Automatic transmission

An automatic transmission includes a fluid-pressure differential cylinder for select operation of the transmission and a fluid-pressure differential cylinder for shift operation of the transmission, each of the differential cylinders being built up into one block and joined with the mating differential cylinder with intake and discharge holes in one block held in communication with intake and discharge holes, respectively, in the other block. A piston rod of each of the differential cylinders has an annular groove and a cylinder block is provided with a locking member engageable with the groove to provide a reference position for the piston rod.

BACKGROUND OF THE INVENTION 
1. Field of the Invention: 
The present invention relates to an automatic transmission for use in an 
automobile. 
2. Prior Art: 
The performance of an automatic transmission greatly depends on 
characteristics of fluid-pressure differential cylinders for shift and 
select operations of the transmission, which cylinders are operative as 
actuators for displacing a shift lever. 
As shown in Japanese Patent Laid-open Publication Nos. 58-146722 and 
60-146953, for example, a solenoid-operated valve used to control a 
fluid-pressure differential cylinder is controlled periodically by a pulse 
signal while regulating the duty factor of the pulse signal to eventually 
control the mechanical output of the cylinder. 
The pulse signal used in the disclosed valve control has a pulse repetition 
frequency (e.g. 40 Hz) equal to an on-off response time of the 
solenoid-operated valve. Thus, the pulse repetition period is equal to 25 
m sec. in which instance the minimum pulse width is 6 m sec. or more and 
hence the pulse duty factor is regulated such that it varies to increase 
from a minimum value corresponding to this minimum pulse width. Where the 
pulse signal has a pulse repetition period of 25 m sec. and a minimum 
width of 6 m sec., each pulse (i.e., a single cycle of on-off operation of 
the valve) causes the piston to be displaced about 0.1 mm even though the 
displacement is related to the volume of the cylinder, the pressure of the 
working fluid, etc. This means that the output of the cylinder can be 
regulated stepwise by about 0.1 mm at a minimum and hence the resolution 
of the cylinder output is about 0.1 mm. 
When the fluid-pressure cylinder having such resolution of the order of 0.1 
mm is used, shift and select positions are determined with an error of 
about 0.2 mm, thus causing deterioration of the performance of an 
automatic transmission in which the cylinder is employed. 
Further, two such fluid-pressure differential cylinders are disposed 
separately for effecting shift and select operations, respectively, of the 
automatic transmission, and they are connected to the corresponding 
pipings. 
Such separate piping requires an increased number of attachments or 
fittings and hence the piping work is complicated as a whole. 
Moreover, the piston of the cylinder is not provided 
e position, positional adjustment of a piston rod and a shift lever must be 
carried out by the trial-and-error method. 
Such trial-and-error positional adjustment is tedious and time-consuming. 
SUMMARY OF THE INVENTION 
It is accordingly an object of the present invention to provide an 
automatic transmission incorporating fluid-pressure differential cylinders 
for shift and select operations which are capable of determining shift and 
select positions accurately, thereby improving the accuracy of the 
transmission as a whole. 
Another object of the present invention is to provide an automatic 
transmission having fluid-pressure differential cylinders for shift and 
select operations which can be connected to a piping with utmost ease. 
A further object of the present invention is to provide an automatic 
transmission having structural features which enable simple positional 
adjustment between a drive side constitute by fluid-pressure differential 
cylinders for shift and select operations, and a driven side constituted 
by a shift-lever actuator device. 
