Press drive clutch with brake

A press drive mechanism is disclosed having relatively rotatable output shaft and flywheel components which are independently rotatably supported at their opposite ends by fixed support members. The flywheel is mounted on a sleeve which is concentric with the output shaft and located between the opposite ends of the shaft. Clutch discs are cooperatively supported by the sleeve and output shaft, and brake discs are cooperatively supported by the output shaft and one of the fixed support members. The brake and clutch are alternately engaged and disengaged by means of a pneumatic piston and cylinder assembly concentric with the output shaft inwardly adjacent the other of the fixed support members.

This invention relates to the art of transmissions and, more particularly, 
to a brake-clutch-flywheel mechanism for use with heavy machinery such as 
metalworking presses. 
Liquid cooled and lubricated brake-clutch-flywheel drive mechanisms have 
been provided heretofore for use with presses. Such mechanisms generally 
include an output shaft, a flywheel driven by a motor, a clutch assembly 
for selectively connecting and disconnecting the flywheel and output 
shaft, and a brake assembly for braking rotation of the output shaft when 
the clutch is actuated to disengage the flywheel and output shaft. A 
suitable liquid, such as oil, is circulated through the interior of the 
drive unit to lubricate and cool the operating parts thereof, including 
the brake and clutch disc components, during operation of the drive 
mechanism. 
In conjunction with drive mechanisms of the foregoing character, it is 
desirable that they can be manufactured as a unit readily useable either 
with a new press or as a replacement for the drive unit of existing 
presses. In conjunction with both these potential uses it is desirable 
that the drive mechanism lend versatility with regard to mounting thereof, 
that the unit be as compact as possible both axially and radially with 
respect to the output shaft, and that the component parts be structurally 
interrelated to enhance the use of high-production techniques in 
manufacturing and, at the same time, to optimize operating characteristics 
in connection with a variety of press designs. Additionally, it is 
desirable that the component parts be structurally interrelated so as to 
minimize unbalanced loading and the imposition of undesirable load forces, 
and to avoid the potential danger of rotation of the output shaft through 
the flywheel when the clutch is disengaged. 
Certain of the foregoing desirable features have been obtained with 
brake-clutch-flywheel mechanisms heretofore provided. However, in 
connection with such previous efforts certain desirable characteristics 
have been sacrificed in favor of others. For example, in an effort to 
obtain radial compactness previous efforts have provided for at least one 
end of the flywheel to be supported for rotation by a bearing assembly 
interposed between the flywheel and output shaft. Such an arrangement 
requires extension of the output shaft beyond the flywheel for rotational 
support, whereby axial compactness is sacrificed and, more importantly, 
the imposition of a bearing between the flywheel and output shaft is a 
potential danger in that freezing of the bearing can cause undesired 
rotation of the output shaft through the flywheel. Efforts to avoid the 
latter situation have resulted in arrangements in which the flywheel is 
disposed at one end of the housing and has a portion extending axially 
inwardly of the housing such that the flywheel is supported for rotation 
relative to the housing by a bearing assembly therebetween. This lends to 
axial compactness and eliminates the potential rotation of the output 
shaft by the flywheel. At the same time, however, radial compactness is 
sacrificed by the necessary expansion of the housing to accommodate the 
flywheel. Additionally, the end of the output shaft at the one end of the 
housing has no bearing support with respect to the housing, whereby 
unbalanced loading and undesirable load forces are potential problems in 
connection with operation and maintenance of the drive mechanism. 
Moreover, such a drive mechanism can be mounted at one end only, thus 
reducing versatility with regard to use thereof and requiring larger and 
stronger mounting supports and housing components to assure adequate 
support for the drive mechanism when mounted. 
The brake-clutch-flywheel drive mechanism according to the present 
invention advantageously provides both axial and radial compactness, 
balanced rotational support for the output shaft and flywheel, and 
rotational support for the flywheel independent of the rotational support 
for the output shaft. Additionally, the drive mechanism is adapted to be 
supported at its opposite ends to facilitate installation thereof and to 
provide balanced loading with respect to the support components and the 
components of the drive mechanism. 
