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Description  |
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BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates generally to speed change gear systems and
more particularly to a speed change gear system which is adapted for
application with fluid couplings utilized within motor vehicles,
especially automobiles.
2. Description of the Prior Art
It is preferable to utilize at least four gear sets within the speed change
gear systems of large automotive vehicles, such as for example, trucks and
buses, and in order to attain a speed change mechanism having more than
four speed shifts, three, four or even more sets of simple, single-pinion
or double-pinion type planetary gear sets have heretofore been combined.
While the combination of these gears may be widely varied, it is
preferable however that the following conditions be attained:
1. The output shaft should be coupled to the same elements within each
speed range.
2. In order to reduce the circumferential speed of the bearings of each
element of the planetary gear set, the number of its revolutions should be
small.
3. The tooth load, that is, the tangential force of each element should be
small so as to maintain the strength of the gear teeth.
4. The gear set should always attain meshing conditions for the number of
teeth required. For example, the sun gear, whose diameter is to be
minimized, as well as each planetary pinion gear, should have the
necessary number of teeth.
5. Within the planetary gear set, the coupling relationship among the
elements should be simple and the distance from each other should be
small.
6. During speed shifts, wherein frictional coupling means are utilized
during forward drive, such speed shifts should be available through one
coupling means alone.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to provide a speed
change gear system which provides at least four speed ranges for forward
drive and one speed range for reverse drive by the use of two planetary
gear sets of the single-pinion type and one simple planetary gear set of
the double-pinion type, two clutches, and three brakes, whereby the
movable members of each of the planetary gear sets are suitably coupled as
a result of the coupling or uncoupling of the clutches and brakes so as to
attain the various speed ranges.
BRIEF DESCRIPTION OF THE DRAWINGS
Various other objects, features and attendant advantages of the present
invention will be more fully appreciated as the same becomes better
understood from the following detailed description when considered in
conjunction with the accompanying drawings, in which like reference
characters designate like or corresponding parts throughout the several
views, and wherein:
FIG. 1A is a schematic view of one embodiment of a speed change gear system
constructed in accordance with the present invention and disclosing its
cooperative parts;
FIG. 2A is a schematic view similar to that of FIG. 1 showing however
another embodiment of the present invention;
FIG. 3A is a schematic view similar to that of FIG. 1 showing however yet
another embodiment of the present invention;
FIG. 4A is a schematic view similar to that of FIG. 1 showing however still
another embodiment of the present invention;
FIG. 5A is a schematic view similar to that of FIG. 1 showing yet still
another embodiment of the present invention;
FIG. 6A is a schematic view similar to that of FIG. 1 showing however a
further embodiment of the present invention;
FIG. 7A is a schematic view similar to that of FIG. 1 showing however a yet
further embodiment of the present invention;
FIG. 8A is a schematic view similar to that of FIG. 1 showing however a
still further embodiment of the present invention; and
FIG. 9A is a schematic view similar to that of FIG. 1 showing however a yet
still further embodiment of the present invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings and more particularly to FIG. 1A thereof, the
disclosed speed change gear system includes a first planetary gear set
generally indicated by the reference character X.sub.1 of the
double-pinion type, a second planetary gear set generally indicated by the
reference character X.sub.2 of the single-pinion type, and a third
planetary gear set generally indicated by the reference character X.sub.3
of the single-pinion type, all of which are interposed between an input
shaft and an output shaft. The first planetary gear set X.sub.1 is seen to
comprise a first sun gear S.sub.1, first planetary gear P.sub.1 engaged
with the first sun gear S.sub.1, a second planetary gear P.sub.2 engaged
with the first planetary gear P.sub.1, a first ring gear RG.sub.1 enmeshed
with the second planetary gear P.sub.2, and a first carrier C.sub.1
rotatably supporting the first and second planetary gears P.sub.1,
P.sub.2, while the second planetary gear set X.sub.2 similarly includes a
second sun gear S.sub.2, a third planetary gear P.sub.3 engaged with the
second sun gear S.sub.2, a second ring gear RG.sub.2 enmeshed with the
third planetary gear P.sub.3 and a second carrier C.sub.2 rotatably
supporting the third planetary gear P.sub.3 and connected to the output
shaft.