According to a first aspect of the present invention, there is provided an 
automatic transmission comprising: 
a first fluid-pressure differential cylinder for select operation of said 
automatic transmission; 
a second fluid-pressure differential cylinder for shift operation of said 
automatic transmission; 
each of said first and second fluid-pressure differential cylinders 
including a first chamber and a second chamber having a larger pressure 
receiving area than said first chamber, said first chamber being connected 
through a first connecting passage to a hydraulic power supply, said 
second chamber being connected through a second connecting passage to a 
tank, said first and second chambers being connected together by a third 
connecting passage; 
a first solenoid-operated valve disposed in said first connecting passage 
for making and blocking a fluid communication between said first chamber 
and said hydraulic power supply; 
a second solenoid-operated valve disposed in said third connecting passage 
for opening and closing the latter; 
a third solenoid-operated valve disposed in said second connecting passage 
for opening and closing the latter; 
a pulse generator connected with said second and third solenoid-operated 
valves for issuing them a high frequency pulse signal having a pulse 
repetition period shorter than an on-off response time of each of said 
second and third solenoid-operated valves, the duty factor of said pulse 
signal being variable; and 
a shift-lever actuator device connected with said first and second 
fluid-pressure differential cylinders respectively through first and 
second transmission means for receiving mechanical positional outputs of 
the respective cylinders to select a gear position corresponding to the 
thus-received mechanical positional outputs. 
Since the second and third solenoid-operated valves are driven by a high 
frequency pulse signal having a pulse repetition period shorter than the 
on-off response time of the second and third solenoid-operated valves, it 
is possible to control the valve opening area in the analog manner, thus 
providing a fine adjustment of inflow and outflow of working fluid of the 
valves. With this fine flow control, the fluid-pressure differential 
cylinders are capable of producing accurate mechanical positional outputs 
which make it possible to effect accurate and smooth shift and select 
operations of the transmission. 
According to a second aspect of the present invention, there is provided an 
automatic transmission comprising: 
a first fluid-pressure differential cylinder for select operation of said 
automatic transmission; 
a second fluid-pressure differential cylinder for shift operation of said 
automatic transmission; 
each of said first and second fluid-pressure differential cylinders 
including a first chamber and a second chamber having a larger pressure 
receiving area than said first chamber, said first chamber being connected 
through a first connecting passage to a hydraulic power supply, said 
second chamber being connected through a second connecting passage to a 
tank, said first and second chambers being connected together by a third 
connecting passage; 
a first solenoid-operated valve disposed in said first connecting passage 
for making and blocking a fluid communication between said first chamber 
and said hydraulic power supply; 
a second solenoid-operated valve disposed in said third connecting passage 
for opening and closing the latter; 
a third solenoid-operated valve disposed in said second connecting passage 
for opening and closing the latter; 
a pulse generator connected with said second and third solenoid-operated 
valves for issuing them a high frequency pulse signal having a pulse 
repetition period shorter than the on-off response time of each of said 
second and third solenoid-operated valves, the duty factor of said pulse 
signal being variable; 
a shift-lever actuator device connected with said first and second 
fluid-pressure differential cylinders respectively through first and 
second transmission means for receiving mechanical positional outputs of 
the respective cylinders to select a gear position corresponding to the 
thus-received mechanical positional outputs; 
a first block containing said first fluid-pressure differential cylinder 
and having a fluid intake hole and a fluid discharge hole, said intake and 
discharge holes opening to a face of said first block respectively through 
a pair of fluid passages defined in said first block; 
a second block containing said second fluid-pressure differential cylinder 
and having a fluid intake hole and a fluid discharge hole; and 
connecting means for joining said first and second blocks together such 
that said first and second blocks are contacting facewise with each other 
with said openings at said face held in communication with said intake and 
discharge holes in said second block. 
The first and second fluid-pressure differential cylinders thus united has 
only one pair of intake and discharge holes and hence can be connected 
with a piping system with utmost ease. 