More particularly in accordance with the present invention, these 
advantages are achieved by supporting the opposite ends of both the 
flywheel and output shaft for independent rotation relative to fixed 
support members. The flywheel surrounds the shaft in concentric 
relationship therewith and is positioned between the opposite ends of the 
shaft. The brake and clutch units and the actuating mechanism therefor are 
located radially between the flywheel and shaft and axially between the 
support members. This arrangement optimizes both radial and axial 
compactness of the drive mechanism while affording balanced rotational 
support for both the output shaft and the flywheel and independent 
rotational support for the shaft and flywheel, thus to eliminate the 
possibility of the shaft being driven by the flywheel due to freezing of 
the flywheel bearings. Each of the fixed support members is suitably 
attached to components of the press frame, whereby the forces resulting 
from the load of the drive mechanism are equally distributed to the press 
frame and are not imposed on components of the drive mechanism. 
Accordingly, it is an outstanding object of the present invention to 
provide a brake-clutch-flywheel press drive mechanism having an improved 
flywheel and output shaft rotational support arrangement. 
Another object is the provision of a drive mechanism of the foregoing 
character by which balanced rotational support for the output shaft and 
flywheel is achieved. 
Yet another object is the provision of a drive mechanism of the foregoing 
character in which the flywheel and output shaft are independently 
supported for rotation relative to one another. 
A further object is the provision of a drive mechanism of the foregoing 
character which enables optimizing radial and axial compactness of the 
mechanism and obtaining balanced load and force distribution with respect 
to the component parts of the drive mechanism. 
Still a further object is the provision of a drive mechanism of the 
foregoing character readily adapted to be used as an original or 
replacement unit with a variety of press designs and having a support 
structure which facilitates versatility in mounting the mechanism on a 
given press. 
Yet a further object is the provision of a drive mechanism of the foregoing 
character which is structurally simple, economical to produce and operate, 
highly efficient in operation, and minimizes wear of component parts and 
maintenance requirements and costs.

Referring now in greater detail to the drawings wherein the showings are 
for the purpose of illustrating a preferred embodiment of the present 
invention only and not for the purpose of limiting the invention, a 
metalworking press is illustrated in FIG. 1 of the drawing which includes 
a frame supporting a fixed work supporting platen 10 and a reciprocable 
tool supporting platen 12. The tool supporting platen is adapted to be 
reciprocated in a well known manner by means of a rotatable crank 14 
having a shaft 16 which is supported for rotation by the press frame and 
is provided on one of its opposite ends with a drive gear 18. Accordingly, 
rotation of gear 18 rotates crank 14 to impart reciprcoating motion to 
tool support platen 12. 
Gear 18 is adapted to be rotated by a pinion gear 20 which is coupled to 
the output shaft of a brake-clutch-flywheel drive mechanism 22 of the 
present invention. As described more fully hereinafter, drive mechanism 22 
includes a pair of fixed support members 24 and 26 by which the drive 
mechanism is mounted on the press such as by bolting members 24 and 26 to 
mounting supports 28 and 30, respectively, which may be part of or 
attached to the press frame. Further, drive mechanism 22 includes a 
flywheel 32 rotatably mounted on support plates 24 and 26, and flywheel 32 
is adapted to be driven by a suitable motor such as electric motor 34 
through a drive belt 36. 