The third planetary gear set X.sub.3 includes a third sun gear S.sub.3, a
fourth planetary gear P.sub.4 engaged with the third sun gear S.sub.3, a
third ring gear RG.sub.3 enmeshed with the fourth planetary gear P.sub.4,
and a third carrier C.sub.3 rotatably supporting the fourth planetary gear
P.sub.4. The second ring gear RG.sub.2, the third carrier C.sub.3 and the
first carrier C.sub.1 are serially connected with each other and a first
clutch CL.sub.1 serves to couple or uncouple the second ring gear
RG.sub.2, the third carrier C.sub.3 and the first carrier C.sub.1 with the
input shaft. The first ring gear RG.sub.1 and the third ring gear RG.sub.3
are similarly drivingly engaged with each other and a second clutch
CL.sub.2 serves to couple or uncouple the first ring gear RG.sub.1 and the
third ring gear RG.sub.3 with the input shaft. Still further, a third
clutch CL.sub.3 serves to couple or uncouple the input shaft and the first
sun gear S.sub.1.
A first brake B.sub.1 is interposed between the first sun gear S.sub.1 and
the gear casing so as to be capable of locking the first sun gear S.sub.1
to the casing when the first brake is actuated and similarly, a second
brake B.sub.2 is interposed between the casing and the element set
comprising the second ring gear RG.sub.2, the third carrier C.sub.3 and
the first carrier C.sub.1 so as to be capable of locking them to the
casing when the second brake is actuated. The second sun gear S.sub.2 and
the third sun gear S.sub.3 are drivingly engaged, and a third brake
B.sub.3 is disposed between the casing and the second and third sun gears
S.sub.2 and S.sub.3 so as to be capable of locking the second and third
sun gears S.sub.2 and S.sub.3 to the casing when the brake is actuated.
The following equations are given as characteristic of the planetary gear
sets X.sub.1, X.sub.2 and X.sub.3 :
n.sub.rg.sbsb.1 -(1 - i.sub.1)n.sub.c.sbsb.1 - i.sub.1 n.sub.s.sbsb.1 = 0
n.sub.rg.sbsb.2 -(1 + i.sub.2)n.sub.c.sbsb.2 + i.sub.2 n.sub.s.sbsb.2 = 0
n.sub.rg.sbsb.3 -(1 + i.sub.3)n.sub.c.sbsb.3 + i.sub.3 n.sub.s.sbsb.3 = 0
wherein:
N.sub.RG.sbsb.1, N.sub.RG.sbsb.2, N.sub.RG.sbsb.3 =the number of
revolutions of the first, second and third ring gears;
N.sub.C.sbsb.1, N.sub.C.sbsb.2, N.sub.C.sbsb.3 =the number of revolutions
of the first, second and third carriers;
N.sub.S.sbsb.1, N.sub.S.sbsb.2, N.sub.S.sbsb.3 =the number of revolutions
of the first, second and third sun gears; and
I.sub.1, I.sub.2, I.sub.3 = the radial ratios of each ring gear to each sun
gear.
Within this embodiment, the radial ratios within each speed range are
I.sub.1 = 0.419, I.sub.2 = 0.548, I.sub.3 = 0.548. Table 1B shows the
relationship between the operation of clutches CL.sub.1, CL.sub.2 and
CL.sub.3 and brakes B.sub.1, B.sub.2 and B.sub.3 relative to the gear
ratio within each speed range, wherein F.sub.n (n =1, 2, 3, . . . )
designates a forward speed range, such as for example, F.sub.1 designates
the first forward speed range, F.sub.2 designates the second forward speed
range, etc. and R.sub.n (n =1, 2, . . . ) designates a reverse speed
range, such as for example, R.sub.1 designates the first reverse speed
range, and it may be seen that a reduction gear ratio of 1 : 1.00 can be
obtained by desirably and selectively employing two of the clutches
CL.sub.1, CL.sub.2 and CL.sub.3. Table 1C shows the relationship regarding
the number of revolutions and the tangential forces of each of the
elements of the planetary gear sets within each speed range. The ratio of
the number of revolutions is based upon the assumption that the number of
revolutions of the input shaft is 1, while the designated tangential
forces are based upon the assumption that the input shaft torque exerted
upon the ring gear is 1, the tangential forces of the planetary gears
being equal to those of the sun gears and the ring gears.