According to a third aspect of the present invention, there is provided an 
automatic transmission comprising: 
a first fluid-pressure differential cylinder for select operation of said 
automatic transmission; 
a second fluid-pressure differential cylinder for shift operation of said 
automatic transmission; 
each of said first and second fluid-pressure differential cylinders 
including a first chamber and a second chamber having a larger pressure 
receiving area than said first chamber, said first chamber being connected 
through a first connecting passage to a hydraulic power supply, said 
second chamber being connected through a second connecting passage to a 
tank, said first and second chambers being connected together by a third 
connecting passage; 
a first solenoid-operated valve disposed in said first connecting passage 
for making and blocking a fluid communication between said first chamber 
and said hydraulic power supply; 
a second solenoid-operated valve disposed in said third connecting passage 
for opening and closing the latter; 
a third solenoid-operated valve disposed in said second connecting passage 
for opening and closing the latter; 
a pulse generator connected with said second and third solenoid-operated 
valves for issuing them a high frequency pulse signal having a pulse 
repetition period shorter than the on-off response time of each of said 
second and third solenoid-operated valves, the duty factor of said pulse 
signal being variable; 
a shift-lever actuator device connected with said first and second 
fluid-pressure differential cylinders respectively through first and 
second transmission means for receiving mechanical positional outputs of 
the respective cylinders to select a gear position corresponding to the 
thus received mechanical positional outputs; 
a first block containing said first fluid-pressure differential cylinder 
and having a fluid intake hole and a fluid discharge hole, said intake and 
discharge holes opening to a face of said first block respectively through 
a pair of fluid passages defined in said first block; 
a second block containing said second fluid-pressure differential cylinder 
and having a fluid intake hole and a fluid discharge hole; 
connecting means for joining said first and second blocks together such 
that said first and second blocks are contacting facewise with each other 
with said openings at said face held in communication with said intake and 
discharge holes in said second block; 
first positioning means for determining a reference position of a piston 
rod of said first fluid-pressure differential cylinder, said first 
positioning means including an annular groove defined on a circumferential 
surface of said piston rod, and a locking member fittingly engageable with 
said annular groove; and 
second positioning means for determining a reference position of a piston 
rod of said second fluid-pressure differential cylinder, said second 
positioning means including an annular groove defined on a circumferential 
surface of the last-named piston rod, and a lock member fittingly 
engageable with the last-named annular groove. 
With this construction, when each of the locking members is fitted into a 
corresponding one of the grooves, a muscle effort is required to displace 
the piston rod in an axial direction. Thus the reference position of the 
piston is determined mechanically, thereby enabling an easy adjustment of 
connection between the piston rod and the shift-lever actuator device.

DETAILED DESCRIPTION 
A preferred embodiment of the present invention will be described below in 
greater detail with reference to the accompanying drawings. 
FIG. 1 schematically shows part of an automatic transmission embodying the 
present invention. The automatic transmission comprises a fluid-pressure 
differential cylinder la for select operation of the transmission, a 
fluid-pressure differential cylinder 1b for shift operation of the 
transmission, first and second transmission means 2a, 2b for transmitting 
mechanical positional outputs of the respective differential cylinders 1a, 
1b to a shift-lever actuating device 3 which in turn selects a gear 
position corresponding to the mechanical positional outputs. 
As shown in FIGS. 2 through 6 and FIGS. 11 and 12, the fluid-pressure 
differential cylinders 1a, 1b are identical in construction and each 
include a cylinder body 4, first to third solenoid-operated valves 5-7, 
and a position sensor 8. 
The cylinder body 4, as shown in FIG. 4, includes a cylinder block 9 having 
an internal cylinder bore 10 closed at one end thereof by a cover plate 
11. A stepped piston 12 is slidably fitted in the cylinder bore 10 to 
define two chambers 13 and 14 in the cylinder body 4 on opposite sides of 
the piston 12. The chamber 13 is disposed on a small pressure-receiving 
area side of the piston 12 while the chamber 14 is disposed on a large 
pressure-receiving area side of the piston 12. 
The piston 12 has a piston rod 15 slidably received in a through-hole 16 in 
the cylinder block 9 and projecting outwardly therefrom at one end 
thereof. The projecting end of the piston rod 15 is concentrically 
threaded to an output connecting rod 17 and supports thereon a connecting 
lever 18 for connection with the position sensor 8. 
