192 clutches and power-stop control – Clutch and brake – Sliding operation
Reexamination Certificate
2002-04-18
2003-12-30
Lorence, Richard M. (Department: 3681)
192 clutches and power-stop control
Clutch and brake
Sliding operation
C192S085060
Reexamination Certificate
active
06668992
ABSTRACT:
Japanese Patent Application No. 2001-131809, filed on Apr. 27, 2001, is hereby incorporated by reference in its entirety.
BACKGROUND OF THE INVENTION
The present invention relates to a clutch-brake system and a press machine using the same.
For example, a press machine
1
P shown in
FIG. 2
is formed by a frame
10
P on which a drive shaft
20
P and flywheel
25
P are rotatably mounted but not movable in an axis (Z) direction (or longitudinal direction) of the drive shaft
20
P. Reference numeral
26
P denotes a cover which houses a clutch device integrally fixed to the flywheel
25
P.
A clutch device
30
P constructed according to the prior art includes a clutch disc
41
P, a clutch friction plate
31
P, an air intake port
48
P and a spring
46
P. The clutch device
30
P is mounted on the drive shaft
20
P at one end (right as viewed in
FIG. 2
) for driving a slider (not shown).
The clutch disc
41
P includes: an inner stationary disc
41
IP mounted on the flywheel
25
P to be synchronously rotatable and not to be movable in the Z direction, when the flywheel is rotatably supported on the drive shaft
20
P through a bearing
14
P; and an outer movable disc
41
OP mounted on the flywheel
25
P to be synchronously rotatable and to be movable in the axial (Z) direction along a guide pin
45
P.
The clutch friction plate
31
P is mounted on the drive shaft
20
P at one end (right end) to be synchronously rotatable with the drive shaft
20
P and to be movable through a spline structure
32
or the like in the Z direction. More particularly, the clutch friction plate
31
P has a rotatable holding portion
31
R mounted on the drive shaft
20
P through an anchoring device
15
P for synchronized rotation and an anchor portion
31
K for screwedly anchoring the clutch friction plate
31
P, these portions being movable relative to each other through the spline structure
32
or the like in the Z direction. Structures of hydraulic lubrication and alignment control incorporated into the spline structure
32
or the like are omitted from FIG.
2
.
The outer disc
41
OP is biased rightward as viewed in
FIG. 2
by the spring
46
P mounted around a guide pin
45
P in the normal (or clutch release) state, in which state the outer disc
41
OP is in its clutch release (OFF) state and spaced apart from the clutch friction plate
31
P. Reference numeral
43
P denotes linings.
When air is supplied from a rotary joint
49
P into a cylinder chamber
26
SP through the air intake port
48
P, a piston
41
DOP is moved leftward as viewed in
FIG. 2
against the bias of the spring
46
P. Thus, the outer movable disc
41
OP integrally mounted on the piston
41
DOP is moved leftward to urge the clutch friction plate
31
P against the inner stationary disc
41
IP while moving the same toward the inner disc
41
IP. As a result, the clutch device will be switched to the clutch engagement (ON) state.
More particularly, the clutch device
30
P can selectively be switched to either of the clutch engagement state that can transmit the rotational energy of the flywheel
25
P (
26
P) to the drive shaft
20
P or the clutch release state that cannot transmit the rotational energy to the drive shaft
20
P, in response to the air supply or exhaust as in FIG.
2
.
A brake device
50
P constructed according to the prior art includes a brake disc
61
P, a brake friction plate
51
P, an air intake port
68
P and a spring
66
P and is mounted on the drive shaft
20
P at the other end (leftward end as viewed in FIG.
2
).
The brake disc
61
P includes an inner stationary disc
61
IP mounted on a frame
10
P (or bracket
19
P) not to be movable in the Z direction and an outer movable disc
61
OP mounted on the frame
10
P (or bracket
19
P) to be movable in the axis direction along a guide pin
67
. Reference numeral
63
P denotes linings.
The brake friction plate
51
P is mounted on the drive shaft
20
P at the other (leftward) end to be synchronously rotatable with the drive shaft
20
P and to be movable through the spline structure or the like in the Z direction. More particularly, the brake friction plate
51
P includes a rotatable rotation holding portion
51
R and an anchoring portion
51
K for screwedly securing the brake friction plate
51
P, these portions being movable relative to each other through the spline structure
52
or the like in the Z direction.
The alignment in the rotation holding portion
51
R of the brake friction plate
51
P can be controlled by using the outer peripheries of a control ring member
18
and lid member
19
F. An O-ring
53
is provided to seal for lubricant. In other words, the brake device
50
P has the lubricating structure (
53
and so on) and the alignment control structure (
18
,
19
F and so on) associated with the spline structure
52
or the like.
When the compressed air within the cylinder chamber
61
SP is exhausted through the air intake port
68
P in the brake release state, the outer movable disc
61
OP is moved rightward as viewed in
FIG. 2
under the bias of the spring
66
P mounted around a guide pin
65
P to urge the brake friction plate
51
P against the inner stationary disc
61
IP while moving the same toward the inner disc
61
IP. Thus, the brake device
50
P can be switched to its brake engagement (ON) state.
On the contrary, if air is supplied into the cylinder chamber
61
SP through the air intake port
68
P, a piston
61
PP in the interior of the cylinder chamber
61
SP is moved leftward as viewed in
FIG. 2
against the bias of the spring
66
P to push a bolt member
62
fastened on the outer disc
61
OP. Thus, the outer disc
61
OP is moved leftward to separate it from the brake friction plate
51
P. This state is the brake release (OFF) state.
In other words, the brake device
50
P can selectively be switched to either of the brake release state that releases the braking force to permit the rotation in the drive shaft
20
P or the brake engagement state that can apply the braking force to the rotating drive shaft
20
P, in response to the air supply or exhaust as in FIG.
2
.
A clutch-brake system is provided by combining the clutch device
30
P with the brake device
50
P. The clutch-brake system can be switched to the clutch engagement and brake release state in response to the air supply and to the clutch release and brake engagement state in response to the air exhaust.
A press machine including such a clutch-brake system has been required to more improve in speed and accuracy, as in the other industrial machines and so on. In the viewpoint of versatility, differentiation and so on, it is strongly required that the press machine is improved in response on start or stop or both start and stop.
However, the prior art clutch device
30
P is designed to provide the braking force by urging the movable clutch disc
41
OP against the stationary clutch disc
41
IP while moving the clutch friction plate
31
P on the drive shaft
20
P in the axial direction. Therefore, the clutch device
30
P is of complicated, large-sized and weighted structure, leading to increase of the manufacturing cost. The clutch disc
41
OP and clutch friction plate
31
P will easily be degraded in rapid and smooth movement. Since the clutch device
30
P has an increased inertial mass, it is difficult that the clutch device
30
P shows quick response. Furthermore, the mechanical backlash and play will reduce the accuracy, provide a source of noise and shorten the mechanical life. This is true of the brake device
50
P.
And yet, the clutch and brake devices
30
P,
50
P have many mechanical setting locations since they are of complicated structure and require mechanical delicate adjustments. Thus, a disagreement may easily be created between the responsibilities of the clutch and brake devices
30
P,
50
P.
If the starting point of a pressing process is to be strictly managed, the degradation of the clutch action in the clutch device
30
P will also degrade the accuracy in product. To improve the accurate work in the press machine, the clutch action must be more improved in speed.
On the
Shiga Masakatsu
Shimizu Noriyuki
Taniguchi Naonori
Aida Engineering Ltd.
Lorence Richard M.
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