: said first members of said first, second, and third
planetary gearsets being a member selected from a first group
consisting of a sun gear member, a ring gear member, and a planet
carrier assembly member; said second members of said first, second,
and third planetary gearsets being a member of a first group
consisting of a sun gear member, a ring gear member, and a planet
carrier assembly member not selected as said first member; and said
third members of said first, second, and third planetary gearsets
being a member of a first group consisting of a sun gear member, a
ring gear member, and a planet carrier assembly member not selected
as either said first member or said second member
Description
TECHNICAL FIELD
[0001] This invention relates to power transmissions and, more
particularly, to power transmissions having three planetary
gearsets and six torque-transmitting mechanisms in order to provide
at least seven forward speed ratios and one reverse speed
ratio.
BACKGROUND OF THE INVENTION
[0002] Automatic shifting power transmissions are currently used in
a majority of the vehicles produced in the United States. These
vehicles generally employ three- and four-speed power
transmissions. More recently, a trend towards more ratios, such as
five- and six-speed power transmissions, has been proposed. In
fact, some manufacturers do provide five-speed transmissions. Many
of the vehicles utilizing manual type transmissions or countershaft
type transmissions employ five- and six-speed power
transmissions.
[0003] The five- and six-speed power transmissions provide improved
vehicle acceleration performance and fuel economy when compared
with three- and four-speed transmissions. Seven-speed transmissions
offer further vehicle acceleration performance and fuel economy
improvements over five- and six-speed power transmissions. However,
seven-speed power transmissions have not been proposed due to the
complexity of these assemblies, as well as size and cost. There are
many current patents that describe five- and six-speed power
transmissions. Some of the six-speed power transmission patents,
especially those assigned to the assignee of the present invention,
describe six-speed power transmissions in families, wherein one or
more family members incorporate a seven-speed power
transmission.
SUMMARY OF THE INVENTION
[0004] It is an object of the present invention to provide an
improved family of seven-speed power transmissions incorporating
three planetary gearsets and six torque-transmitting
mechanisms.
[0005] In one aspect of the present invention, the six
torque-transmitting mechanisms are engaged in combinations of two
to establish at least seven forward speed ratios and one reverse
speed ratio within the planetary gearsets.
[0006] In another aspect of the present invention, an
interconnecting member continuously interconnects a first member of
the first planetary gearset and a first member of the second
planetary gearset.
[0007] In still another aspect of the present invention, a second
interconnecting member continuously interconnects a second member
of the first planetary gearset with a first member of the third
planetary gearset.
[0008] In yet another aspect of the present invention, a third
interconnecting member continuously interconnects a second member
of the second planetary gearset with a second member of the third
planetary gearset.
[0009] In yet still another aspect of the present invention, a
third member of the first planetary gearset is continuously
interconnected with a stationary member, such as a transmission
case or housing.
[0010] In a yet still another aspect of the present invention, an
output shaft is continuously interconnected with at least one
member of one of the planetary gearsets.
[0011] In yet still another aspect of the present invention an
input shaft is not continuously connected with any of the planetary
gear sets but rather only selectively connectible therewith through
selectively engageable torque transmitting mechanisms.
[0012] In a further aspect of the present invention, a first of the
torque-transmitting mechanisms selectively interconnects an input
shaft with a member of one of the planetary gearsets.
[0013] In a still further aspect of the present invention, a second
of the torque-transmitting mechanisms selectively interconnects the
input shaft with a member of one of the planetary gearsets not
interconnected with the first torque-transmitting mechanism.
[0014] In yet a further aspect of the present invention, a third of
the torque-transmitting mechanisms selectively interconnects a
member of one of the planetary gearsets or one of the
interconnecting members with either the input shaft, the output
shaft, or another member of one of the planetary gearsets.
[0015] In a yet still further aspect of the present invention, a
fourth of the torque-transmitting mechanisms selectively
interconnects a member of one of the planetary gearsets with either
the input shaft, the output shaft, or another member of one of the
planetary gearsets.
[0016] In a still further aspect of the present invention, a fifth
of the torque-transmitting mechanisms selectively interconnects at
least one member of one of the planetary gearsets with another
member of the first, second, or third planetary gearset, or with
the transmission housing.
[0017] In a further aspect of the present invention, a sixth of the
torque-transmitting mechanisms selectively interconnects a member
of one of the planetary gearsets with either the output shaft,
another member of one of the planetary gearsets, or with the
transmission housing.
[0018] In a yet further aspect of the present invention, each of
the members of the planetary gearsets can be either a sun gear
member, a ring gear member, or a planet carrier assembly member,
and each of the planet carrier assembly members can be either of
the single pinion type or of the double pinion type.
DESCRIPTION OF THE DRAWINGS
[0019] FIG. 1 is a schematic representation of a powertrain having
one embodiment of the present invention incorporated therein.
[0020] FIG. 2 is a truth table and chart depicting some of the
operating parameters of the powertrain shown in FIG. 1.
[0021] FIG. 3 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0022] FIG. 4 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 3.
[0023] FIG. 5 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0024] FIG. 6 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 5.
[0025] FIG. 7 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0026] FIG. 8 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 7.
[0027] FIG. 9 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0028] FIG. 10 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 9.
[0029] FIG. 11 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0030] FIG. 12 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 11.
[0031] FIG. 13 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0032] FIG. 14 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 13.
[0033] FIG. 15 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0034] FIG. 16 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 15.
[0035] FIG. 17 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0036] FIG. 18 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 17.
[0037] FIG. 19 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0038] FIG. 20 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 19.
[0039] FIG. 21 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0040] FIG. 22 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 21.
[0041] FIG. 23 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0042] FIG. 24 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 23.
[0043] FIG. 25 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0044] FIG. 26 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 25.
[0045] FIG. 27 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0046] FIG. 28 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 27.
[0047] FIG. 29 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0048] FIG. 30 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 29.
[0049] FIG. 31 is a schematic representation of a powertrain having
another embodiment of the present invention incorporated
therein.
[0050] FIG. 32 is a truth table and chart depicting some of the
operating parameters of the embodiment shown in FIG. 31.
DESCRIPTION OF THE EXEMPLARY EMBODIMENTS
[0051] 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 or
prime mover 12, a conventional starting device 13, a planetary
transmission 14, and a conventional final drive mechanism 16. The
starting device 13 may be a mechanism, such as a torque converter,
a fluid coupling, or a starting clutch. The final drive mechanism
16 is a conventional differential type mechanism, which is
drivingly connected with the drive wheels of a vehicle, not
shown.
[0052] 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 starting device 13 or
with the engine 12. The output shaft 19 is continuously
interconnected with the final drive mechanism 16.
[0053] The planetary gear arrangement 18 includes a planetary
gearset 20 having 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 member 29 and disposed in meshing relationship
with the sun gear member 22 and the ring gear member 24.
[0054] The planetary gear arrangement 18 also includes a planetary
gearset 30 having a sun gear member 32, a ring gear member 34, and
a planet carrier assembly member 36. The planet carrier assembly
member 36 includes a plurality of pinion gears 37 rotatably mounted
on a planet carrier member 39 and disposed in meshing relationship
with the sun gear member 32 and the ring gear member 34.
[0055] The planetary gear arrangement 18 further includes a third
planetary gearset 40 having 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 member 49 and disposed in
meshing relationship with the sun gear member 42 and the ring gear
member 44.
[0056] Also included in the planetary gear arrangement 18 are six
torque-transmitting mechanisms 50, 52, 54, 56, 58, and 60. The
torque-transmitting mechanisms 50, 52, 54, and 56 are conventional
rotating type torque-transmitting mechanisms, commonly termed
clutches. These devices, as well known, are multiple type friction
devices having a fluid-operated apply piston. The
torque-transmitting mechanisms 58 and 60 are conventional
stationary type torque-transmitting mechanisms, commonly termed
brakes. Each of these stationary type torque-transmitting
mechanisms can be either a disc type brake a band type brake. Both
constructions are well known to those skilled in the art.
[0057] The ring gear member 24 and the planet carrier assembly
member 36 are continuously interconnected by an interconnecting
member 70. The planet carrier assembly member 26 and the ring gear
member 44 are continuously interconnected by an interconnecting
member 72. The ring gear member 34 and the planet carrier assembly
member 46 are continuously interconnected by an interconnecting
member 74. The planet carrier assembly member 26 is continuously
connected with the output shaft 19
[0058] The input shaft 17 is selectively connectible with the sun
gear member 42 through the torque-transmitting mechanism 50,
selectively connectible with the interconnecting member 74 through
the torque-transmitting mechanism 52, and selectively connectible
with the sun gear member 32 through the torque-transmitting
mechanism 54. The sun gear member 22 is continuously connected with
the transmission housing 62. The sun gear member 42 is selectively
interconnectible with the planet carrier assembly member 46 through
the torque-transmitting mechanism 56, and selectively connectible
with the transmission housing 62 through the torque-transmitting
mechanism 58. The planet carrier assembly member 46 and therefore
interconnecting member 74 are selectively connectible with the
transmission housing 62 through the torque-transmitting mechanism
60.
[0059] Each of these interconnecting descriptions refer to the
planet carrier assembly members being interconnected, however, as
is well known, the input and output member of the planet carrier
assembly member is the planet carrier member itself. For example,
with the planet carrier assembly member 26, any interconnections
are made through the planet carrier member 29.
[0060] The truth table shown in FIG. 2 describes the engagement
combinations and sequence for the torque-transmitting mechanisms in
order to establish seven forward speed ratios and one reverse speed
ratio in the planetary gear arrangement 18 between the input shaft
17 and the output shaft 19. As can be seen in the truth table, the
torque-transmitting mechanisms are engaged in combinations of two
for each of the speed ratios. Also, it should be recognized from
the truth table that all of the single step interchanges in the
forward direction are of the single transition variety as is the
reverse-to-first forward speed ratio interchange when the
torque-transmitting mechanism 60 remains engaged through a neutral
condition. Further information given in the truth table is a
numerical example for each of the forward speed ratios as well as
the reverse speed ratio. The numerical values are determined
utilizing the ring gear/sun gear tooth ratios of the planetary
gearsets 20, 30, and 40 when the ring gear/sun gear tooth ratios
are as defined in R1/S1, R2/S2, and R3/S3. The planetary gear
arrangement is not limited to the particular gear ratios shown, or
to the particular tooth ratio shown. Those skilled in the art will
recognize that in order to modify the overall ratio spread or the
step ratio between adjacent forward speed ratios, it is possible to
change the ring gear/sun gear tooth ratios. A chart in FIG. 2
provides the numerical value for the ratio steps between adjacent
forward speed ratios as well as between the reverse and first
forward speed ratio. Other information given in the chart is the
numerical value of the overall ratio spread of the forward speed
ratios.