The piston rod 15 has n annular groove 20 at a proper position on its 
circumferential surface. The block 9 has a stepped vertical hole 21 
extending perpendicular to the through-hole 16 and opening at one end to 
the through-hole 16 for receiving therein a locking member 22. The locking 
member 22 is in the form of a detent mechanism and includes a ball 22a, a 
compression coil spring 22b and a mounting screw 22c. The mounting screw 
22c is threaded into a threaded portion of the stepped bore and has a 
blind hole extending longitudinally from the distal end of its shank. The 
ball 22a is slidably retained in the blind hole and urged outwardly to 
project into the through-hole 16 by means of the spring 22b which is 
disposed in the blind hole and acts between the ball 22a and the mounting 
screw 22c. The ball 22a of the lock member 22 thus constructed is 
snappingly engageable with the annular groove 20 of the piston rod 15 to 
thereby releasably lock the piston rod 15 aganist axial displacement, 
thereby making it possible to determine a reference position of the piston 
12. 
In the illustrated embodiment, the reference position is set at a midpoint 
of the stroke of the piston 12. With the reference position thus provided, 
a driven member which is connected to the piston rod 15 via the output 
connecting rod 17 can easily be set at a midpoint of the stroke thereof, 
accordingly. 
The reference position of the piston 12 can easily be sensed by the 
operator as the resistance to an axial movement of the piston rod 15 is 
suddenly changed upon arrival of the piston 12 at the reference position 
or departure of the piston 12 from the reference position (i.e., upon 
engagement and disengagement of the locking member 22 with the annular 
groove 20) when the piston rod 15 is axially displaced while the 
solenoid-operated valves 5-7 are kept de-energized. The resistance is 
negligible when the piston 12 is displaced by the force of the pressurized 
working fluid. 
The position sensor 8 is so constructed as to detect a displacement or a 
positional change of the piston rod 15 as a change of electric resistance. 
The position sensor 8 is disposed below the cylinder body 4 and supported 
by the cover plate 11 and a support bracket 24 depending from the cylinder 
block 9. The position sensor 8 has a sensor rod 23 projecting outwardly 
from the body of the position sensor 8 and connected at an outer end to 
the connecting lever 18 secured to the piston rod 15. 
Four connecting holes 25 extend through the block 9 from a front face to a 
rear face of the block 9 and disposed adjacent to four corners of the 
block 9 for receiving respectively therein connecting bolts 26 (FIGS. 11 
and 12) when the differential cylinders 1a, 1b are joined together as 
described later on. 
The first solenoid-operated valve 5, as shown in greater detail in FIG. 7, 
includes a body 30 having a downwardly extending tubular mounting portion 
32 and a plunger guide tube 33 disposed concentrically above the mounting 
portion 32, the mounting portion 32 being externally threaded as at 31. A 
cylindrical excitation coil 34 is disposed around the plunger guide tube 
33 and held in position against displacement by a molded synthetic resin 
35 covered by a case 36. 
The case 36 is secured to the valve body 30 by means of a nut 37 threaded 
to an upper end of the plunger guide tube 33. The plunger guide tube 33 
movably receives therein a plunger 38 which is normally urged axially 
downwardly by a compression coil spring 40 disposed between an upper end 
of the plunger 38 and an end cap 39 fitted into the upper end of the 
plunger guide tube 33. 
The tubular mounting portion 32 of the body 30 is also internally threaded 
as at 41 and guidedly receives therein a rod guide member 42. The rod 
guide, member 42 is firmly retained in the mounting portion 32 by a valve 
seat member 43 threaded into the internally threaded hole 41 of the 
tubular mounting portion 32. 
The valve seat member 43 has an externally threaded upper portion 44 
tightly fastened to the mounting portion 32, a central axial hole 45 
extending longitudinally therethrough, a radial inlet port 46 disposed 
adjacent to the externally threaded upper portion 44 and communicating 
with the axial hole 45, and a radial outlet port 47 disposed below the 
inlet port 46 and communicating with the axial hole 45. The axial hole 45 
is stepped at a portion between the inlet port 46 and the outlet port 47 
so as to form a downwardly facing valve seat 48. 