The general arrangement of the components of drive mechanism 22 is 
illustrated in FIGS. 2-4 of the drawing. As will be seen from these 
Figures, fixed support members 24 and 26 are parallel and spaced apart to 
define opposite ends of the drive mechanism and have apertures 
therethrough to receive and rotatably support an output shaft 38 which 
carries gear 20 on one end thereof. More particularly, support member 24 
includes a hub 40 and a radially outwardly extending plate portion 42 by 
which the support member is attached to mounting members 28 such as by 
means of a plurality of studs 44. Hub 40 includes a portion 40a extending 
axially inwardly of plate portion 42 and a portion 40b extending axially 
outwardly of the plate portion. A bearing assembly 46 is interposed 
between hub 40 and output shaft 38 to support the corresponding end of the 
output shaft for rotation. Similarly, support member 26 at the opposite 
end of the drive mechanism includes a hub 48 and a radially outwardly 
extending plate portion 50 by which the support member is attached to 
mounting members 30 such as by means of a plurality of studs 52. Hub 48 
includes an axially inwardly extending portion 48a and an axially 
outwardly extending portion 48b, and a bearing assembly 54 is interposed 
between hub 48 and output shaft 38 to rotatably support the corresponding 
end of the shaft. 
Flywheel 32 is disposed between end support members 24 and 26 and is 
supported thereby for rotation relative thereto and independent of the 
rotational support of output shaft 38. More particularly, flywheel 32 is 
mounted on a sleeve assembly extending between support members 24 and 26 
and including a sleeve member 56 coaxial with output shaft 38 and collars 
58 and 60 attached to the axially opposite ends of sleeve 56. The outer 
surface of sleeve 56 is stepped to provide a shoulder 62 and the inner 
surface of flywheel 32 is stepped to provide a shoulder 63 which engages 
shoulder 62 to axially position flywheel 32 on sleeve 56. The end of 
flywheel 32 adjacent collar 58 is provided with a peripheral shoulder 64 
engaged by collar 58, and a plurality of studs 66 extend through collar 58 
and into sleeve 56 to interconnect the collar and sleeve and to maintain 
flywheel 32 against sleeve shoulder 62. A plurality of studs 68 extend 
through collar 60 and into sleeve 56 to interconnect the latter collar and 
sleeve, and relative rotation between flywheel 32 and the sleeve assembly 
is prevented by means of a key and keyway arrangement 70 between the 
flywheel and sleeve 56. 
Collar 58 axially overlaps and surrounds hub portion 40a of end support 
member 24, and collar 60 axially overlaps and surrounds hub portion 48a of 
support member 26. The sleeve assembly and flywheel are supported for 
rotation relative to support members 24 and 26 by means of bearing 
assemblies 72 and 74 between the collars and corresponding hub portion. 
Thus, it will be appreciated that flywheel 32 and output shaft 38 are each 
supported adjacent their opposite ends for rotation relative to support 
members 24 and 26 and for rotation relative to and independent of one 
another. 
Drive mechanism 22 further includes a brake assembly 76 and a clutch 
assembly 78 in the radial space between sleeve member 56 and output shaft 
38. Brake assembly 76 includes a plurality of interposed brake discs 80 
and 82, and clutch assembly 78 includes a plurality of interposed clutch 
discs 84 and 86. The brake and clutch discs are positioned on axially 
opposite sides of an abutment ring 88 which is axially and 
circumferentially fixed on a radially enlarged portion 38a of output shaft 
38. Abutment ring 88 has axially opposite ends 88a and 88b respectively 
defining brake and clutch disc abutment surfaces. 
Brake discs 80 are supported against rotation relative to end support 
member 24 and for axial displacement relative thereto by means of a brake 
disc supporting sleeve 90 which is attached to end support member 24 by 
means of a plurality of studs 92 extending through hub 40. The outer 
peripheries of brake discs 80 and the inner periphery of the axially inner 
end of sleeve 90 are cooperatively interengaged such as by a splined 
interconnection 94. In a well known manner, splined interconnection 94 
provides for discs 80 to be fixed against rotation and to be axially 
slidable relative to sleeve 90. The inner peripheries of brake discs 82 
and the outer periphery of the underlying shaft portion 38a are 
cooperatively interengaged such as by a splined interconnection 96 which 
provides for brake discs 82 to rotate with output shaft 38 and to be 
axially slidable relative thereto. 