[0061] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 50 and 60. During the reverse
speed ratio, the ring gear member 44 and therefore output shaft 19
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 numerical value of the reverse speed ratio is
determined by the ring gear/sun gear tooth ratio of the planetary
gearset 40.
[0062] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 54 and 60. During
the first forward speed ratio, the planet carrier assembly member
36 and ring gear member 24 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 planet carrier assembly
member 26 and therefore output shaft 19 are rotated at a speed
determined by the speed of the ring gear member 24 and the ring
gear/sun gear tooth ratio of the planetary gearset 20. 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.
[0063] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 54 and 58. During
the second forward speed ratio, the planet carrier assembly member
46 and ring gear member 34 are rotated at a speed determined by the
speed of the ring gear member 44 and the ring gear/sun gear tooth
ratio of the planetary gearset 40. The planet carrier assembly
member 36 and ring gear member 24 are rotated at a speed determined
by the speed of the sun gear member 32, the speed of the ring gear
member 34, and the ring gear/sun gear tooth ratio of the planetary
gearset 30. The planet carrier assembly member 26 and therefore
output shaft 19 are rotated at a speed determined by the speed of
the ring gear member 24 and the ring gear/sun gear tooth ratio of
the planetary gearset 20. The numerical value of the second forward
speed ratio is determined by the ring gear/sun gear tooth ratios of
all three planetary gearsets 20, 30, and 40.
[0064] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 54 and 56. During
the third forward speed ratio, the planetary gearset 40 and the
ring gear member 34 rotate in unison. The planet carrier assembly
member 36 and ring gear member 24 are rotated at a speed determined
by the speed of the sun gear member 32, the speed of the ring gear
member 34, and the ring gear/sun gear tooth ratio 30. The planet
carrier assembly member 26, ring gear member 44, and ring gear
member 34 are rotated at a speed determined by the speed of the
ring gear member 24 and the ring gear/sun gear tooth ratio of the
planetary gearset 20. The numerical value of the third forward
speed ratio is determined by the ring gear/sun gear tooth ratios of
the planetary gearsets 20 and 30.
[0065] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 50 and 54. During
the fourth forward speed ratio, the planet carrier assembly member
46 and ring gear member 34 are rotated at a speed determined by the
speed of the sun gear member 42, the speed of the ring gear member
44, and the ring gear/sun gear tooth ratio of the planetary gearset
40. The planet carrier assembly member 36 and ring gear member 24
are rotated at a speed determined by the speed of the sun gear
member 32, the speed of the ring gear member 34, and the ring
gear/sun gear tooth ratio of the planetary gearset 30. The
interconnecting member 72 and the output shaft 19 are rotated at a
speed determined by the speed of the ring gear member 24 and the
ring gear/sun gear tooth ratio of the planetary gearset 20. The
numerical value of the fourth forward speed ratio is determined by
the ring gear/sun gear tooth ratios of all three planetary gearsets
20, 30, and 40.
[0066] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 52 and 54. During
the fifth forward speed ratio, the planetary gearset 30 and ring
gear member 24 rotate in unison with the input shaft 17. The planet
carrier assembly member 26 and therefore output shaft 19 are
rotated at a speed determined by the speed of the ring gear member
24 and the ring gear/sun gear tooth ratio of the planetary gearset
20. The numerical value of the fifth forward speed ratio is
determined by the ring gear/sun gear tooth ratio of the planetary
gearset 20.
[0067] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 50 and 52. During
the sixth forward speed ratio, the planetary gearset 40, the planet
carrier assembly member 26 and therefore output shaft 19 rotate in
unison with the input shaft 17. The numerical value of the sixth
forward speed ratio is one.
[0068] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 52 and 58. During
the seventh forward speed ratio, the ring gear member 44, planet
carrier assembly member 26 and therefore output shaft 19 are
rotated at a speed determined by the speed of the planet carrier
assembly member 46 and the ring gear/sun gear tooth ratio of the
planetary gearset 40. The numerical value of the seventh forward
speed ratio is determined by the ring gear/sun gear tooth ratio of
the planetary gearset 40.
[0069] A powertrain 110, shown in FIG. 3, includes the engine 12,
the starting device 13, 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 six torque-transmitting
mechanisms 150, 152, 154, 156, 158, and 160. The
torque-transmitting mechanisms 158 and 160 are stationary type
torque-transmitting mechanisms, while the remaining
torque-transmitting mechanisms 150, 152, 154, and 156 are of the
rotating type.
[0070] 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 the sun gear member 122 and the ring gear
member 124.
[0071] 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 a planet carrier 139 and disposed in
meshing relationship with the sun gear member 132 and the ring gear
member 134.
[0072] 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 the sun gear member 142 and the ring gear
member 144.
[0073] The planet carrier assembly member 126 by way of its planet
carrier member 129 is continuously interconnected with the ring
gear member 134 through an interconnecting member 170. The ring
gear member 124 is continuously interconnected with the planet
carrier assembly member 146 through the planet carrier member 149
by an interconnecting member 172. The planet carrier assembly
member 136, the ring gear member 144, and the output shaft 19 are
all continuously interconnected by an interconnecting member 174.
The sun gear member 122 is continuously connected with the
transmission housing 62.
[0074] The input shaft 17 is selectively interconnectible with the
interconnecting member 172 through the torque-transmitting
mechanism 150, selectively interconnectible with the sun gear
member 132 through the torque-transmitting mechanism 152, and
selectively interconnectible with the sun gear member 142 through
the torque-transmitting mechanism 154. The planet carrier assembly
member 146 is selectively interconnectible with the interconnecting
member 174 through the torque-transmitting mechanism 156, and
selectively interconnectible with the transmission housing 62
through the torque-transmitting mechanism 158. The sun gear member
142 is selectively interconnectible with the transmission housing
62 through the torque-transmitting mechanism 160.
[0075] As seen in the truth table of FIG. 4, the planetary gear
arrangement 118 is capable of providing seven forward speed ratios
and one reverse speed ratio when the torque-transmitting mechanisms
are engaged in combinations of two in the sequence shown. Also
given in the truth table 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 are as given in FIG. 4 as R1/S1, R2/S2, and R3/S3. Further
information given in FIG. 4 is the numerical value for the ratio
steps between adjacent forward speed ratios as well as between the
reverse and first forward speed ratio. The chart in FIG. 4 also
provides the numerical value for the overall ratio spread of the
forward speed ratios.
[0076] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 154 and 158. During the
reverse speed ratio, the ring gear member 144 and therefore output
shaft 19 are rotated at a speed determined by the speed of the sun
gear member 142 and the ring gear/sun gear tooth ratio of the
planetary gearset 140. The numerical value of the reverse speed
ratio is determined by the ring gear/sun gear tooth ratio of the
planetary gearset 140.
[0077] 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 planet carrier assembly
member 136 and therefore output shaft 19 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
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
130.
[0078] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 152 and 160.
During the second forward speed ratio, the planet carrier assembly
member 146 and ring gear member 124 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 planet
carrier assembly member 126 and ring gear member 134 are rotated at
a speed determined by the speed of the ring gear member 124 and the
ring gear/sun gear tooth ratio of the planetary gearset 120. The
planet carrier assembly member 136 and therefore output shaft 19
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
numerical value of the second forward speed ratio is determined by
the ring gear/sun gear tooth ratios of all three planetary gearsets
120, 130, and 140.
[0079] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 152 and 156.
During the third forward speed ratio, the planet carrier assembly
member 126 and ring gear member 134 are rotated at a speed
determined by the speed of the ring gear member 124 and the ring
gear/sun gear tooth ratio of the planetary gearset 120. The planet
carrier assembly member 136 and therefore output shaft 19 are
rotated at a speed determined by the speed of the ring gear member
134, the speed of the sun gear member 132, and the ring gear/sun
gear tooth ratio of the planetary gearset 130. The numerical value
of the third forward speed ratio is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 130 and 120.
[0080] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 152 and 154.
During the fourth forward speed ratio, the planet carrier assembly
member 146 and ring gear member 124 are rotated at a speed
determined by the speed of the sun gear member 142, 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 member 126
and ring gear member 134 are rotated at a speed determined by the
speed of the ring gear member 124 and the ring gear/sun gear tooth
ratio of the planetary gearset 120. The planet carrier assembly
member 136 and therefore output shaft 19 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 numerical value of the fourth
forward speed ratio is determined by the ring gear/sun gear tooth
ratios of all three planetary gearsets 120, 130, and 140.
[0081] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 150 and 152.
During the fifth forward speed ratio, the planet carrier assembly
member 126 and ring gear member 134 are rotated at a speed
determined by the speed of the ring gear member 124 and the ring
gear/sun gear tooth ratio of the planetary gearset 120. The planet
carrier assembly member 136 and therefore output shaft 19 are
rotated at a speed determined by the speed of the ring gear member
134, the speed of the sun gear member 132, and the ring gear/sun
gear tooth ratio of the planetary gearset 130. The numerical value
of the fifth forward speed ratio is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 120 and 130.
[0082] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 150 and 154.
During the sixth forward speed ratio, the planetary gearset 140,
planet carrier assembly member 136, and output shaft 19, are
rotated in unison with the input shaft 17. The numerical value for
the sixth forward speed ratio is one.
[0083] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 150 and 160.
During the seventh forward speed ratio, the ring gear member 144,
planet carrier assembly member 136, and output shaft 19 are rotated
at a speed determined by the speed of the planet carrier assembly
member 146 and the ring gear/sun gear tooth ratio of the planetary
gearset 140. The numerical value of the seventh forward speed ratio
is determined by the ring gear/sun gear tooth ratio of the
planetary gearset 140.
[0084] A powertrain 210, shown in FIG. 5, includes the engine 12,
the starting device 13, 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, four rotating type
torque-transmitting mechanisms 250, 252, 254, and 256, and two
stationary type torque-transmitting mechanisms 258, and 260.
[0085] 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 the sun gear member 222 and the ring gear
member 224.
[0086] 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 a planet carrier 239 and disposed in
meshing relationship with the sun gear member 232 and the ring gear
member 234.
[0087] 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 the sun gear member 242 and the ring gear
member 244.
[0088] The planet carrier assembly member 226 through its planet
carrier member 229 is continuously interconnected with the ring
gear member 234 through an interconnecting member 270. The ring
gear member 224 is interconnected with the planet carrier assembly
member 246 through an interconnecting member 272. The ring gear
member 244, planet carrier assembly member 236, and the output
shaft 19 are continuously interconnected by an interconnecting
member 274. The sun gear member 222 is continuously connected with
the transmission housing 62.