A valve element 49 comprising a ball valve is held in a valve retainer 50 
and urged into contact with the valve seat 48 by means of a compression 
coil spring 51 acting between the valve retainer 50 and a spring retainer 
threaded to a lower portion of the valve seat member 43. 
The valve element 49 is held in contact with one end of a push rod 53 
connected at the other end to the plunger 38 so that when the excitation 
coil 34 is de-energized, the valve element 49 is held in contact with the 
valve seat 48 under the force of the spring 51, thereby closing the 
solenoid-operated valve 5. 
As shown in FIGS. 2-6, the first solenoid-operated valve 5 of the foregoing 
construction is mounted on the cylinder block 9 by threading the mounting 
portion 32 into an internally threaded mounting hole 100 in the cylinder 
block 9. In this mounted condition, the inlet port 46 of the valve seat 
member 43 opens at its one end to a lower portion of the mounting hole 
100. The mounting hole 100 is connected to an intake hole 104 through a 
fluid passage 103 formed in the body 4 and hence the inlet port 46 of the 
first solenoid-operated valve 5 is held in fluid communication with the 
intake hole 104. 
On the other hand, the outlet port 47 of the first solenoid-operated valve 
5 is connected through a fluid passage 105 in the cylinder block 9 with 
the small pressure-receiving area side chamber 13 in the cylinder body 4. 
The second solenoid-operated valve 6 is shown in greater detail in FIG. 8, 
in which a body 60 of the valve 6 includes a downwardly projecting tubular 
mounting portion 62 threaded externally as at 61, and a plunger guide tube 
63 disposed concentrically above the tubular mounting portion 60. A 
cylindrical excitation coil 64 is disposed around the plunger guide tube 
63 and firmly retained in position against displacement by being embedded 
in a molded synthetic resin 65 covered by a case 66. 
The case 66 is secured to the valve body 60 by means of a nut 67 threaded 
over an externally threaded upper end of the plunger guide tube 63. The 
plunger guide tube 63 movably receives therein a plunger 68 which is 
normally urged axially downwardly under the force of a compression coil 
spring 70 disposed between an upper end of the plunger 68 and an end cap 
69 fitted in the upper end of the plunger guide tube 63. 
The mounting portion 62 of the body 60 is also internally threaded as at 71 
and guidedly receives therein a rod guide member 72. The rod guide member 
72 is firmly retained in the mounting protion 62 by means of a valve seat 
member 73 threaded into the internally threaded hole 71 in the tubular 
mounting portion 62. 
The valve seat member 73 has an extenally threaded upper portion 74 
fastened to the mounting portion 62, and an axial hole 75 extending 
longitudinally through the valve seat member 73, the lower end of the 
axial hole 75 constituting the only inlet port 76. The valve seat member 
73 also has a radial outlet port 77 disposed upwardly of the inlet port 
76, and an upwardly facing annular valve seat 78 disposed between the 
inlet port 76 and the outlet port 77. 
A valve element 73 is in the from of a ball valve and held in a valve 
retainer 80 movably received in the axial hole 75 in the valve seat member 
73. A compression coil spring 82 acts between, the valve seat member 73 
and an upper flange 81 of the valve retainer 80 to urge the valve retainer 
80 upwardly. The valve element 79 is thus normally held out of contact 
with the valve seat 78 under the force of the spring 82. The valve 
retainer 80 is held in contact with a lower end of a push rod 83 which in 
turn is connected at its upper end to the plunger 68. With this 
construction, when the excitation coil 64 is de-energized, the valve 
element 79 is held out of contact with the valve seat 78 under the force 
of the spring 82. The second solenoid-operated valve 6 therefore normally 
stands opened. 
The second solenoid-operated valve 6 of the foregoing construction is 
mounted on the cylinder block 9, as shown in FIGS. 2 and 6, in which the 
mounting portion 62 of the valve 6 is threaded into an internally threaded 
mounting hole 101 in the cylinder block 9. In this mounted condition, the 
inlet port 76 is communicated with the fluid passage 105 through a fluid 
passage 106 while the outlet port 77 is opening to a lower portion of the 
mounting hole 101 and connected through a fluid passage 107 to the large 
pressure-receiving area side chamber 12 in the cylinder body 4. 