Within Table 1C, like reference characters designate identical or
corresponding parts shown within Table 1B, and in addition, A designates a
particular speed range, B designates an element of the planetary gear set,
N designates the number of revolutions, and W designates the tangential
force. Because the reduction gear ratio of the fourth forward speed range
F.sub.4 is 1 : 1.00, the number of revolutions N of each sun gear, ring
gear, and carrier is 1.00, the number of revolutions N of an individual
sun gear, ring gear and carrier is 1.00, and the number of revolutions N
of each planetary gear is 0.00. The tangential forces W are therefore
considerably less than those produced within the other speed ranges.
Within the other speed ranges, the torque of the input shaft is
transmitted to all of the elements through only one engaged clutch, while
to the contrary, the torque of the input shaft of the fourth speed range
F.sub.4 is distributed to all elements as a result of engaging at least
two clutches, and accordingly, it is clear that the resulting tangential
forces of the elements of such speed range are smaller than those produced
as a result of the transmission of torque from the input shaft as a result
of coupling only one clutch. Hereinafter, a discussion of the number of
revolutions N and the tangential forces W within the speed range having
the reduction gear ratio of 1 : 1.00 will be omitted.
TABLE 1B
______________________________________
Reduction
CL1 CL2 CL3 B1 B2 B3 B4 gear ratio
______________________________________
F1 O O 1 : 3.57
F2 O O 1 : 2.40
F3 O O 1 : 1.55
F4 O O 1 : 1.00
F5 O O 1 : 0.79
F6 O O 1 : 0.46
R1 O O 1 : -3.70
R2 O O 1 : -1.55
______________________________________
TABLE 1C
__________________________________________________________________________
B X1 X2 X3
A S1 C1 RG1 P1 P2 S2 C2 RG2 P3 S3 C3 RG3 P4
__________________________________________________________________________
F1 N 1.00
0.43
0.67
-0.86
0.86 0.0 0.28 0.43
0.68 0.0 0.43
0.67
1.05
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31
2.31 2.39 4.77
2.39
2.39
F2 N 1.49
0.65
1.00
-1.29
1.29 0.00 0.42 0.65
1.01 0.0 0.65
1.00
1.57
W 0.0 0.00
0.00
0.00 0.00 1.55 3.10 1.55
1.55 1.00 2.00
1.00
1.00
F3 N 2.31
1.00
1.55
-1.99
1.99 0.0 0.65 1.00
1.57 0.0 1.00
1.55
2.42
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00
1.00 0.00 0.00
0.00
0.00
F4 N 0.0 1.00
0.58
1.52 -1.52
1.76 1.27 1.00
-1.20
1.76 1.00
0.58
1.85
W 0.51
1.02
0.51
0.51 0.51 0.51 1.02 0.51
0.51 0.51 1.02
0.51
0.51
F5 N 0.0 1.72
1.00
2.62 -2.62
3.04 2.19 1.72
-2.06
3.04 1.72
1.00
3.19
W 1.30
2.59
1.30
1.30 1.30 0.30 0.59 0.30
0.30 0.30 0.59
0.30
0.30
R1 N 1.00
0.0 0.42
-1.52
1.52 -0.76
-0.27
0.0 1.20 -0.76
0.0 0.42
1.85
W 2.39
4.77
2.39
2.39 2.39 2.39 4.77 2.39
2.39 2.39 4.77
2.39
2.39
R2 N 2.39
0.0 1.00
-3.64
3.64 -1.82
-0.65
0.0 2.86 -1.82
0.0 1.00
4.42
W 0.0 0.0 0.00
0.00 0.00 1.00 2.00 1.00
1.00 1.00 2.00
1.00
1.00
__________________________________________________________________________
Referring now to FIG. 2A there is shown another embodiment of the present
invention wherein a fourth planetary gear set generally indicated by the
reference character X.sub.4 of the single-pinion type is interposed
between the third planetary gear set X.sub.3 and the output shaft, such
fourth planetary gear set X.sub.4 including a fourth sun gear S.sub.4
connected to the output shaft as well as to the second carrier C.sub.2, a
fifth planetary gear P.sub.5 engaged with the fourth sun gear S.sub.4, a
fourth ring gear RG.sub.4 enmeshed with the fifth planetary gear P.sub.5,
and a fourth carrier C.sub.4 rotatably supporting the fifth planetary gear
P.sub.5. The fourth ring gear RG.sub.4 is also drivingly engaged with the
second and third sun gears S.sub.2 and S.sub.3 and is additionally locked,
in conjunction with the second and third sun gears S.sub.2 and S.sub.3, to
the gear casing when the third brake B3 is actuated. A fourth brake
B.sub.4 is also interposed between the fourth carrier C.sub.4 and the
casing so as to be capable of locking the former to the latter when the
brake is actuated.