[0089] The input shaft 17 is selectively interconnectible with the
interconnecting member 272 through the torque-transmitting
mechanism 250, selectively connectible with the sun gear member 232
through the torque-transmitting mechanism 252, and selectively
interconnectible with the sun gear member 242 through the
torque-transmitting mechanism 254. The sun gear member 242 is
selectively interconnectible with the interconnecting member 272
through the torque-transmitting mechanism 256. The interconnecting
member 270 is selectively connectible with the transmission housing
62 through the torque-transmitting mechanism 258. The sun gear
member 242 is selectively interconnectible with the transmission
housing 62 through the torque-transmitting mechanism 260.
[0090] The truth table of FIG. 6 describes the engagement
combinations and sequence for the torque-transmitting mechanisms in
order to establish seven forward speed ratio and one reverse speed
ratio in the planetary gear arrangement 218 between the input shaft
17 and the output shaft 19 in the planetary transmission 214. The
truth table also provides an example of the numerical values of the
speed ratios of the planetary gear arrangement 218. A chart in FIG.
6 provides the numerical examples for the ratio steps between
adjacent forward speed ratios as well as between the reverse and
first forward speed ratio when the speed ratios given in the truth
table are employed. Also given in the chart of FIG. 6 is the
overall ratio spread of the forward speed ratios. The numerical
values given in the truth table are determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 220, 230, and 240
displayed in FIG. 6 as R1/S1, R2/S2, and R3/S3, respectively.
[0091] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanism 254 and 258. During the
reverse speed ratio, the ring gear member 244 and therefore output
shaft are rotated at a speed determined by the speed of the sun
gear member 242 and the ring gear/sun gear tooth ratio of the
planetary gearset 240. The numerical value of the reverse speed
ratio is determined by the ring gear/sun gear tooth ratio of the
planetary gearset 240.
[0092] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 252 and 258.
During the first forward speed ratio, the planet carrier assembly
member 236 and therefore output shaft 19 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
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
230.
[0093] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 252 and 260.
During the second forward speed ratio, the planet carrier assembly
member 246 and ring gear member 224 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 226 and ring gear member 234 are rotated at
a speed determined by the speed of the ring gear member 224 and the
ring gear/sun gear tooth ratio of the planetary gearset 220. The
planet carrier assembly member 236 and therefore output shaft 19
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
numerical value of the second forward speed ratio is determined by
the ring gear/sun gear tooth ratios of all three planetary gearsets
220, 230, and 240.
[0094] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 252 and 256.
During the third forward speed ratio, the planet carrier assembly
member 226 and ring gear member 234 are rotated at a speed
determined by the speed of the ring gear member 224 and the ring
gear/sun gear tooth ratio of the planetary gearset 220. The planet
carrier assembly member 236 and therefore output shaft 19 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. It should be noted
that during the third forward speed ratio, the ring gear member
224, the planetary gearset 240, and the planet carrier assembly
member 236 are rotated in unison. The numerical value of the third
forward speed ratio is determined by the ring gear/sun gear tooth
ratios of the planetary gearsets 220 and 230.
[0095] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 252 and 254.
During the fourth forward speed ratio, the planet carrier assembly
member 246 and ring gear member 224 are rotated at a speed
determined by the speed of the sun gear member 242, 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 226
and ring gear member 234 are rotated at a speed determined by the
speed of the ring gear member 224 and the ring gear/sun gear tooth
ratio of the planetary gearset 220. The planet carrier assembly
member 236 and therefore output shaft 19 are rotated at a speed
determined by the speed of the ring gear member 234, the speed of
the sun gear member 232, and the ring gear/sun gear tooth ratio of
the planetary gearset 230. The numerical value of the fourth
forward speed ratio is determined by the ring gear/sun gear tooth
ratios of all three planetary gearsets 220, 230, and 240.
[0096] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 250 and 252.
During the fifth forward speed ratio, the planet carrier assembly
member 226 and ring gear member 234 are rotated at a speed
determined by the speed of the ring gear member 224 and the ring
gear/sun gear tooth ratio of the planetary gearset 220. The planet
carrier assembly member 236 and therefore output shaft 19 are
rotated at a speed determined by the speed of the ring gear member
234, the speed of the sun gear member 232, and the ring gear/sun
gear tooth ratio of the planetary gearset 230. 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 230.
[0097] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 250 and 254.
During the sixth forward speed ratio, the planetary gearset 240,
planet carrier assembly member 236, and the output shaft 19, are
rotated in unison with the input shaft 17. The numerical value of
the sixth forward speed ratio is one.
[0098] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 250 and 260.
During the seventh forward speed ratio, the ring gear member 244
and therefore output shaft 19 are rotated at a speed determined by
the speed of the planet carrier assembly member 246 and the ring
gear/sun gear tooth ratio of the planetary gearset 240. The
numerical value of the seventh forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
240.
[0099] A powertrain 310, shown in FIG. 7, includes the engine 12,
the starting device 13, 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, four rotating type
torque-transmitting mechanisms 350, 352, 354, and 356, and two
stationary type torque-transmitting mechanisms 358, and 360.
[0100] 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 the sun gear member 322 and the ring gear
member 324.
[0101] 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 a planet carrier 339 and disposed in
meshing relationship with the sun gear member 332 and the ring gear
member 334.
[0102] 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 the sun gear member 342 and the ring gear
member 344.
[0103] The planet carrier assembly member 326 is continuously
interconnected with the ring gear member 334 through an
interconnecting member 370. The ring gear member 324, planet
carrier assembly member 346, and the output shaft 19 are
continuously interconnected by an interconnecting member 372. The
planet carrier assembly member 336 and ring gear member 344 are
continuously interconnected by an interconnecting member 374. The
sun gear member 322 is continuously connected with the transmission
housing 62.
[0104] The input shaft 17 is selectively connectible with the sun
gear member 332 through the torque-transmitting mechanism 350,
selectively interconnectible with the interconnecting member 374
through the torque-transmitting mechanism 352, and selectively
interconnectible with the sun gear member 342 through the
torque-transmitting mechanism 354. The interconnecting member 370
is selectively interconnectible with the interconnecting member 374
through the torque-transmitting mechanism 356. The interconnecting
member 374 is selectively interconnectible with the transmission
housing 62 through the torque-transmitting mechanism 360. The sun
gear member 332 is selectively interconnectible with transmission
housing 62 through the torque-transmitting mechanism 358.
[0105] As seen in the truth table of FIG. 8, the
torque-transmitting mechanisms are selectively engaged in
combinations of two to provide seven forward speed ratios and one
reverse speed ratio in the planetary gear arrangement 318. Also
given in the truth table is a numerical example of the speed ratios
that are available with the planetary gear arrangement 318 when the
ring gear/sun gear tooth ratios of the planetary gearsets 320, 330,
and 340 are as defined as R1/S1, R2/S2, and R3/S3, respectively.
Further information given in FIG. 8 by way of a chart that provides
numerical values for the ratio steps between adjacent forward speed
ratios as well as between reverse and first forward speed ratio.
Also given in the chart of FIG. 8 is the numerical value of the
overall ratio spread of the forward speed ratios.
[0106] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 350 and 360. During the
reverse speed ratio, the ring gear member 334 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, planet
carrier assembly member 346, 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 reverse speed ratio is determined
by the ring gear/sun gear tooth ratios of the planetary gearsets
320 and 330.
[0107] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 354 and 360.
During the first forward speed ratio, the planet carrier assembly
member 346 and therefore output shaft 19 are rotated at a speed
determined by the speed of the sun gear member 342 and the ring
gear/sun gear tooth ratio of the planetary gearset 340. The
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
340.
[0108] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 354 and 358.
During the second forward speed ratio, the ring gear member 344 and
planet carrier assembly member 336 are rotated at a speed
determined by the speed of the sun gear member 342, 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 planet carrier assembly member 326 are rotated at a speed
determined by 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, planet carrier assembly member 346,
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 all three planetary gearsets 320,
330, and 340.
[0109] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 354 and 356.
During the third forward speed ratio the ring gear member 344, ring
gear member 334, and planet carrier assembly member 326 are rotated
at a speed determined by the speed of the sun gear member 342, 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, planet carrier assembly member 346, 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
third forward speed ratio is determined by the ring gear/sun gear
tooth ratios of the planetary gearsets 320 and 340.
[0110] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 350 and 354.
During the fourth forward speed ratio, the ring gear member 344 and
planet carrier assembly member 336 are rotated at a speed
determined by the speed of the sun gear member 342, 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 planet carrier assembly member 326 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,
planet carrier assembly member 346, 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 fourth forward speed ratio
is determined by the ring gear/sun gear tooth ratios of all three
planetary gearsets 320, 330, and 340.
[0111] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 352 and 354.
During the fifth forward speed ratio, the planetary gearset 340 and
therefore output shaft 19 rotate in unison with the input shaft 17.
The numerical value of the fifth forward speed ratio is one.
[0112] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 350 and 352.
During the sixth forward speed ratio, the planetary gearset 330 and
planet carrier assembly member 326 are rotated in unison with the
input shaft 17. The ring gear member 324, planet carrier assembly
member 346, and the 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 ratio of the planetary
gearset 320.
[0113] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 352 and 358.
During the seventh forward speed ratio, the ring gear member 334
and planet carrier assembly member 326 are rotated at a speed
determined by 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, planet carrier assembly member 346,
and the 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 seventh forward speed ratio is determined by
the ring gear/sun gear tooth ratios of the planetary gearsets 320
and 330.
[0114] A powertrain 410, shown in FIG. 9, includes the engine 12,
the starting device 13, 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, five rotating type
torque-transmitting mechanisms 450, 452, 454, 456, 458, and one
stationary type torque-transmitting mechanisms 460.
[0115] 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 the sun gear member 422 and the ring gear
member 424.
[0116] 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 a planet carrier 439 and disposed in
meshing relationship with the sun gear member 432 and the ring gear
member 434.
[0117] 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 the sun gear member 442 and the ring gear
member 444.
[0118] The planet carrier assembly member 426 is continuously
interconnected with the ring gear member 434 through an
interconnecting member 470. The ring gear member 424 is
continuously interconnected with the planet carrier assembly member
446 through an interconnecting member 472. The ring gear member
444, the planet carrier assembly member 436, and the output shaft
19 are continuously interconnected by an interconnecting member
474. The sun gear member 422 is continuously connected with the
transmission housing 62.
[0119] The input shaft 17 is selectively interconnectible with the
interconnecting member 470 through the torque-transmitting
mechanism 450, selectively connectible with the interconnecting
member 472 through the torque-transmitting mechanism 452,
selectively interconnectible with the sun gear member 432 through
the torque-transmitting mechanism 454, and selectively
interconnectible with the sun gear member 442 through the
torque-transmitting mechanism 456. The sun gear member 442 and
planet carrier assembly member 426 are selectively interconnectible
through the torque-transmitting mechanism 458. The interconnecting
member 470 is selectively interconnectible with the transmission
housing 62 through the torque-transmitting mechanism 460.