As shown in FIG. 9, the third solenoid-operated valve 7 is identical in 
structure to the second solenoid-operated valve 6 described above and 
hence no description is necessary. In this identical structure, 
corresponding parts are designated by the same reference numerals with a 
prime affixed thereto. The third solenoid-operated valve 7 is mounted on 
the cylinder block 9 by threading the mounting portion 62' into a mounting 
hole 102 in the cylinder block 9. An inlet port 76' in a valve seat member 
73' communicates with the fluid passage 107 through a fluid passage 108 
while an outlet port 77' is open to a lower portion of the mounting hole 
102 and connected through a fluid passage 109 to a discharge hole 110. 
FIG. 10 shows a control circuit for the differential cylinder actuator 1a 
or 1b described above. The small pressure-receiving area side chamber, 13 
is connected successively through the fluid passages 105, 103 and the 
first solenoid-operated valve 5 disposed therein to a hydraulic power 
supply (not shown). On the other hand, the large pressure-receiving area 
side chamber 14 is connected through the fluid passage 108, 109 and the 
third solenoid-operated valve 7 disposed therein to a tank. Both chambers 
13, 15 are connected together through the fluid passages 106, 107 and the 
second solenoid-operated valve 6 disposed therein. 
The first to third solenoid-operated valves 5-7 receive pulse signals 
issued respectively from driver circuits 203-205 for controlling an inflow 
and an outflow of working fluid in both chamber 13 and 14 of the 
differential cylinder 1a or 1b. The inflow and outflow of working fluid 
are converted into mechanical forces which are finally outputted to an 
external device via the piston rod 15. 
The first solenoid-operated valve 5 is merely controlled in an on-off mode 
as in the case of a two-position directional control valve. When the 
driver circuit 203 issues an exciting current to energize the coil 34, the 
valve 5 is turned on or opened. The valve 5 is kept closed while the coil 
34 is de-energized. 
To the second solenoid-operated valve 6, the driver circuit 204 supplies a 
pulse signal of a high frequency such as 500 Hz such that the pulse 
repetition period of the pulse signal is smaller than the on-off response 
time of the valve element 79. The duty factor (pulse width/pulse 
repetition period) of the pulse signal is regulated to achieve an analog 
proportional control of the open area of the valve 6. Stated more 
specifically, the greater the duty factor, the smaller the valve open 
area. When the duty factor comes to a maximum value, the valve 6 is fully 
closed. Conversely, the valve open area increases with a decrease in duty 
factor. When the duty factor is lowered to a minimum value, the valve 6 is 
fully opened, thereby allowing a maximum flow of the working fluid. 
The driver circuit 204 is composed of a pulse generator 207 capable of 
producing a high frequency pulse signal and including a duty factor 
regulator 208. Operation of the drive circuit 204 is controlled according 
to a suitable program stored in the microcomputer 206. 
The third solenoid-operated valve 7, like the second solenoid-operated 
valve 6 described above, receives a high frequency (e.g. 500 Hz) pulse 
signal delivered from the driver circuit 205. The duty factor of the high 
frequency pulse signal is regulated to achieve an analog proportional 
control of the open area of the valve 7. 
In order to control the output of the differential cylinder 1a or 1b, the 
microcomputer 206 sends control demand signals to the respective driver 
circuits 203, 204, 205 which in turn issue predetermined pulse signals to 
the corresponding solenoid-operated valves 5-7 whereupon the 
solenoid-operated valves 5-7 are operated to vary the inflow and outflow 
of the differential cylinder 1a or 1b, thereby varying the mechanical 
output of the cylinders 1a, 1b. 
