Note: Descriptions are shown in the official language in which they were submitted.
DRIVE ASSEMBLY ~OR POWER SHOVELS AND THE LIKE
Technical Field
This invention relates to a drive assembly and
more particularly to a drive assembly mountable on a machine
for performing a work function. This invention specifically
contemplates a drive assembly for a power shovel for perform-
ing a work function such as crowding, hoisting, swinging and
propelling.
Background of the Invention
Large, heavy-duty mining shovels of the type dis-
closed in U.S. Patents Nos. 3,50~,034 and 3,648,863 general
ly are provided with crowd, hoist, swing and propel systems
which are operated to produce the various work functions of
the machine. Each of such systems basically includes a
drive assembly mounted on the machine, operatively connected
to a working component of the machine. In the case of the
crowd system of a rope type, the drive assembly is operative-
ly connected to a rope drum for paying out and taking in a
;, crowd rope. In a hoist system of the rope type, the drive
assembly is operatively connected to a hoist drum for paying
out and taking in hoist line. In the case of a swing system,
the drive assembly usually is mounted on an upper rotatable
frame and i9 provided with a depending shaft having a pinion
' drivingly engaged with a ring gear mounted on a lower frame
of the machine. In a typical propel system of the crawler
type, the drive assembly is operatively connected to a drive
sprocket journaled in a crawler frame which is drivingly con-
nected to a crawler tread.
In each application, the drive assembly for a par-
~- 30 ticular work function is mounted on the machine and generally
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consists of a drive means such as an electric or hydraulic
motor, a driven means such as a drum, rack, rotatable frame
or a drive sprocket and a gear train drivingly interconnecting
the drive means and the driven means for effecting torque
transmission and speed reduction.
During the normal operation of a large, heavy-duty
mining shovel, as when the machine is crowding or retracting
its dipper, hoisting or lowering its dipper, swinging its
upper frame or propelling the entire machine, the machine is
subjected to a multitude of loads in tension, compression,
bending and torsion, in a variety of magnitudes, which are
transmitted to the upper and lower frames of the machine.
Such loads result in deflections of the upper and lower
frames of the machine on which the drive assemblies for the
crowd, hoist, swing and propulsion systems are mounted. In-
evitably, such frame deflections are imposed on the drive and
driven components of such assemblies which are translated to
misalignments of the gear trains thereof. Such misalignments
produce non-uniform bearing contact of the gear teeth which
'~ 20 results in inefficient torque transmission, undue tooth wear
and often tooth breakage. It thus has been found to be
desirable to provide drive assemblies mounted on machines of
the type described which are capable of withstanding the
adverse effects of loads being imposed on the machines during
normal operating conditions.
Summary of the Invention
Accordingly, it is the principal object of the
present invention to provide an improved drive assembly for
a system mounted on a machine for performing a work function.
Another object of the present invention is to pro-
vide an improved drive assembly for a system mounted on a
machine for performing a work function, in which the machine
is subjected to various applied loads during normal opera-
ting conditions.
A further object of the present invention is to
provide an improved drive assembly for a system mounted on a
machine for performing a work function which is capable of
counteracting the adverse effects of loads applied to the
machine during normal operating conditions.
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The above objects are met by the present invention
which broadly provides in an earth working machine having a
frame subject to loads resulting in frame deflections, an
assembly for effecting a work function on the machine comprising
a drive unit supported on the frame, a driven unit supported on
the frame, a gear train set, flexible coupling means drivingly
interconnecting the drive unit and the gear train set and
flexible coupling means drivingly interconnecting the gear train
set and the driven unit whereby the gear train set is isolated
from the frame deflections.
Other objects and features of the present invention
will become more apparent to those persons having ordinary
skill in the art to which the present invention pertains, from
the following description taken in conjunction with the
accompanying drawings, wherein:
Description of the Drawings
Figure 1 is a side elevational view of a power
shovel incorporating several embodiments of the present invention;
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Figure 2 is an enlarged top plan view of an upper
cleck of the machine show in Figure 1, illustrating the
arran~ement of various drive assemblies thereon;
Figure 3 is an enlarged, rear elevational view of
5 the crowd drive assembly shown in Figure l;
Figure 4 is an enlarged cross-sectional view taken
along line 4-4 in Figure l;
Figure 5 is a rear elevational view of another
crowd drive assembly embodying the invention, shown partially
in section;
Figure 6 is a rear elevational view of a further
crowd drive assembly embodying the invention, shown partially
in section;
Figure 7 is a rear elevational view of a still
further crowd drive assembly embodying the present invention,
shown partially in section;
Figure 8 is an enlarged cross-sectional view taken
along line 8-8 in Figure l;
Figure 9 is a rear elevational view of another
;~ 20 hoist drive assembly embodying the present invention, shown
partially in section;
~: Figure 10 is an enlarged cross-sectional view taken
along line 10-10 in Figure 2; and
Figure 11 is an enlarged cross-sectional view taken
along line 11-11 in Figure 1.