[0120] As seen in the truth table of FIG. 10, the
torque-transmitting mechanisms are selectively engaged in
combinations of two to establish seven forward speed ratios and one
reverse speed ratio in the planetary gear arrangement 418. Also,
the truth table provides a numerical example for the speed ratios
that are available with the planetary gear arrangement 418 when the
ring gear/sun gear tooth ratios of the planetary gearsets 420, 430,
and 440 are as shown in the truth table as R1/S1, R2/S2, and R3/S3,
respectively. Also described in FIG. 10 is a chart, which provides
the numerical example of the step ratios between adjacent forward
speed ratios as well as between the reverse and first forward speed
ratio. The chart of FIG. 10 also gives a numerical example of the
overall ratio spread for the forward speed ratios.
[0121] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 456 and 460. During the
reverse speed ratio, the ring gear member 444 and therefore output
shaft 19 are rotated at a speed determined by the speed of the sun
gear member 442 and the ring gear/sun gear tooth ratio of the
planetary gearset 440. The numerical value of the reverse speed
ratio is determined by the ring gear/sun gear tooth ratio of the
planetary gearset 440.
[0122] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 454 and 460.
During the first forward speed ratio, the planet carrier assembly
member 436 and therefore output shaft 19 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
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
430.
[0123] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 454 and 458.
During the second forward speed ratio, the ring gear member 434,
planet carrier assembly member 426, and sun gear member 442 are
rotated at a speed determined by the speed 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 planet carrier assembly member 446 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 ring gear member 444, planet carrier
assembly member 436, and output shaft 19 are rotated at a speed
determined by the speed of the sun gear member 442, the speed of
the planet carrier assembly member 446, and ring gear/sun gear
tooth ratio of the planetary gearset 440. The numerical value of
the second forward speed ratio is determined by the ring gear/sun
gear tooth ratios of all three planetary gearsets 420, 430, and
440.
[0124] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 454 and 456.
During the third forward speed ratio, the ring gear member 434 and
planet carrier assembly member 426 are rotated at a speed
determined by the speed 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 planet carrier assembly member 446 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 ring gear member 444, planet carrier assembly member 436,
and the output shaft 19 are rotated at a speed determined by the
speed of the planet carrier assembly member 446, the speed of the
sun gear member 442, and the ring gear/sun gear tooth ratio of the
planetary gearset 440. The numerical value of the third forward
speed ratio is determined by the ring gear/sun gear tooth ratios of
all three planetary gearsets 420, 430, and 440.
[0125] 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 planet carrier assembly
member 426 and ring gear member 434 are rotated at a speed
determined by the speed of the ring gear member 424 and the ring
gear/sun gear tooth ratio of the planetary gearset 420. The planet
carrier assembly member 436 and output shaft 19 are rotated at a
speed determined by the speed of the ring gear member 434, the
speed of the sun gear member 432, and the ring gear/sun gear tooth
ratio of the of planetary gearset 430. The numerical value of the
fourth forward speed ratio is determined by the ring gear/sun gear
tooth ratios of the planetary gearsets 420 and 430.
[0126] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 452 and 456.
During the fifth forward speed ratio, the planetary gearset 440 and
therefore the output shaft 19 are rotated at the same speed as the
input shaft 17. The numerical value of the fifth forward speed
ratio is one.
[0127] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 452 and 458.
During the sixth forward speed ratio, the planet carrier assembly
member 426 and sun gear member 442 are rotated at a speed
determined by the speed of the ring gear member 424 and the ring
gear/sun gear tooth ratio of the planetary gearset 420. The ring
gear member 444 and therefore output shaft 19 are rotated at a
speed determined by the speed of the planet carrier assembly member
446, the speed of the sun gear member 442, and the ring gear/sun
gear tooth ratio of the planetary gearset 440. 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.
[0128] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 450 and 458.
During the seventh forward speed ratio, the ring gear member 424
and planet carrier assembly member 446 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 ring gear member 444 and therefore output shaft 19 are
rotated at a speed determined by the speed of the sun gear member
442, the speed of the planet carrier assembly member 446, and the
ring gear/sun gear tooth ratio of the planetary gearset 440. The
numerical value of the seventh forward speed ratio is determined by
the ring gear/sun gear tooth ratios of the planetary gearsets 420
and 440.
[0129] A powertrain 510, shown in FIG. 11, includes the engine 12,
the starting device 13, 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, five rotating type
torque-transmitting mechanisms 550, 552, 554, 556, 558 and one
stationary type torque-transmitting mechanisms 560.
[0130] 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 the sun gear member 522 and the ring gear
member 524.
[0131] 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 a planet carrier 539 and disposed in
meshing relationship with the sun gear member 532 and the ring gear
member 534.
[0132] 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 the sun gear member 542 and the ring gear
member 544.
[0133] The ring gear member 524 and planet carrier assembly member
536 are continuously interconnected by an interconnecting member
570. The planet carrier assembly member 526 and ring gear member
544 are continuously interconnected by an interconnecting member
572. The sun gear member 532 and planet carrier assembly member 546
are continuously interconnected by an interconnecting member 574.
The output shaft 19 is continuously interconnected with the ring
gear member 534. The sun gear member 522 is continuously
interconnected with the transmission housing 62.
[0134] The input shaft 17 is selectively interconnectible with the
interconnecting member 570 through the torque-transmitting
mechanism 550, selectively interconnectible with the
interconnecting member 574 through the torque-transmitting
mechanism 552, and selectively interconnectible with the sun gear
member 542 through the torque-transmitting mechanism 554. The
interconnecting member 572 is selectively interconnectible with the
output shaft 19 through the torque-transmitting mechanism 556. The
interconnecting member 572 is selectively interconnectible with the
interconnecting member 574 through the torque-transmitting
mechanism 558. The interconnecting member 572 is selectively
connectible with the transmission housing 62 through the
torque-transmitting mechanism 560.
[0135] As seen in the truth table of FIG. 12, the
torque-transmitting mechanisms are engaged in combinations of two
to establish seven forward speed ratios and one reverse speed ratio
in the planetary gear arrangement 518. Also given in the truth
table is an example of the numerical values of the speed ratios
that are available with the planetary gear arrangement 518. These
numerical values are determined by the ring gear/sun gear tooth
ratios of the planetary gearsets 520, 530, and 540, which are given
by way of example in FIG. 12 as R1/S1, R2/S2, and R3/S3,
respectively. A chart in FIG. 12 gives the numerical example of the
ratio steps between adjacent forward speed ratios as well as
between the reverse and first forward speed ratio when the
numerical values for the speed ratios given the truth table are
employed. Also given in the chart of FIG. 12 is the numerical value
of the overall ratio spread for the forward speed ratios.
[0136] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 554 and 560. During the
reverse speed ratio, the planet carrier assembly member 546 and sun
gear member 532 are rotated at a speed determined by the speed of
the sun gear member 542 and the ring gear/sun gear tooth ratio of
the planetary gearset 540. The ring gear member 534 and therefore
output shaft 19 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 numerical value of the reverse speed
ratio is determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 530 and 540.
[0137] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 554 and 556.
During the first forward speed ratio, the planet carrier assembly
member 546 and sun gear member 532 are rotated at a speed
determined by the speed of the sun gear member 542, 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 ring gear member 524 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 planet carrier assembly member 526, ring gear
member 544, ring gear member 534, and the output shaft 19 are
rotated at a speed determined by the speed of the ring gear member
524 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 all three
planetary gearsets 520, 530, and 540.
[0138] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 552 and 556.
During the second forward speed ratio, the planet carrier assembly
member 536 and ring gear member 524 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 planet carrier assembly member 526,
ring gear member 544, ring gear member 534, and the output shaft 19
are rotated at a speed determined by the speed of the ring gear
member 524 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.
[0139] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 550 and 556.
During the third forward speed ratio, the planet carrier assembly
member 526, ring gear member 544, ring gear member 534, and
therefore output shaft 19 are rotated at a speed determined by the
speed of the ring gear member 524 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 ratio of the planetary gearset 520.
[0140] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 550 and 552.
During the fourth forward speed ratio, the planetary gearset 530
and therefore output shaft 19 are rotated in unison with the input
shaft 17. The numerical value of the fourth forward speed ratio is
one.
[0141] 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 526 and ring gear member 544 are rotated at a speed
determined by the speed of the ring gear member 524 and the ring
gear/sun gear tooth ratio of the planetary gearset 520. The planet
carrier assembly member 546 and sun gear member 532 are rotated at
a speed determined by the speed of the sun gear member 542, 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 534 and
therefore output shaft 19 are rotated at a speed determined by the
speed of the planet carrier assembly member 536, the speed of the
sun gear member 532, and the ring gear/sun gear tooth ratio of the
planetary gearset 530. The numerical value of the fifth forward
speed ratio is determined by the ring gear/sun gear tooth ratios of
all three planetary gearsets 520, 530, and 540.
[0142] The sixth forward speed ratio is established with the
engagement with of the torque-transmitting mechanisms 550 and 558.
During the sixth forward speed ratio, the planet carrier assembly
member 526 and sun gear member 532 are rotated at a speed
determined by the speed of the ring gear member 524 and the ring
gear/sun gear tooth ratio of the planetary gearset 520. The ring
gear member 534 and therefore output shaft 19 are rotated at a
speed determined by the speed of the planet carrier assembly member
536, the speed of the sun gear member 532, and the ring gear/sun
gear tooth ratio of the planetary gearset 530. The numerical value
of the sixth forward speed ratio is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 520 and 530.
[0143] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 552 and 558.
During the seventh forward speed ratio, the ring gear member 524
and planet carrier assembly member 536 are rotated 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 speed of the ring gear member 534 and therefore output
shaft 19 are determined by the speed of the sun gear member 532,
the speed of the planet carrier assembly member 536, and the ring
gear/sun gear tooth ratio of the planetary gearset 530. The
numerical value of the seventh forward speed ratio is determined by
the ring gear/sun gear tooth ratios of the planetary gearsets 520
and 530.
[0144] A powertrain 610, shown in FIG. 13, includes the engine 12,
the starting device 13, 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, five rotating type
torque-transmitting mechanisms 650, 652, 654, 656, 658 and one
stationary type torque-transmitting mechanisms 660.
[0145] 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 the sun gear member 622 and the ring gear
member 624.
[0146] 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 a planet carrier 639 and disposed in
meshing relationship with the sun gear member 632 and the ring gear
member 634.
[0147] 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 the sun gear member 642 and the ring gear
member 644.
[0148] The ring gear member 624 and planet carrier assembly member
636 are continuously interconnected by an interconnecting member
670. The planet carrier assembly member 626 and ring gear member
644 are continuously interconnected by an interconnecting member
672. The ring gear member 634 and sun gear member 642 are
continuously interconnected by an interconnecting member 674. The
sun gear member 622 is continuously connected with the transmission
housing 62. The output shaft 19 is continuously interconnected with
the planet carrier assembly member 646 and selectively
interconnectible with the interconnecting member 670 through the
torque-transmitting mechanism 656.