An exemplary operation mode of the differential cylinders, 1a, 1b will be 
described below with reference to FIGS. 10 and 15. The first 
solenoid-operated valve 5 is energized to open. At the same time, an 
exciting current is issued to the third solenoid-operated valve 7 to fully 
close the same. The second solenoid-operated valve 6 is kept de-energized 
and hence is fully opened. Thus, a working fluid is allowed to 
concurrently flow into both the small pressure-receiving area side chamber 
13 and the large pressure-receiving area side chamber 15 of the 
differential cylinder 1a, 1b. Due to a pressure difference generated 
between the two chambers 13, 14, the piston 12 is caused to start moving 
rightwards at a point t1 shown in FIG. 15. At a point t2, the driver 
circuit 204 begins to issue a high frequency pulse signal to the second 
solenoid-operated valve 6 for temporarily stopping the rightward movement 
of the piston 12 when the piston 12 arrives at a midpoint S1 of its 
stroke. The pulse signal is applied such that the duty factor of the pulse 
signal is initially small, then gradually increased as the time goes on, 
and finally becomes maximum at the time just before a point t3 shown in 
FIG. 15. This means that the open area of the second solenoid-operated 
valve 6 varies in the analog manner to increase gradually from the maximum 
(the valve full open position) to the minimum (the valve full close 
position) in which an inflow of working fluid to the large pressure 
receiving area side chamber 15 is blocked. The piston 12 is thus stopped 
ar the predetermined position S1. When a predetermined period of time 
extending between points t3 and t4 has lapsed, the duty factor of the 
pulse signal on the second solenoid-operated valve 6 is decreased 
gradually to thereby increase the valve open area from zero to the 
maximum. The piston 10 again moves rightwards. This condition is 
maintained for the period ranging from a point t5 a point t6 at which the 
piston 10 reaches to a position near a final target position S2. In this 
instance, the pulse duty factor is again increased to thereby reduce the 
valve open area proportionally. At a point t7, the valve 6 is fully closed 
whereupon the forward stroke of the piston 12 is completed and the piston 
12 is thus stopped at the final target position S2. 
The movement of the piston 12 of the differential cylinder actuator 1a, 1b 
is controlled by a feed back signal issued from the position sensor 8 such 
that the pulse duty factor is increased as the piston 12 approaches the 
intermediate position S1 and the final target position S2, thereby 
preventing the piston 12 from overrunning beyond the positions S1, S2. 
When the piston 12 is to be returned from the final target position, the 
first solenoid-operated valve 5 is energized to open at a point t9. 
Simultaneously therewith, a pulse signal having a large pulse duty factor 
is supplied to the second solenoid-operated valve 6 at a large duty factor 
to keep the closed condition of the valve 6. Conversely, the third 
solenoid-operated valve 7 receives a pulse signal having a small duty 
factor with the result that the working fluid is expelled from the large 
pressure-receiving area side chamber 14, thereby moving the piston 
leftwards. The return speed of the piston 12 can be controlled by 
regulating the duty factor of the high frequency pulse issued to the third 
solenoid-operated valve 7. This pulse duty factor is set at a maximum 
value when the return stroke of the piston 12 is terminated. 
The fluid-pressure differential cylinders 1a, 1b are joined together as 
shown in FIGS. 11 and 12. In assembly, the cylinder blocks 9 of the 
differential cylinders 1a, 1b are brought into facewise contact with each 
other. Then the connecting bolts 26 are inserted through the connecting 
holes 25, respectively, and thereafter four nuts 27 are threaded tightly 
to the respective bolts 26 to join the differential cylinders 1a, 1b. 
Prior to this assembly, one of the cylinder blocks 9 is finished or 
processed by boring or drilling such that the flow passages 103, 109 
extend transversely across the cylinder block 9 and open at opposite ends 
thereof to front and back faces of the cylinder block 9. Accordingly, the 
flow passages 103, 109 in the thus-bored one cylinder block 9 communicate 
respectively with the flow passages 103, 109 in the other cylinder block 9 
when the two blocks 9 are joined facewise with each other. A plurality of 
seals 111 are provided between contacting surfaces of the cylinder blocks 
9 in the vicinity of the flow passages 103, 109 to prevent the leakage of 
working fluid. 