The inner surface of sleeve 56 is provided with a circumferentially 
extending radially inwardly projecting flange 98, and the outer 
peripheries of clutch discs 84 and the inner periphery of flange 98 are 
cooperatively interengaged through a splined interconnection 100. It will 
be appreciated that this splined interconnection provides for clutch discs 
84 to rotate with sleeve 56 and to be axially slidable relative thereto. 
The inner peripheries of clutch discs 86 and the outer periphery of the 
underlying shaft portion 38a are cooperatively interengaged by a splined 
interconnection 102 which provides for clutch discs 86 to rotate with 
output shafts 38 and to be axially slidable relative thereto. 
Brake assembly 76 further includes an annular brake pressure member 104 
which is rotatable with output shaft 38 and axially reciprocable relative 
thereto in the direction toward and away from end 88a of abutment ring 88. 
In the embodiment shown, the inner periphery of presser member 104 has a 
splined interconnection with the underlying shaft portion 38a and is 
supported for axial reciprocation relative to the output shaft by a 
radially inwardly extending ring portion 106 which is integral with 
presser member 104 and slidably surrounds the output shaft. Clutch 
assembly 78 further includes an annular clutch presser member 108 which is 
rotatable with the output shaft and axially slidable relative thereto in a 
direction toward and away from end 88b of abutment ring 88. In the 
embodiment shown, the inner periphery of presser member 108 has a splined 
interconnection with the underlying shaft portion 38a and is integrally 
connected with a component of the actuating assembly, to be described 
hereinafter, so as to be axially reciprocable relative to the output 
shaft. 
The brake and clutch assemblies are adapted to be alternately actuated by 
displacing the brake and clutch discs toward the corresponding end of 
abutment ring 88. In the embodiment shown, such alternate displacement is 
achieved by an actuating mechanism which provides for presser members 104 
and 108 to be reciprocated together in axially opposite directions. The 
actuating mechanism includes a pneumatic piston and cylinder unit 110 
including a radially extending annular piston member 112 attached to 
output shaft 38 adjacent end support member 26 for rotation with the 
output shaft and against axial displacement relative thereto. Piston and 
cylinder unit 110 further includes a cylinder member having a radially 
outwardly extending wall 114 surrounding and slidably engaging output 
shaft 38 and an axially outwardly extending peripheral wall 116 slidably 
receiving the outer periphery of piston member 12. The space between the 
piston and cylinder members defines a chamber 118, and the corresponding 
end of output shaft 38 is provided with an axial passageway 120 and radial 
passageways 122 for directing air under pressure from a suitable source, 
not shown, into chamber 118. 
The brake and clutch actuating mechanism further includes a plurality of 
rigid actuator rods 124 extending through corresponding openings 125 in 
portion 38a of the output shaft and interconnecting presser members 104 
and 108 for reciprocation together in axially opposite directions relative 
to the output shaft. For this purpose, one end of each rod 124 is 
threadedly engaged with wall 114 of the cylinder member of piston and 
cylinder unit 110, and the other end of each rod is threaded to receive a 
nut 126 by which ring 106 is axially clamped against a shoulder on the 
corresponding end of the rod. An axial portion 127 of each of the rod 
openings 125 extending through shaft portion 38a is radially enlarged to 
receive a corresponding compression spring 128. The axially inner end of 
spring 128 abuts against a shoulder 129 at the inner end of enlarged 
portion 127, and the outer end of the spring abuts against cylinder wall 
114. Springs 128 bias the cylinder member toward piston 112 and thus bias 
presser member 104 toward end 88a of abutment ring 88 to engage the brake. 
At the same time, springs 128 bias presser member 108 in the direction 
away from end 88b of the abutment ring to release the clutch. By 
introducing air under pressure into chamber 118, the cylinder member of 
piston and cylinder unit 110 is displaced away from piston 112 and against 
the bias of springs 128. This movement of the cylinder displaces presser 
member 108 toward end 88b of abutment ring 88 to engage the clutch and 
displaces presser member 104 in the direction away from end 88a of the 
abutment ring to release the brake. The rigid interconnection of the 
presser members for movement together advantageously prevents an overlap 
in the braking and clutching functions. 