The following formula is given as characteristic of the fourth planetary
gear set X.sub.4 :
n.sub.rg.sbsb.4 - (1 + i.sub.4)n.sub.c.sbsb.4 + i.sub.4 n.sub.s.sbsb.4 = 0
wherein:
N.sub.RG.sbsb.4 =the number of revolutions of the fourth ring gear;
N.sub.C.sbsb.4 = the number of revolutions of the fourth carrier;
N.sub.S.sbsb.4 = the number of revolutions of the fourth sun gear; and
I.sub.4 = the radial ratio of the fourth ring gear to the fourth sun gear.
Within this embodiment, the radial ratio within each speed range is I.sub.4
= 0.562. Table 2B shows the relationship between the operation of all
clutches CL.sub.1, CL.sub.2, and CL.sub.3 and brakes B.sub.1, B.sub.2,
B.sub.3 and B.sub.4 with respect to the reduction gear ratio within each
speed range and Table 2C shows the relationship regarding the number of
revolutions and the tangential forces of the elements of the planetary
gear sets within each speed range.
TABLE 2B
______________________________________
Reduction
CL1 CL2 CL3 B1 B2 B3 B4 gear ratio
______________________________________
F1 O O 1 : 5.02
F2 O O 1 : 3.57
F3 O O 1 : 3.18
F4 O O 1 : 2.40
F5 O O 1 : 1.86
F6 O O 1 : 1.55
F7 O O 1 : 1.00
F8 O O 1 : 0.79
F9 O O 1 : 0.46
R1 O O 1 : -3.70
R2 O O 1 : -1.55
______________________________________
TABLE 2C
__________________________________________________________________________
B X1 X2
A S1 C1 RG1 P1 P2 S2 C2 RG2 P3
__________________________________________________________________________
F1 N 1.00
0.37
0.63
-0.96
0.96 -0.11
0.20 0.37 0.75
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31 2.31
F2 N 1.00
0.43
0.67
-0.86
0.86 0.0 0.28 0.43 0.68
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31 2.31
F3 N 1.58
0.58
1.00
-1.51
1.51 -0.18
0.31 0.58 1.19
W 0.0 0.00
0.00
0.00 0.00 1.55 3.10 1.55 1.55
F4 N 1.49
0.65
1.00
-1.29
1.29 0.0 0.42 0.65 1.01
W 0.0 0.00
0.00
0.00 0.00 1.55 3.10 1.55 1.55
F5 N 2.70
1.00
1.71
-2.60
2.60 -0.30
0.54 1.00 2.00
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
F6 N 2.31
1.00
1.55
-1.99
1.99 0.0 0.65 1.00 1.57
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
F8 N 0.0 1.00
0.58
1.52 -1.52
1.76 1.27 1.00 - 1.20
W 0.51
1.02
0.51
0.51 0.51 0.51 1.02 0.51 0.51
F9 N 0.0 1.72
1.00
2.62 -2.62
3.04 2.19 1.72 -2.06
W 1.30
2.59
1.30
1.30 1.30 0.30 0.59 0.30 0.30
R1 N 1.00
0.0 0.42
-1.52
1.52 -0.76
-0.27
0.0 1.20