Detailed Description
-
Referring to Figures 1 and 2 of the drawings, there
is illustrated a power shovel utilizing several embodiments
of the present invention which generally includes a main
support unit 20 mounted on a pair of crawler units 21, a
front end assembly 22 mounted on the front end of the main
support unit, a crowd system 23 mounted on the main support
unit and operatively connected to the front end assembly, a
hoist system 24 mounted on the main support unit and opera-
tively connected to the front end assembly, a swing system 25
; mounted on the main support unit, crawler drive assemblies 26
and 27 mounted on the rear end of the main support unit and
the rear ends of crawler units 21, and appropriate power
supplies and controls mounted on the main support unit for
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operating such various systems and assemblies.
The crawler units are substantially similar in con-
struction and operation. Each of such units includes a
crawler frame 28, a drive sprocket 29 mounted on the rear end
thereof, a driven sprocket 30 mounted on the front end there-
of, a crawler tread 3~, a plurality of support rollers 32
mounted on the lower side of the crawler frame and supported
on the lower flight of the tread, and a plurality of guide
rollers 33 mounted on the upper side of the crawler frame and
supporting the upper flight of the tread. Each of the crawler
units functions in the conventional manner to propel the
machine.
As best seen in Figures 1, 2 and 10, main support
unit 20 generally consists of a lower frame 34, a live roller
circle 35 and an upper frame 36. Lower frame 34 is supported
on crawler frames 28 of the crawler units and is provided
with a ring gear 37. Live roller circle 35 consists of a
lower circular rail 38 mounted on the lower frame, an upper
circular rail 39 mounted on the underside of upper frame 36
and a pluality of rollers 40. The rollers are supported on
shafts carried by a cage structure 41. As best illustrated
in Figure 10, rollers 40 are supported on lower rail 38 and
upper rail 39 is supported on the rollers so that the upper
frame can be rotated or swung relative to the lower frame
~ 25 about the vertical center line of the live roller circle.
; The upper frame also is provided with a pair of mounting
brackets 42 and 43 on the front end thereof for mounting
the front end assembly to the front end of the upper frame.
Front end assembly 22 generally includes a stiffleg
- 30 44, a hoist frame 45, a dipper handle 46, a dipper 47 and a
hoist link 48. Stiffleg 44 consists of a structural member
pivotally connected at its lower end to mounting lugs 42 and
43 by means of a pair of foot pins, and is provided at its
` upper end with a head shaft 49. Hoist frame 45 is pivotally
mounted on head shaft 49. Handle 19 consists of a suitable
structural member and is provided with upper and lower bi-
furcated ends. The upper bifurcated end is connected to the
hoist frame by means of a pair of connecting pins. The lower
bifurcated end of the stiffleg is pivotally connected to the
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upper rear end of dipper 47 by means of a pair of axially
aligned pins 50. The forwardly disposed head section of the
hoist frame and the upper end of dipper 47 are connected by
hoist link 48. The upper end of the hoist link is bifurcated
and connected to the head section of the hoist frame by means
of a connecting pin 51. The lower bifurcated end of the
hoist link is connected to the dipper by means of a pair of
axially aligned pins 52. It thus will be seen that hoist
frame 45, handle 46, dipper 47 and hoist link 48 are pivotal-
ly connected together to provide a four-bar linkage with the
link comprising the hoist frame being pivotally connected to
the upper end of the stiffleg by means of head shaft 49.
To provide a substantially flat pass of the dipper
when it is crowded into a bank of material being excavated or
loaded, there is provided on the front end assembly a pitch
control system 53, the construction and operation of which
is fully described in U.S. Patents Nos. 3,501,034 and
3,648,863. In addition, the front end assembly is provided
with a pitch stop assembly 54, the construction and operation
of which is fully described in U.S. Patent No. 4,085,854.