[0149] The input shaft 17 is selectively interconnectible with the
interconnecting member 670 through the torque-transmitting
mechanism 650, selectively interconnectible with the
interconnecting member 674 through the torque-transmitting
mechanism 652, and selectively interconnectible with the sun gear
member 632 through the torque-transmitting mechanism 654. The sun
gear member 632 is selectively interconnectible with the
interconnecting member 670 through the torque-transmitting
mechanism 658. The interconnecting member 672 is selectively
interconnectible with the transmission housing 62 through the
torque-transmitting mechanism 660.
[0150] The truth table of FIG. 14 describes the engagement
combinations and sequence for the torque-transmitting mechanisms in
order to establish seven forward speed ratios and one reverse speed
ratio in the planetary gear arrangement 618. An example of the
numerical values for these speed ratios is also given in the truth
table. The numerical example is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 620, 630, and 640,
which are shown in FIG. 14 as R1/S1, R2/S2, and R3/S3,
respectively. Also given in FIG. 14 is a chart, which provides the
numerical values for the step ratios between the adjacent forward
speed ratios as well as between the reverse and first forward speed
ratio. The numerical value of the overall ratio spread for forward
speed ratios is also given in the chart.
[0151] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 654 and 660. During the
reverse speed ratio, the ring gear member 634 and sun gear member
642 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 planet carrier assembly member 646 and therefore
output shaft 19 are rotated at a speed determined by the speed of
the sun gear member 642 and the ring gear/sun gear tooth ratio of
the planetary gearset 640. The numerical value of the reverse speed
ratio is determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 630 and 640.
[0152] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 652 and 660.
During the first forward speed ratio, the planet carrier assembly
member 646 and therefore output shaft 19 are rotated at a speed
determined by the speed of the sun gear member 642 and the ring
gear/sun gear tooth ratio of the planetary gearset 640. The
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
640.
[0153] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 652 and 656.
During the second 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 sun gear member 642, 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,
planet carrier assembly member 646, 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 640.
[0154] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 652 and 658.
During the third forward speed ratio, the planet carrier assembly
member 626 and ring gear member 644 are rotated at a speed
determined by the speed of the ring gear member 624 and the ring
gear/sun gear tooth ratio of the planetary gearset 620. The planet
carrier assembly member 646 and therefore output shaft 19 are
rotated at a speed determined by the speed of the sun gear member
642, the speed of the ring gear member 644, and the ring gear/sun
gear tooth ratio of the planetary gearset 640. It should be noted
that the ring gear member 624 rotates at the speed of the input
shaft 17 during the third forward speed ratio. The numerical value
of the third forward speed ratio is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 620 and 640.
[0155] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanism 650 and 652. During
the fourth forward speed ratio, the planetary gearset 640 and
therefore output shaft 19 are rotated in unison with the input
shaft 17. The numerical value of the fourth forward speed ratio is
one.
[0156] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 650 and 658.
During the fifth forward speed ratio, the ring gear member 624 and
sun gear member 642 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 planet carrier
assembly member 646 and therefore output shaft 19 are rotated at a
speed determined by the speed of the ring gear member 644, the
speed of the sun gear member 642, and the ring gear/sun gear tooth
ratio of the planetary gearset 640. 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.
[0157] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 650 and 654.
During the sixth forward speed ratio, the ring gear member 624 and
planet carrier assembly member 636 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 ring gear member 634 and sun gear member 642 are rotated
at a speed determined by the speed of the planet carrier assembly
member 636, the speed of the sun gear member 632, and the ring
gear/sun gear tooth ratio of the planetary gearset 630. The planet
carrier assembly member 646 and therefore output shaft 19 are
rotated at a speed determined by the speed of the ring gear member
644, the speed of the sun gear member 642, and the ring gear/sun
gear tooth ratio of the planetary gearset 640. The numerical value
of the sixth forward speed ratio is determined by the ring gear/sun
gear tooth ratios of all three planetary gearsets 620, 630, and
640.
[0158] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 650 and 656.
During the seventh forward speed ratio, the ring gear member 624,
planet carrier assembly member 636, planet carrier assembly member
646, 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 seventh forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
620.
[0159] A powertrain 710, shown in FIG. 15, includes the engine 12,
the starting device 13, 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 six rotating type
torque-transmitting mechanisms 750, 752, 754, 756, 758, and
760.
[0160] 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 the sun gear member 722 and the ring gear
member 724.
[0161] 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 a planet carrier 739 and disposed in
meshing relationship with the sun gear member 732 and the ring gear
member 734.
[0162] 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 pinion
gears 747 rotatably mounted on a planet carrier 749 and disposed in
meshing relationship with the sun gear member 742 and the ring gear
member 744.
[0163] The ring gear member 724 and planet carrier assembly member
736 are continuously interconnected by an interconnecting member
770. The planet carrier assembly member 726 and ring gear member
744 are continuously interconnected by an interconnecting member
772. The ring gear member 734 and sun gear member 742 are
continuously interconnected by an interconnecting member 774. The
sun gear member 722 is continuously interconnected with the
transmission housing 62. The output shaft 19 is continuously
interconnected with the planet carrier assembly member 746 and
selectively interconnectible with the interconnecting member 770
through the torque-transmitting mechanism 758.
[0164] The input shaft 17 is selectively interconnectible with the
interconnecting member 772 through the torque-transmitting
mechanism 750, selectively interconnectible with the
interconnecting member 774 through the torque-transmitting
mechanism 752, and selectively interconnectible with the sun gear
member 732 through the torque-transmitting mechanism member 754.
The interconnecting member 772 is selectively interconnectible with
the interconnecting member 770 through the torque-transmitting
mechanism 756. The sun gear member 732 is selectively
interconnectible with the interconnecting member 774 through the
torque-transmitting mechanism 760.
[0165] The truth table of FIG. 16 describes the engagement
combinations and sequence for the torque-transmitting mechanisms to
establish seven forward speed ratios and one reverse speed ratio
within the planetary gear arrangement 718. Also given in the truth
table are numerical examples that are available with the planetary
gear arrangement 718 when the ring gear/sun gear tooth ratios of
the planetary gearsets 720, 730, and 740 are as shown in FIG. 16 as
R1/S1, R2/S2, and R3/S3, respectively. Also given in FIG. 16 is a
chart which gives a numerical example of the ratio steps between
adjacent forward speed ratios as well as between the reverse and
first forward speed ratio, as well as the overall ratio spread of
the forward speed ratios.
[0166] The reverse speed ratio is established with the engagement
of the torque-transmitting mechanisms 754 and 756. During the
reverse speed ratio, the ring gear member 734 and sun gear member
742 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 planet carrier assembly member 746 and therefore
output shaft 19 are rotated at a speed determined by the speed of
the sun gear member 742 and the ring gear/sun gear tooth ratio of
the planetary gearset 740. The numerical value of the reverse speed
ratio is determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 730 and 740.
[0167] The first forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 752 and 756.
During the first forward speed ratio, the planet carrier assembly
member 746 and therefore output shaft 19 are rotated at a speed
determined by the speed of the sun gear member 742 and the ring
gear/sun gear tooth ratio of the planetary gearset 740. The
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
740.
[0168] The second forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 752 and 758.
During the second forward speed ratio, the ring gear member 744 and
planet carrier assembly member 726 are rotated at a speed
determined by the speed of the sun gear member 742, 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,
planet carrier assembly member 736, planet carrier assembly member
746 and therefore 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 720
and 740.
[0169] The third forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 752 and 760.
During the third forward speed ratio, the planet carrier assembly
member 726 and ring gear member 744 are rotated at a speed
determined by the speed of the ring gear member 724 and the ring
gear/sun gear tooth ratio of the planetary gearset 720. The planet
carrier assembly member 746 and therefore output shaft 19 are
rotated at a speed determined by the speed of the sun gear member
742, the speed of the ring gear member 744, and the ring gear/sun
gear tooth ratio of the planetary gearset 740. The numerical value
of the third forward speed ratio is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 720 and 740.
[0170] The fourth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 750 and 752.
During the fourth forward speed ratio, the planetary gearset 740
and therefore output shaft 19 rotate in unison with the input shaft
17. The numerical value of the fourth forward speed ratio is
one.
[0171] The fifth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 750 and 760.
During the fifth forward speed ratio, the ring gear member 724 and
sun gear member 742 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 planet carrier
assembly member 746 and therefore output shaft 19 are rotated at a
speed determined by the speed of the sun gear member 742, the speed
of the ring gear member 744, and the ring gear/sun gear tooth ratio
of the planetary gearset 740. 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.
[0172] The sixth forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 750 and 754.
During the sixth forward speed ratio, the ring gear member 724 and
planet carrier assembly member 736 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 ring gear member 734 and sun gear member 742 are rotated
at a speed determined by the speed of the planet carrier assembly
member 736, the speed of the sun gear member 732, and the ring
gear/sun gear tooth ratio of the planetary gearset 730. The planet
carrier assembly member 746 and therefore output shaft 19 are
rotated at a speed determined by the speed of the sun gear member
742, the speed of the ring gear member 744, and the ring gear/sun
gear tooth ratio of the planetary gearset 740. The numerical value
of the sixth forward speed ratio is determined by the ring gear/sun
gear tooth ratios of all three planetary gearsets 720, 730, and
740.
[0173] The seventh forward speed ratio is established with the
engagement of the torque-transmitting mechanisms 750 and 758.
During the seventh forward speed ratio, the ring gear member 724,
planet carrier assembly member 736, planet carrier assembly member
746, 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 seventh forward speed ratio is determined by
the ring gear/sun gear tooth ratio of the planetary gearset
720.
[0174] A powertrain 810, shown in FIG. 17, includes the engine 12,
the starting device 13, 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, four rotating type
torque-transmitting mechanisms 850, 852, 854, 856, and two
stationary type torque-transmitting mechanisms 858 and 860.
[0175] 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 the sun gear member 822 and the ring gear
member 824.
[0176] 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 pinion
gears 837 rotatably mounted on a planet carrier 839 and disposed in
meshing relationship with the sun gear member 832 and the ring gear
member 834.
[0177] 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 the sun gear member 842 and the ring gear
member 844.
[0178] The ring gear member 824 and the sun gear member 832 are
continuously interconnected by a interconnecting member 870. The
planet carrier assembly member 826 and the ring gear member 844 are
continuously interconnected by an interconnecting member 872. The
planet carrier member 836 is continuously interconnected with the
planet carrier assembly member 846 by an interconnecting member
874. The output shaft 19 is continuously interconnected with the
sun gear member 842. The sun gear member 822 is continuously
interconnected with the transmission housing 62.