W 2.39
4.77
2.39
2.39 2.39 2.39 4.77 2.39 2.39
R2 N 2.39
0.0 1.00
-3.64
3.64 -1.82
-0.65
0.0 2.86
W 0.0 0.0 0.00
0.00 0.00 1.00 2.00 1.00 1.00
__________________________________________________________________________
B X3 X4
A S3 C3 RG3 P4 S4 C4 RG4 P5
__________________________________________________________________________
F1 N -0.11 0.37 0.63 1.17 0.20 0.00 -0.11
-0.51
W 2.39 4.77 2.39 2.39 2.57 5.15 2.57 2.57
F2 N 0.0 0.43 0.67 1.05 0.28 0.10 0.0 -0.46
W 2.39 4.77 2.39 2.39 0.0 0.0 0.0 0.0
F3 N -0.18 0.58 1.00 1.84 0.31 0.00 -0.18
-0.81
W 1.00 2.00 1.00 1.00 1.40 2.79 1.40 1.40
F4 N 0.0 0.65 1.00 1.57 0.42 0.15 0.0 -0.69
W 1.00 2.00 1.00 1.00 0.0 0.0 0.0 0.0
F5 N -0.30 1.00 1.71 3.16 0.54 0.00 -0.30
-1.38
W 0.00 0.00 0.00 0.00 0.55 1.10 0.55 0.55
F6 N 0.0 1.00 1.55 2.42 0.65 0.23 0.0 -1.06
W 0.00 0.00 0.00 0.00 0.0 0.0 0.0 0.0
F8 N 1.76 1.00 0.58 -1.85 1.27 1.59 1.76 0.81
W 0.51 1.02 0.51 0.51 0.0 0.0 0.0 0.0
F9 N 3.04 1.72 1.00 -3.19 2.19 2.73 3.04 1.40
W 0.30 0.59 0.30 0.30 0.0 0.0 0.0 0.0
R1 N -0.76 0.00 0.42 1.85 -0.27
-0.59
-0.76
-0.81
W 2.39 4.77 2.39 2.39 0.0 0.0 0.0 0.0
R2 N -1.82 0.00 1.00 4.42 -0.65
-1.40
-1.82
-1.94
W 1.00 2.00 1.00 1.00 0.0 0.0 0.0 0.0
__________________________________________________________________________
Referring now to FIG. 3A, yet another embodiment of the present invention
is disclosed wherein the fourth planetary gear set X.sub.4 of the
single-pinion type includes a fourth sun gear S.sub.4 drivingly engaged
with the second and third sun gears S.sub.2 and S.sub.3 and being capable
of being locked, together with the second and third sun gears S.sub.2 and
S.sub.3, to the gear casing when the third brake B.sub.3 is actuated. The
fourth brake B.sub.4 is interposed between the fourth carrier C.sub.4 and
the casing so as to be capable of locking the fourth carrier C.sub.4
thereto when B.sub.4 is actuated, and the ring gear RG.sub.4 is connected
to the output shaft. Within this embodiment, the radial ratio within each
speed range is I.sub.4 = 0.562 and Table 3B shows the relationship between
the operation of the clutches and brakes with respect to the reduction
gear ratios within each speed range while Table 3C shows the relationship
regarding the number of revolutions and the tangential forces of the
elements of the planetary gear sets within each speed range.