It is to be noted that radially inwardly extending flange 98 of sleeve 56 
and radially inwardly extending collar 60 on the end of the sleeve provide 
a radial recess with the inner surface of the sleeve which accommodates 
the outer periphery of piston and cylinder unit 110. This advantageously 
promotes radial and axial compactness of the drive mechanism without 
sacrificing a desirable effective surface area for air pressure actuation 
of the piston and cylinder unit. 
Preferably, the component parts of the drive mechanism are lubricated and 
cooled by continuous circulation of a liquid such as oil therethrough. For 
this purpose, the end of output shaft 38 adjacent end support member 24 is 
provided with an axial passageway 130 adapted to be connected to a 
suitable source of oil, not illustrated, and the shaft is provided with 
branch passageways 132, 134 and 136 by which oil is distributed to the 
interior of the drive mechanism through the brake and clutch disc 
components. End support members 24 and 26 are provided with corresponding 
oil accumulators 138 surrounding the corresponding one of the sleeves 58 
and 60 and having radially inner peripheries slidably and sealingly 
engaging the collar. Further, each collar is provided with an oiled 
diverter ring 140 to channel accumulated oil into sump areas 142 of the 
accumulators. Oil received in accumulators 138 is discharged therefrom 
through outlet passages 144 and, preferably, to an external heat transfer 
unit for cooling before returning to inlet passage 130. 
From the foregoing description of the embodiment illustrated in the 
drawings, it will be appreciated that operation of the drive mechanism is 
as follows. When the component parts are in the position illustrated in 
FIG. 2, springs 128 bias presser members 104 and 108 to the right, whereby 
brake discs 80 and 82 are pressed into engagement with end 88a of abutment 
ring 88. This engages the brake to prevent rotation of output shaft 38, 
and the position of presser member 108 releases the clutch discs so that 
flywheel 32 can rotate relative to the output shaft. By introducing air 
under pressure into chamber 118 of piston and cylinder unit 110, the 
cylinder member is displaced to the left in FIG. 2 against the bias of 
springs 128 to displace presser member 108 toward end 88b of abutment ring 
88 and to displace presser member 104 in the direction away from the 
abutment ring. This engages the clutch and disengages the brake, whereby 
rotation of flywheel 32 rotates output shaft 38. Upon release of air under 
pressure from chamber 118, springs 128 bias the cylinder and thus the 
presser members to the positions illustrated in FIG. 2 to reengage the 
brake and release the clutch. 
While considerable emphasis has been placed herein on the specific 
structure of and the specific structural interrelationship between 
component parts of the drive mechanism, it will be readily appreciated 
that many changes can be made in the structures and relationships shown 
without departing from the principles of the present invention. For 
example, brake and clutch actuating arrangements other than the piston and 
cylinder arrangement shown can be employed and, in connection with a 
piston and cylinder actuating arrangement, the cylinder component can be 
fixed with respect to the output shaft and the piston component axially 
displaceable relative thereto. Further, while the clutch presser member is 
disclosed as being integral with the cylinder member of the piston and 
cylinder unit it will be appreciated that these components can be 
structurally separate and suitably interconnected for displacement of the 
cylinder to impart like displacement to the clutch presser member. Still 
further, other sleeve and end support structures can be devised for 
supporting the flywheel and output for rotation. It is only important in 
accordance with the present invention that opposite ends of the flywheel 
be supported for rotation relative to fixed support members so that the 
rotational support of the flywheel is balanced and that the flywheel be 
supported for rotation independent of the rotational support for the 
output shaft. 
Since many embodiments of the present invention can be made and since many 
changes can be made in the embodiment herein illustrated and described, it 
is to be distinctly understood that the foregoing descriptive matter is to 
be interpreted merely as illustrative of the present invention and not as 
a limitation.