[0179] The input shaft 17 is selectively interconnectible with the
interconnecting member 870 through the torque-transmitting
mechanism 850, selectively interconnectible with the
interconnecting member 872 through the torque-transmitting
mechanism 852, and selectively interconnectible with the ring gear
member 834 through the torque-transmitting mechanism 854. The ring
gear member 834 is selectively interconnectible with the output
shaft 19 through the torque-transmitting mechanism 856. The
interconnecting member 872 is selectively interconnected with the
transmission housing 62 through the torque-transmitting mechanism
858. The interconnecting member 874 is selectively interconnectible
with the transmission housing 62 through the torque-transmitting
mechanism 860.
[0180] The truth table of FIG. 18 describes the combinations and
sequence of engagements for the torque-transmitting mechanisms in
order to establish seven forward speed ratios and one reverse speed
ratio between the input shaft 17 and the output shaft 19 through
the planetary gearset 818. The truth table also provides a
numerical example for the speed ratios that are available within
the planetary gear arrangement 818 when the ring gear/sun gear
tooth ratios of the planetary gearsets 820, 830, and 840 are as
shown in FIG. 18 as R1/S1, R2/S2, and R3/S3, respectively. The
chart in FIG. 18 provides a numerical example of the ratio steps
between the reverse and first forward speed ratio, the adjacent
seven forward speed ratios, and the overall ratio spread of the
forward speed ratios.
[0181] Upon reviewing the truth table in planetary gear arrangement
818, those skilled in the art will recognize that the numerical
values of the reverse speed ratio and the fifth forward speed ratio
are determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 820 and 840. The numerical values of the first
forward speed ratio, the second forward speed ratio, the fourth
forward speed ratio, and the seventh forward speed ratio are
determined by the ring gear/sun gear tooth ratios of all three
planetary gearsets 820, 830, and 840. The numerical value of the
third forward speed ratio is one. The numerical value of the sixth
forward speed ratio is determined by the ring gear/sun gear tooth
ratios of the planetary gearsets 830 and 840.
[0182] A powertrain 910, shown in FIG. 19, includes the engine 12,
the starting device 13, 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, four rotating type
torque-transmitting mechanisms 950, 952, 954, 956, and two
stationary type torque-transmitting mechanisms 958 and 960.
[0183] 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 pinion
gears 927 rotatably mounted on a planet carrier 929 and disposed in
meshing relationship with the sun gear member 922 and the ring gear
member 924.
[0184] 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 a planet carrier 939 and disposed in
meshing relationship with the sun gear member 932 and the ring gear
member 934.
[0185] 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 the sun gear member 942 and the ring gear
member 944.
[0186] The planet carrier assembly member 926 is continuously
interconnected with the planet carrier assembly member 936 through
an interconnecting member 970. The sun gear member 922 and planet
carrier assembly member 946 are continuously interconnected by an
interconnecting member 972. The ring gear members 934 and 944 are
continuously interconnected by an interconnecting member 974. The
output shaft 19 is continuously interconnected with the ring gear
member 924. The sun gear member 942 is continuously connected with
the transmission housing 62.
[0187] The input shaft 17 is selectively interconnectible with the
interconnecting member 972 through the torque-transmitting
mechanism 950 and selectively interconnectible with the sun gear
member 932 through the torque-transmitting mechanism 952. The sun
gear member 932 is selectively interconnectible with the output
shaft 19 through the torque-transmitting mechanism 954. The sun
gear member 932 is selectively interconnectible with the
interconnecting member 970 through the torque-transmitting
mechanism 956. The interconnecting member 970 is selectively
interconnectible with the transmission housing 62 through the
torque-transmitting mechanism 960. The interconnecting member 972
is selectively interconnectible with the transmission housing 62
through the torque-transmitting mechanism 958.
[0188] The truth table of FIG. 20 describes the engagement
combinations as well as the engagement sequence for the
torque-transmitting mechanisms in order to establish seven forward
speed ratios and one reverse speed ratio in the planetary gear
arrangement 918. The truth table also provides a numerical example
of the speed ratios that are available with the planetary gear
arrangement 918 when the ring gear/sun gear tooth ratios of the
planetary gearsets 920, 930, and 940 are as shown in FIG. 20 as
R1/S1, R2/S2, and R3/S3, respectively. The chart in FIG. 20
provides numerical examples for the ratio steps between adjacent
forward speed ratios, between the reverse and first forward speed
ratios, and the overall ratio spread of the forward speed
ratios.
[0189] Upon reviewing the truth table engagement combinations in
the planetary gear arrangement 918, those skilled in the art will
recognize that the numerical value of the reverse speed ratio is
determined by the ring gear/sun gear tooth ratio of the planetary
gearset 920. The numerical values of the first forward speed ratio,
the fifth forward speed ratio, and the seventh forward speed ratio
are determined by the ring gear/sun gear tooth ratios of all three
planetary gearsets 920, 930, and 940. 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. The numerical
value of the third forward speed ratio is one. The numerical value
of the fourth forward speed ratio and the sixth forward speed ratio
are determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 920 and 940.
[0190] A powertrain 1010, shown in FIG. 21, includes the engine 12,
the starting device 13, a planetary transmission 1014, and the
final drive mechanism 16. The planetary transmission 1014 includes
the input shaft 17, a planetary gear arrangement 1018, and the
output shaft 19. The planetary gear arrangement 1018 includes three
planetary gearsets 1020, 1030, and 1040, five rotating type
torque-transmitting mechanisms 1050, 1052, 1054, 1056, 1058, and
one stationary type torque-transmitting mechanism 1060.
[0191] The planetary gearset 1020 includes a sun gear member 1022,
a ring gear member 1024, and a planet carrier assembly member 1026.
The planet carrier assembly member 1026 includes a plurality of
pinion gears 1027 rotatably mounted on a planet carrier 1029 and
disposed in meshing relationship with the sun gear member 1022 and
the ring gear member 1024.
[0192] The planetary gearset 1030 includes a sun gear member 1032,
a ring gear member 1034, and a planet carrier assembly member 1036.
The planet carrier assembly member 1036 includes a plurality of
pinion gears 1037 rotatably mounted on a planet carrier 1039 and
disposed in meshing relationship with the sun gear member 1032 and
the ring gear member 1034.
[0193] The planetary gearset 1040 includes a sun gear member 1042,
a ring gear member 1044, and a planet carrier assembly member 1046.
The planet carrier assembly member 1046 includes a plurality of
pinion gears 1047 rotatably mounted on a planet carrier 1049 and
disposed in meshing relationship with the sun gear member 1042 and
the ring gear member 1044.
[0194] The ring gear member 1024 and planet carrier assembly member
1036 are continuously interconnected by an interconnecting member
1070. The planet carrier assembly member 1026 and ring gear member
1044 are continuously interconnected by an interconnecting member
1072. The ring gear member 1034 and planet carrier assembly member
1046 are continuously interconnected by an interconnecting member
1074. The sun gear member 1022 is continuously connected with the
transmission housing 62. The sun gear member 1042 is continuously
connected with the output shaft 19.
[0195] The input shaft 17 is selectively interconnectible with the
interconnecting member 1070 through the torque-transmitting
mechanism 1050, selectively interconnectible with the sun gear
member 1032 through the torque-transmitting mechanism 1052, and
selectively interconnectible with the interconnecting member 1074
through the torque-transmitting mechanism 1054. The sun gear member
1032 is selectively interconnectible with the interconnecting
member 1072 through the torque-transmitting mechanism 1056. The
interconnecting member 1074 is selectively interconnectible with
the sun gear member 1042 and output shaft 19 through the
torque-transmitting mechanism 1058, and selectively
interconnectible with the transmission housing 62 through the
torque-transmitting mechanism 1060.
[0196] The truth table of FIG. 22 describes the engagement
combinations and sequence for the torque-transmitting mechanisms in
order to establish seven forward speed ratios and one reverse speed
ratio within the planetary gear arrangement 1018. Also provided in
the truth table is an example of numerical values for these speed
ratios. These numerical values are determined utilizing the ring
gear/sun gear tooth ratios of the planetary gearsets 1020, 1030,
and 1040, which are given by way of example as R1/S1, R2/S2, and
R3/S3. Also given in FIG. 22 is a chart, which provides numerical
values for the ratio steps between the reverse and first forward
speed ratio, the adjacent forward speed ratios, and the overall
ratio spread of the forward speed ratios.
[0197] Those skilled in the art, upon reviewing the engagement
combinations in the planetary gear arrangement 1018, will be aware
that the numerical value of the reverse speed ratio, the fifth
forward speed ratio, the sixth forward speed ratio, and the seventh
forward speed ratio are determined by the ring gear/sun gear tooth
ratios of all three planetary gearsets 1020, 1030, and 1040. The
numerical value of the first forward speed ratio is determined by
the ring gear/sun gear tooth ratios of the planetary gearsets 1020
and 1030. The numerical value of the second forward speed ratio is
determined by the ring gear/sun gear tooth ratio of the planetary
gearset 1020. The third forward speed ratio has a numerical value
of one. The numerical value of the fourth forward speed ratio is
determined by the ring gear/sun gear tooth ratios of the planetary
gearsets 1020 and 1040.
[0198] A powertrain 1110, shown in FIG. 23, includes the engine 12,
the starting device 13, a planetary transmission 1114, and the
final drive mechanism 16. The planetary transmission 1114 includes
the input shaft 17, a planetary gear arrangement 1118, and the
output shaft 19. The planetary gear arrangement 1118 includes three
planetary gearsets 1120, 1130, and 1140, six rotating type
torque-transmitting mechanisms 1150, 1152, 1154, 1156, 1158, and
1160.
[0199] The planetary gearset 1120 includes a sun gear member 1122,
a ring gear member 1124, and a planet carrier assembly member 1126.
The planet carrier assembly member 1126 includes a plurality of
pinion gears 1127 rotatably mounted on a planet carrier 1129 and
disposed in meshing relationship with the sun gear member 1122 and
the ring gear member 1124.
[0200] The planetary gearset 1130 includes a sun gear member 1132,
a ring gear member 1134, and a planet carrier assembly member 1136.
The planet carrier assembly member 1136 includes a plurality of
pinion gears 1137 rotatably mounted on a planet carrier 1139 and
disposed in meshing relationship with the sun gear member 1132 and
the ring gear member 1134.
[0201] The planetary gearset 1140 includes a sun gear member 1142,
a ring gear member 1144, and a planet carrier assembly member 1146.
The planet carrier assembly member 1146 includes a plurality of
pinion gears 1147 rotatably mounted on a planet carrier 1149 and
disposed in meshing relationship with the sun gear member 1142 and
the ring gear member 1144.