TABLE 3B
______________________________________
Reduction
CL1 CL2 CL3 B1 B2 B3 B4 gear ratio
______________________________________
F1 O O 1 : 8.15
F2 O O 1 : 4.88
F3 O O 1 : 3.57
F4 O O 1 : 2.52
F5 O O 1 : 2.40
F6 O O 1 : 1.55
F7 O O 1 : 1.00
F8 O O 1 : 0.79
F9 O O 1 : 0.46
R1 O O 1 : -3.70
R2 O O 1 : -1.55
______________________________________
TABLE 3C
__________________________________________________________________________
B X1 X2
A S1 C1 RG1 P1 P2 S2 C2 RG2 P3
__________________________________________________________________________
F1 N 1.00
0.31
0.60
-1.05
1.05 -0.22
0.12 0.31 0.83
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31 2.31
F2 N 1.67
0.52
1.00
-1.76
1.76 -0.36
0.20 0.52 1.38
W 0.0 0.00
0.0 0.0 0.0 1.55 3.10 1.55 1.55
F3 N 1.00
0.43
0.67
-0.86
0.86 0.00 0.28 0.43 0.68
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31 2.31
F4 N 3.23
1.00
1.93
-3.40
3.40 -0.71
0.40 1.00 2.67
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
F5 N 1.49
0.65
1.00
-1.29
1.29 0.0 0.42 0.65 1.01
W 0.0 0.00
0.00
0.00 0.00 1.55 3.10 1.55 1.55
F6 N 2.31
1.00
1.55
-1.99
1.99 0.0 0.65 1.00 1.57
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
F8 N 0.0 1.00
0.58
1.52 -1.52
1.76 1.27 1.00 - 1.20
W 0.51
1.02
0.51
0.51 0.51 0.51 1.02 0.51 0.51
F9 N 0.0 1.72
1.00
2.62 -2.62
3.04 2.19 1.72 -2.06
W 1.30
2.59
1.30
1.30 1.30 0.30 0.59 0.30 0.30
R1 N 1.00
0.0 0.42
-1.52
1.52 -0.76
-0.27
0.0 1.20
W 2.39
4.77
2.39
2.39 2.39 2.39 4.77 2.39 2.39
R2 N 2.39
0.0 1.00
-3.64
3.64 -1.82
-0.65
0.0 2.86
W 0.0 0.0 0.00
0.00 0.00 1.00 2.00 1.00 1.00
__________________________________________________________________________
B X3 X4
A S3 C3 RG3 P4 S4 C4 RG4 P5
__________________________________________________________________________
F1 N -0.22 0.31 0.60 1.28 -0.22
-0.00
0.12 0.56
W 2.39 4.77 2.39 2.39 4.58 9.16 4.58 4.58
F2 N -0.36 0.52 1.00 2.14 -0.36
-0.00
0.20 0.94
W 1.00 2.00 1.00 1.00 2.48 4.97 2.48 2.48
F3 N 0.0 0.43 0.67 1.05 0.0 0.18 0.23 0.46
W 2.39 4.77 2.39 2.39 0.0 0.0 0.0 0.0
F4 N -0.71 1.00 1.93 4.13 -0.71
0.0 0.40 1.81
W 0.00 0.00 0.00 0.00 0.98 1.95 0.98 0.98
F5 N 0.0 0.65 1.00 1.57 0.0 0.27 0.42 0.69
W 1.00 2.00 1.00 1.00 0.0 0.0 0.0 0.0
F6 N 0.0 1.00 1.55 2.42 0.0 0.41 0.65 1.06
W 0.00 0.00 0.00 0.00 0.0 0.0 0.0 0.0
F8 N 1.76 1.00 0.58 -1.85 1.76 1.45 1.27 -0.81
W 0.51 1.02 0.51 0.51 0.00 0.0 0.0 0.0
F9 N 3.04 1.72 1.00 -3.19 3.04 2.49 2.19 -1.40
W 0.30 0.59 0.30 0.30 0.00 0.0 0.0 0.0
R1 N -0.76 0.00 0.42 1.85 -0.76
-0.45
-0.27
0.81
W 2.39 4.77 2.39 2.39 0.00 0.0 0.0 0.0
R2 N -1.82 0.00 1.00 4.42 -1.82
-1.07
-0.65
1.94
W 1.00 2.00 1.00 1.00 0.00 0.0 0.0 0.0
__________________________________________________________________________
A fourth embodiment of a speed change gear system constructed in accordance
with the present invention is illustrated within FIG. 4A and includes a
fourth planetary gear set X.sub.4 of the single-pinion type interposed
between the third planetary gear set X.sub.3 and the output shaft, the
fourth carrier C.sub.4 being drivingly engaged with the second and third
sun gears S.sub.2 and S.sub.3 so as to be capable of being locked to the
gear casing when the third brake B.sub.3 is actuated. The fourth brake
B.sub.4 is disposed between the fourth sun gears S.sub.4 and the casing so
as to be capable of locking the fourth sun gear S.sub.4 thereto when the
brake B.sub.4 is actuated, and the fourth ring gear RG.sub.4 is drivingly
engaged with the second carrier C.sub.2 through means of the output shaft.