The differential cylinders 1a, 1b thus joined have only one pair of intake 
and discharge holes 104, 110 and hence can be connected to a piping with 
utmost ease. 
The transmission means 2a, 2b comprise a pair of elongate plate-like 
levers, each lever 2a and, 2b being connected at one of its opposite ends 
to the output connecting rod 17 of the piston rod 15 of the corresponding 
differential cylinder 1a, 1b, the opposite end of the respective levers 
2a, 2b being connected to corresponding levers 102a, 102b of the 
shift-lever actuator device 3. 
The shift-lever actuator device 3, as shown FIGS. 1 and 13, is disposed on 
a transmission (indicated by phantom lines in FIG. 13) and includes a 
downwardly open cover 113 and a drive shaft 116 disposed in the cover 113 
and rotatably supported by a pair of aligned bores 114, 115 defined at 
opposite end portions of the cover 113. The drive shaft 116 fixedly 
supports thereon a gearshift lever 118 engageable with a gearshift fork 
117 of the transmission. A compression coil spring 119 acts between the 
cover 113 and the gearshift lever 118 to urge the drive shaft 116 
leftwards in FIG. 13. 
One end portion of the drive shaft 116 projects outwardly from the cover 
113 and is connected to the lever 120b which in turn is connected to the 
transmission means or lever 2b. The lever 120b takes part in the shift 
operation of the transmission. The end portion also has a circumferential 
groove 121 in which a pin 122 of the lever 120a is engaged. The lever 120a 
takes part in the select operation of the transmission. The lever 120a is 
generally L-shaped as shown in FIG, 1, and is pivoted at its intermediate 
portion to the cover 113 by means of a shaft 123. The L-shaped lever 120a 
is pivotably connected to the transmission lever 2a and is provided with 
the pin 122 held in engagement with the groove 121 in the drive shaft 116. 
With this arrangement, when the lever 120a is driven by the transmission 
lever 2a to turn about the shaft 123, interaction between the pin 122 and 
the groove 121 causes the drive shaft 116 to be displaced longitudinally 
to such an extent that the gearshift lever 118 is movable between 
positions N1, N2 and N3. 
When the lever 120b is moved by the transmission lever 2b, the drive shaft 
116 is driven to rotate about its own axis to thereby select a desired 
gearshift position. 
In operation, the mechanical positional outputs of the respective 
differential cylinders la, 1b are delivered from the piston rods 15 
through the transmission levers 2a, 2b to the shift-lever actuator device 
3 for shifting a gear train to a desired position. 
For example, when starting an automotive vehicle, the gearshift lever 118 
is to be moved from the current position N1 to the first gear position 
indicated by circled numeral 1 in FIG. 14 In this instance, the 
fluid-pressure differential cylinder 1a for actuating the lever 120 for 
achieving select .operation of the transmission is de-activated while the 
lever 120b is turned by the mechanical output of the fluid-pressure 
differential cylinder lb in a direction to move the gearshift lever 118 to 
the first gear position. As the vehicle travelling speed increases, the 
second gear position indicated by circled numeral 2 is to be selected. At 
this time, the shift lever 118 is moved from the first gear position 
through the position N1 to the second gear position by the output of the 
differential cylinder 1b. A further increase in vehicle travelling speed 
makes it necessary to select the third gear position indicated by circled 
numeral 3 in which instance the gearshift lever 118 is returned to the 
position N1 by the output of the differential cylinder 1b, then the 
differential cylinder la is activated to move the gearshift lever 118 to a 
position N2, and thereafter the differential cylinder 1b is activated 
again to displace the gearshift lever 118 to the third gear position. Thus 
the gearshift lever 118 is placed accurately and smoothly in a desired one 
of the gear positions under the control of the differential cylinders 1a, 
1b. 
Obviously, many modifications and variations of the present invention are 
possible in the light of the above teaching. It is therefore to be 
understood that within the scope of the appended claims, the invention may 
be practiced otherwise than as specifically described.