[0202] The planet carrier assembly member 1126 is continuously
interconnected with the sun gear member 1132 through an
interconnecting member 1170. The sun gear member 1122 is
continuously interconnected with the ring gear member 1144 through
an interconnecting member 1172. The ring gear member 1134 is
continuously interconnected with the planet carrier assembly member
1146 through an interconnecting member 1174. The ring gear member
1124 is continuously interconnected with the transmission housing
62. The output shaft 19 is continuously interconnected with the
planet carrier assembly member 1136.
[0203] The input shaft 17 is selectively interconnectible with the
interconnecting member 1170 through the torque-transmitting
mechanism 150 and selectively interconnectible with the sun gear
member 1142 through the torque-transmitting mechanism 1152. The
interconnecting member 1170 is selectively interconnectible with
the planet carrier assembly member 1136 through the
torque-transmitting mechanism 1154. The interconnecting member 1172
is selectively interconnectible with the planet carrier assembly
member 1136 through the torque-transmitting mechanism 1156 and
selectively interconnectible with the interconnecting member 1174
through the torque-transmitting mechanism 1158. The sun gear member
1142 is selectively interconnectible with the planet carrier
assembly member 1136 and output shaft 19 through the
torque-transmitting mechanism 1160.
[0204] The truth table shown in FIG. 24 describes the combination
of engagements as well as the engagement sequence for the
torque-transmitting mechanisms in order to establish seven forward
speed ratios and one reverse speed ratio in the planetary gear
arrangement 1118. A numerical example for the speed ratios is also
given in the truth table. These numerical examples are established
using the ring gear/sun gear tooth ratios of the planetary gearsets
1120, 1130, and 1140, shown as R1/S1, R2/S2, and R3/S3,
respectively. Also given in FIG. 24 is a chart, which describes the
numerical values of the ratio steps between adjacent forward speed
ratios, the reverse-to-first forward speed ratio, and the overall
ratio spread of the forward speed ratios.
[0205] Those skilled in the art, upon reviewing the truth table and
planetary gear arrangement 1118, will recognize that the numerical
value of the reverse speed ratio is determined by the ring gear/sun
gear tooth ratios of the planetary gearsets 1120 and 1140. The
numerical value of the first forward speed ratio, the fourth
forward speed ratio, and the fifth forward speed ratio, are
determined by the ring gear/sun gear tooth ratios of all three
planetary gearsets 1120, 1130, and 1140. The numerical value of the
second forward speed ratio and the sixth forward speed ratio are
determined by the ring gear/sun gear tooth ratios of the planetary
gearsets 1120 and 1130. The numerical value of the third forward
speed ratio is one. The numerical value of the seventh forward
speed ratio is determined by the ring gear/sun gear tooth ratio of
the planetary gearset 1120.
[0206] A powertrain 1210, shown in FIG. 25, includes the engine 12,
the starting device 13, a planetary transmission 1214, and the
final drive mechanism 16. The planetary transmission 1214 includes
the input shaft 17, a planetary gear arrangement 1218, and the
output shaft 19. The planetary gear arrangement 1218 includes three
planetary gearsets 1220, 1230, and 1240, four rotating type
torque-transmitting mechanisms 1250, 1252, 1254, and 1256, and two
stationary type torque-transmitting mechanisms 1258 and 1260.
[0207] The planetary gearset 1220 includes a sun gear member 1222,
a ring gear member 1224, and a planet carrier assembly member 1226.
The planet carrier assembly member 1226 includes a plurality of
pinion gears 1227 rotatably mounted on a planet carrier 1229 and
disposed in meshing relationship with the sun gear member 1222 and
the ring gear member 1224.
[0208] The planetary gearset 1230 includes a sun gear member 1232,
a ring gear member 1234, and a planet carrier assembly member 1236.
The planet carrier assembly member 1236 includes a plurality of
pinion gears 1237 rotatably mounted on a planet carrier 1239 and
disposed in meshing relationship with the sun gear member 1232 and
the ring gear member 1234.
[0209] The planetary gearset 1240 includes a sun gear member 1242,
a ring gear member 1244, and a planet carrier assembly member 1246.
The planet carrier assembly member 1246 includes a plurality of
pinion gears 1247 rotatably mounted on a planet carrier 1249 and
disposed in meshing relationship with the sun gear member 1242 and
the ring gear member 1244.
[0210] The ring gear member 1224 is continuously interconnected
with the sun gear member 1232 through an interconnecting member
1270. The sun gear member 1222 is continuously interconnected with
the sun gear member 1242 through an interconnecting member 1272.
The planet carrier assembly member 1236 is continuously
interconnected with the ring gear member 1244 through an
interconnecting member 1274. The ring gear member 1234 is
continuously interconnected with the transmission housing 62. The
output shaft 19 is continuously interconnected with the planet
carrier assembly member 1246.
[0211] The input shaft 17 is selectively interconnectible with the
planet carrier assembly member 1226 through the torque-transmitting
mechanism 1250 and selectively interconnectible with the
interconnecting member 1272 through the torque-transmitting
mechanism 1252. The interconnecting member 1270 is selectively
interconnectible with the planet carrier assembly member 1246 and
output shaft 19 through the torque-transmitting mechanism 1254. The
planet carrier assembly member 1226 is selectively interconnectible
with the interconnecting member 1274 through the
torque-transmitting mechanism 1256 and selectively interconnectible
with the transmission housing 62 through the torque-transmitting
mechanism 1260. The interconnecting member 1274 is selectively
interconnectible with the transmission housing 62 through the
torque-transmitting mechanism 1258.
[0212] The truth table shown in FIG. 26 describes the engagement
combinations and sequence for the torque-transmitting mechanisms in
order to establish seven forward speed ratios and one reverse speed
ratio in the planetary gear arrangement 1218. The truth table also
provides a numerical example of the speed ratios that can be
obtained in the planetary gear arrangement 1218 when the ring
gear/sun gear tooth ratios of the planetary gearsets 1220, 1230,
and 1240 are chosen as represented by R1/S1, R2/S2, and R3/S3,
respectively. A chart in FIG. 26 provides the numerical value for
the ratio steps between adjacent forward speed ratios, between the
reverse and first forward speed ratio, and the overall ratio spread
of the forward speed ratios.
[0213] Upon reviewing the truth table and planetary gear
arrangement 1218, those skilled in the art will recognize that the
numerical value of the reverse speed ratio, the first forward speed
ratio, the second forward speed ratio, and the sixth forward speed
ratio are determined by the ring gear/sun gear tooth ratios of all
three planetary gearsets 1220, 1230, and 1240. The numerical value
of the third forward speed ratio is determined by the ring gear/sun
gear tooth ratio of the planetary gearset 1240. The numerical value
of the fourth forward speed ratio and the fifth forward speed ratio
are determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 1230 and 1240. The numerical value of the
seventh forward speed ratio is determined by the ring gear/sun gear
tooth ratios of the planetary gearset 1220 and 1240.
[0214] As is evident from the numerical values given, the planetary
gear arrangement 1218 does not provide a direct or 1:1 ratio in any
of the forward speeds. Also, it is noted that the planetary gear
arrangement 1218 provides six underdrive ratios and one overdrive
ratio.
[0215] A powertrain 1310, shown in FIG. 27, includes the engine 12,
the starting device 13, a planetary transmission 1314, and the
final drive mechanism 16. The planetary transmission 1314 includes
the input shaft 17, a planetary gear arrangement 1318, and the
output shaft 19. The planetary gear arrangement 1318 includes three
planetary gearsets 1320, 1330, and 1340, five rotating type
torque-transmitting mechanisms 1350, 1352, 1354, 1356 and 1358, and
one stationary type torque-transmitting mechanism 1360.
[0216] The planetary gearset 1320 includes a sun gear member 1322,
a ring gear member 1324, and a planet carrier assembly member 1326.
The planet carrier assembly member 1326 includes a plurality of
pinion gears 1327 rotatably mounted on a planet carrier 1329 and
disposed in meshing relationship with the sun gear member 1322 and
the ring gear member 1324.
[0217] The planetary gearset 1330 includes a sun gear member 1332,
a ring gear member 1334, and a planet carrier assembly member 1336.
The planet carrier assembly member 1336 includes a plurality of
pairs of intermeshing pinion gears 1337 and 1338 that are rotatably
mounted on a planet carrier 1339 and disposed in meshing
relationship with the sun gear member 1332 and the ring gear member
1334.
[0218] The planetary gearset 1340 includes a sun gear member 1342,
a ring gear member 1344, and a planet carrier assembly member 1346.
The planet carrier assembly member 1346 includes a plurality of
pinion gears 1347 rotatably mounted on a planet carrier 1349 and
disposed in meshing relationship with the sun gear member 1342 and
the ring gear member 1344.
[0219] It will be noted that the planetary gearset 1330 is a
compound or double pinion type planetary gearset. A double pinion
planetary gearset has a feature that when the carrier member of the
planet carrier assembly member is held stationary, the sun gear
member and ring gear member will rotate in the same direction.
[0220] The ring gear member 1324 and sun gear member 1332 are
continuously interconnected by an interconnecting member 1370. The
sun gear member 1322 and sun gear member 1342 are continuously
interconnected by an interconnecting member 1372. The ring gear
members 1334 and 1344 are continuously interconnected by an
interconnecting member 1374. The planet carrier assembly member
1336 is continuously connected with the transmission housing 62.
The output shaft 19 is continuously connected with the planet
carrier assembly member 1346, selectively connectible with the
interconnecting member 1370 through the torque-transmitting
mechanism 1356, and selectively interconnectible with the planet
carrier assembly member 1326 through the torque-transmitting
mechanism 1358.
[0221] The input shaft 17 is selectively interconnectible with the
interconnecting member 1370 through the torque-transmitting
mechanism 1350, selectively interconnectible with the planet
carrier assembly member 1326 through the torque-transmitting
mechanism 1352, and selectively interconnectible with the
interconnecting member 1372 through the torque-transmitting
mechanism 1354. The interconnecting member 1370 is selectively
interconnectible with the transmission housing 62 through the
torque-transmitting mechanism 1360.
[0222] The truth table of FIG. 28 describes the engagement
combinations and sequence for the torque-transmitting mechanisms in
order to establish seven forward speed ratios and one reverse speed
ratio between input shaft 17 and the output shaft 19 through the
planetary gear arrangement 1318. The truth table also provides a
numerical example for possible speed ratios for the seven forward
speed ratios as well as the reverse speed ratio when the ring
gear/sun gear tooth ratios of the planetary gearsets 1320, 1330,
and 1340 are as given as R1/S1, R2/S2, and R3/S3, respectively. A
chart in FIG. 28 describes the numerical values for the ratio steps
between the reverse and first forward speed ratio, between the
adjacent forward speed ratios, and the overall ratio spread of the
forward speed ratios.