Within this embodiment, the radial ratio within each speed range is
I.sub.4 = 0.562, and Table 4B shows the relationship between the operation
of the clutches and brakes with respect to the reduction gear ratio within
each speed range while Table 4C shows the relationship regarding the
number of revolutions and the tangential forces of all of the embodiments
of the planetary gear sets within each speed range.
TABLE 4B
______________________________________
Reduction
CL1 CL2 CL3 B1 B2 B3 B4 gear ratio
______________________________________
F1 O O 1 : 3.57
F2 O O 1 : 2.40
F3 O O 1 : 1.93
F4 O O 1 : 1.55
F5 O O 1 : 1.52
F6 O O 1 : 1.20
F7 O O 1 : 1.00
F8 O O 1 : 0.79
R1 O O 1 : -3.70
R2 O O 1 : -1.55
______________________________________
TABLE 4C
__________________________________________________________________________
B XI X2
A S1 C1 RG1 P1 P2 S2 C2 RG2 P3
__________________________________________________________________________
F1 N 1.00
0.43
0.67
-0.86
0.86 0.0 0.28 0.43 0.68
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31 2.31
F2 N 1.49
0.65
1.00
-1.29
1.29 0.0 0.42 0.65 1.01
W 0.0 0.0 0.00
0.00 0.00 1.55 3.10 1.55 1.55
F3 N 1.00
0.62
0.78
-0.58
0.58 0.33 0.52 0.62 0.45
W 2.39
4.77
2.39
2.39 2.39 2.31 4.62 2.31 2.31
F4 N 2.31
1.00
1.55
-1.99
1.99 0.0 0.65 1.00 1.57
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
F5 N 1.28
0.80
1.00
-0.74
0.74 0.43 0.67 0.80 0.58
W 0.0 0.0 0.00
0.00 0.00 1.55 3.10 1.55 1.55
F6 N 1.61
1.00
1.25
-0.93
0.93 0.53 0.84 1.00 0.73
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
F8 N 0.0 1.00
0.58
1.52 -1.52
1.76 1.27 1.00 -1.20
W 0.51
1.02
0.51
0.51 0.51 0.51 1.02 0.51 0.51
R1 N 1.00
0.0 0.42
-1.52
1.52 -0.76
-0.27
0.0 1.20
W 2.39
4.77
2.39
2.39 2.39 2.39 4.77 2.39 2.39
R2 N 2.39
0.0 1.00
-3.64
3.64 -1.82
-0.65
0.0 2.86
W 0.0 0.00
0.00
0.00 0.00 1.00 2.00 1.00 1.00
__________________________________________________________________________
B X3 X4
A S3 C3 RG3 P4 S4 C4 RG4 P5
__________________________________________________________________________
F1 N 0.0 0.43 0.67 1.05 -0.50
0.0 0.28 1.28
W 2.39 4.77 2.39 2.39 0.0 0.00 0.00 0.00
F2 N 0.0 0.65 1.00 1.57 -0.74
0.0 0.42 1.91
W 1.00 2.00 1.00 1.00 0.0 0.00 0.00 0.00
F3 N 0.33 0.62 0.78 0.70 0.0 0.33 0.52 0.85
W 2.39 4.77 2.39 2.39 1.65 3.29 1.65 1.65
F4 N 0.0 1.00 1.55 2.42 -1.15
0.0 0.65 2.95
W 0.00 0.00 0.00 0.00 0.0 0.00 0.00 0.00
F5 N 0.43 0.80 1.00 0.90 0.0 0.43 0.67 1.09
W 1.00 2.00 1.00 1.00 0.89 1.79 0.89 0.89
F6 N 0.53 1.00 1.25 1.13 0.0 0.53 0.84 1.37
W 0.00 0.00 0.00 0.00 0.35 0.70 0.35 0.35
F8 N 1.76 1.00 0.58 -1.85 2.64 1.76 1.27 -2.26
W 0.51 1.02 0.51 0.51 0.0 0.00 0.00 0.00
R1 N -0.76 0.00 0.42 1.85 -1.64
-0.76
-0. | | |