[0223] Those skilled in the art, upon reviewing the engagement
combinations and the interconnections of the planetary gear
arrangement 1318, will be aware that the numerical value of the
reverse speed ratio, the first forward speed ratio, the fourth
forward speed ratio, and the fifth forward speed ratio are
determined by the ring gear/sun gear tooth ratios of all three
planetary gearsets 1320, 1330, and 1340. The numerical value of
second forward speed ratio and the sixth are determined by the ring
gear/sun gear tooth ratios of the planetary gearsets 1320 and 1340.
The numerical value of the third forward speed ratio is determined
by the ring gear/sun gear tooth ratios of the planetary gearsets
1330 and 1340. The numerical value of the seventh forward speed
ratio is one.
[0224] The family member described in FIG. 27 has no overdrive
ratios, six underdrive ratios, and a direct drive ratio.
[0225] A powertrain 1410, shown in FIG. 29, includes the engine 12,
the starting device 13, a planetary transmission 1414, and the
final drive mechanism 16. The planetary transmission 1414 includes
the input shaft 17, a planetary gear arrangement 1418, and the
output shaft 19. The planetary gear arrangement 1418 includes three
planetary gearsets 1420, 1430, and 1440, five rotating type
torque-transmitting mechanisms 1450, 1452, 1454, 1456 and 1458, and
one stationary type torque-transmitting mechanism 1460.
[0226] The planetary gearset 1420 includes a sun gear member 1422,
a ring gear member 1424, and a planet carrier assembly member 1426.
The planet carrier assembly member 1426 includes a plurality of
pinion gears 1427 rotatably mounted on a planet carrier 1429 and
disposed in meshing relationship with the sun gear member 1422 and
the ring gear member 1424.
[0227] The planetary gearset 1430 includes a sun gear member 1432,
a ring gear member 1434, and a planet carrier assembly member 1436.
The planet carrier assembly member 1436 includes a plurality of
pinion gears 1437 rotatably mounted on a planet carrier 1439 and
disposed in meshing relationship with the sun gear member 1432 and
the ring gear member 1434.
[0228] The planetary gearset 1440 includes a sun gear member 1442,
a ring gear member 1444, and a planet carrier assembly member 1446.
The planet carrier assembly member 1446 includes a plurality of
pinion gears 1447 rotatably mounted on a planet carrier 1449 and
disposed in meshing relationship with the sun gear member 1442 and
the ring gear member 1444.
[0229] The sun gear member 1422 and ring gear member 1434 are
continuously interconnected by an interconnecting member 1470. The
ring gear member 1424 and sun gear member 1442 are continuously
interconnected by an interconnecting member 1472. The planet
carrier assembly member 1436 and ring gear member 1444 are
continuously interconnected by an interconnecting member 1474. The
planet carrier assembly member 1426 is continuously connected with
the transmission housing 62. The planet carrier assembly member
1446 is continuously interconnected with the output shaft 19.
[0230] The input shaft 17 is selectively interconnectible with the
interconnecting member 1470 through the torque-transmitting
mechanism 1450, selectively interconnectible with the sun gear
member 1432 through the torque-transmitting mechanism 1452, and
selectively interconnectible with interconnecting member 1474
through the torque-transmitting mechanism 1454. The output shaft 19
and planet carrier assembly member 1446 are selectively
interconnectible with the interconnecting member 1470 through the
torque-transmitting mechanism 1456 and selectively interconnectible
with the interconnecting member 1472 through the
torque-transmitting mechanism 1458. The interconnecting member 1472
is selectively interconnectible with the transmission housing 62
through the torque-transmitting mechanism 1460.
[0231] The torque-transmitting mechanisms are engaged in
combinations of two, as shown in the truth table of FIG. 30. The
truth table also describes the sequence of engagements for the
torque-transmitting mechanisms, such that seven forward speed
ratios and one reverse speed ratio are established in the planetary
gear arrangement 1418. Also given in the truth table is an example
of the numerical values for the seven forward speed ratios and the
reverse speed ratio. These numerical values are determined by the
ring gear/sun gear tooth ratios of the planetary gearsets 1420,
1430, and 1440, which are given by way of example as R1/S1, R2/S2,
and R3/S3, respectively. A chart shown in FIG. 30 provides the
numerical examples of the ratio steps between adjacent forward
speed ratios, the ratio step between the reverse and first forward
speed ratio, and the overall ratio spread of the forward speed
ratios.
[0232] Those skilled in the art will, upon reviewing the engagement
combinations in the truth table and the interconnections of the
planetary gear arrangement 1418, be aware that the numerical value
of the reverse speed ratio is determined by the ring gear/sun gear
tooth ratio of the planetary gearset 1420. The numerical value of
the first forward speed ratio and the third forward speed ratio are
determined by the ring gear/sun gear tooth ratios of all three
planetary gearsets 1420, 1430, and 1440. The numerical value of the
second forward speed ratio is determined by the ring gear/sun gear
tooth ratios of the planetary gearsets 1430 and 1440. The numerical
value of the fourth forward speed ratio and the fifth forward speed
ratio are determined by the ring gear/sun gear tooth ratios of the
planetary gearsets 1420 and 1440. The numerical value of the sixth
forward speed ratio is determined by the ring gear/sun gear tooth
ratio of the planetary gearset 1440. The numerical value of the
seventh forward speed ratio is one.
[0233] The family member described in FIG. 29, as with the family
member described in FIG. 27, does not have an overdrive ratio but
does have six underdrive ratios and one direct drive ratio.
[0234] A powertrain 1510, shown in FIG. 31, includes the engine 12,
the starting device 13, a planetary transmission 1514, and the
final drive mechanism 16. The planetary transmission 1514 includes
the input shaft 17, a planetary gear arrangement 1518, and the
output shaft 19. The planetary gear arrangement 1518 includes three
planetary gearsets 1520, 1530, and 1540, five rotating type
torque-transmitting mechanisms 1550, 1552, 1554, 1556 and 1558, and
one stationary type torque-transmitting mechanism 1560.
[0235] The planetary gearset 1520 includes a sun gear member 1522,
a ring gear member 1524, and a planet carrier assembly member 1526.
The planet carrier assembly member 1526 includes a plurality of
pinion gears 1527 rotatably mounted on a planet carrier 1529 and
disposed in meshing relationship with the sun gear member 1522 and
the ring gear member 1524.
[0236] The planetary gearset 1530 includes a sun gear member 1532,
a ring gear member 1534, and a planet carrier assembly member 1536.
The planet carrier assembly member 1536 includes a plurality of
pinion gears 1537 rotatably mounted on a planet carrier 1539 and
disposed in meshing relationship with the sun gear member 1532 and
the ring gear member 1534.
[0237] The planetary gearset 1540 includes a sun gear member 1542,
a ring gear member 1544, and a planet carrier assembly member 1546.
The planet carrier assembly member 1546 includes a plurality of
pinion gears 1547 rotatably mounted on a planet carrier 1549 and
disposed in meshing relationship with the sun gear member 1542 and
the ring gear member 1544.
[0238] An interconnecting member 1570 continuously interconnects
the planet carrier assembly member 1526 with the ring gear member
1534. An interconnecting member 1574 continuously interconnects the
planet carrier assembly member 1536 with the planet carrier
assembly member 1546. An interconnecting member 1572 continuously
interconnects the sun gear members 1522 and 1542. The sun gear
member 1532 is continuously interconnected with the transmission
housing 62. The ring gear member 1544 is continuously
interconnected with the output shaft 19.
[0239] The input shaft 17 is selectively interconnectible with the
interconnecting member 1570 through the torque-transmitting
mechanism 1550, selectively interconnectible with the ring gear
member 1524 through the torque-transmitting mechanism 1552, and
selectively interconnectible with the interconnecting member 1572
through the torque-transmitting mechanism 1554. The ring gear
member 1524 is selectively interconnectible with the
interconnecting member 1574 through the torque-transmitting
mechanism 1556. The interconnecting member 1572 is selectively
interconnectible with the interconnecting member 1574 through the
torque-transmitting mechanism 1558. The ring gear member 1524 is
selectively interconnectible with the transmission housing 62
through the torque-transmitting mechanism 1560.
[0240] The truth table shown in FIG. 32 describes the engagement
combinations, as well as the engagement sequence, for the
torque-transmitting mechanisms in order to establish seven forward
speed ratios and one reverse speed ratio in the planetary gear
arrangement 1518 between the input shaft 17 and the output shaft
19. Also provided in the truth table is a numerical example for
each of the forward speed ratios and the reverse speed ratio. These
speed ratio values are determined by the ring gear/sun gear tooth
ratios of the planetary gearsets 1520, 1530, and 1540 as
represented by R1/S1, R2/S2, and R3/S3, respectively. Also given in
FIG. 32 is a chart, which provides a numerical example for the
ratio steps between the reverse and first forward speed ratio, each
of the adjacent forward speed ratios, and the overall ratio spread
of the forward speed ratios.
[0241] Those skilled in the art, upon reviewing the engagement
combinations shown in the truth table, as well as the
interconnections provided in the planetary gear arrangement 1518,
will recognize that the numerical value of the reverse speed ratio,
the first forward speed ratio, the second forward speed ratio, and
the third forward speed ratio are determined by the ring gear/sun
gear tooth ratios of all three planetary gearsets 1520, 1530, and
1540. The numerical value of the fourth forward speed ratio is
determined by the ring gear/sun gear tooth ratios of the planetary
gearsets 1530 and 1540. The numerical value of the fifth forward
speed ratio is determined by the ring gear/sun gear tooth ratios of
the planetary gearsets 1520 and 1530. The numerical value of the
sixth forward speed ratio is determined by the ring gear/sun gear
tooth ratio of the planetary gearset 1430. The numerical value of
the seventh forward speed ratio is one.
[0242] The family member described in FIG. 31 for the planetary
gear arrangement 1518 also provides six underdrive speed ratios and
one direct speed ratio.
[0243] In reviewing the above descriptions of the family members
shown, it should now be apparent that each of the family members
has three planetary gearsets. At least one member of one of the
planetary gearsets is continuously connected with the transmission
housing and another member of one of the planetary gearsets is
continuously connected with the transmission output shaft. The
planetary gearsets are interconnected such that a member of the
first planetary gearset is continuously connected with a member of
the second planetary gearset, another member of the first planetary
gearset is connected with a member of the third planetary gearset,
and another member of the second planetary gearset is connected
with another member of the third planetary gearset. Also provided
within each family member are six torque-transmitting mechanisms,
which are selectively engaged in combinations of two to establish
seven forward speed ratios and one reverse speed ratio in the
planetary gear arrangement of each family member.
[0244] It should also be apparent that modifications and variations
are possible to the family that are not depicted in the
above-described embodiments. Therefore, the invention should only
be limited by the appended claims.
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