Crowd syst0m 23 consists of a gantry 55 mounted on
upper frame 36 of the machine, a crowd drive assembly 56
mounted on the upper end of the gantry, above housing
structure 57 supported on the upper frame, a mast 58 provided
with sheaves 59, a crowd link 60 and a crowd rope 61. Mast
58 consists of a structural member pivotally connected at its
lower end to a pair of brackets 62 and 63 rigidly secured to
the upper frame 36, forwardly of the vertical center line of
live roller circle 35. The upper end of mast 58 is provided
with a shaft 64 on whic~ sheaves 59 are mounted. Crowd link
~` 60 is pivotally connected at the ends thereof to hoist frame
45 and mounting shaft 64 at the upper end of the mast so that
pivotal motion of mast 58 in a vertical plane will be trans-
mitted by crowd link 60 to the front end assembly of the
machine. Crowd rope 61 is operatively connected to crowd
drive assembly 56 and extendsforwardly and around sheaves
59, and rearwardly where it is connected to a bail 65 mounted
on the head portion of the gantry.
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Referring to Figures 3 and 4, crowd drive assembly
56 consists of a rope drum 66 and a drive unit 67. The rope
drum is trunnionmounted in a set of bearings 67 and 68
mounted in the upper end of gantry 55. It is provided with
a pair of transversely spaced bull gears 69 and 70 and an
intermediate drum portion 71 provided with suitable guide
grooves for winding crowd rope 61 thereon. Drum portion 71
is disposed substantially in longitudinal alignment with
; mast 58. Drive unit 67 generally consists of a gear case 72,
a pinion shaft 73, a motor 74, a drive shaft 75 and planetary
gear sets 76 and 77. Gear case 72 is formed with an annular
portion 78 which is journaled in a bearing 79 mounted in a
bearing block 80 supported in an opening of gantry 55, for
mounting the gear case on one side of the gantry.
15The axial opening of annular portion 78 is provided
with a pair of bearings 81 and 82 for supporting one end of
pinion shaft 73. Aligned axially with bearings 81 and 82 is
a bearing 83 mounted in a bearing block 84 provided in an i-
opening in gantry 55, for supporting the other end of the
pinion shaft.
Pinion shaft 73 is provided with an axially dis-
posed passageway and a pair of integrally formed pinions 85
and 86 which mesh with bull gears 69 and 70 of crowd drum 66
when the drum is trunnion mounted on bearings 67 and 68 and
pinion shaft 73 is journaled in bearings 81, 82 and 83. The
pinion shaft is also provided with a pair of brake drums 87
and 88 which are adapted to be frictionally engaged by brake
bands to arrest the rotation of the pinion shaft. Motor 74
may consist of either an electrical or hydraulic motor and is
rigidly mounted on gantry 55 on a side opposite ~rom gear
!case 72. Drive shaft 75 is drivingly connected to the output
shaft of motor 74 and extends through the entire length of
the axial opening in the pinion shaft, into gear case 72.
The free end of shaft 75 abuts a stop 89 mounted on the end
wall 9~ of the gear case.
Planetary gear set 76 consists of a sun gear 91, a
ring gear 92 and a plurality of planetary gears 93. Sun gear
91 is formed integrally with the end of drive shaft 75. Ring
gear 92 is formed as an outer wall section of gear case 72.
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Each of planetary gears 93 is provided with a shaft 94
mounted on a planetary gear carrier 95.
Planetary gear set 77 consists of a sun gear 96, a
ring gear 97 and a plurality of planetary gears 98. Sun
gear 96 is provided with an axial opening, receiving drive
shaft 75 therethrough, and is drivingly connected to plane-
tary gear carrier 9S of gear set 7Ç. Ring gear 97 is formed
as a component of gear case 72. Each of planetary gears 98
is provided with a shaft 99 mounted on a rotatable carrier
100. Planetary gear carrier 100 is provided with an annular
portion 101 which extends into an enlarged section of the
opening in pinion shaft 73 and which receives drive shaft 75
therethrough. The outer end of annular carrier portion 101
is provided with crowned, external splines which engage with
a set of internal splines on the end of the pinion shaft to
drivingly connect the planetary gear carrier of gear set 77
to the pinion shaft.
In the operation of the drive unit shown in Figure
4, whenever motor 74 is operated, drive will be transmitted
through drive shaft 75, planetary gear set 76, planetary gear
set 77 and pinion shaft 73 to drum 66. Under such circum-
stances, the drive will undergo a first stage spe~d reduction
by planetary gear set 76, a second stage speed reduction by
planetary gear set 77 and a third stage reduction by the
parallel pinion and bull gears transmitting drive from the
pinion shaft to the rope drum. Whenever it is desired to
brake the unit, a suitable mechanism is operated to cause the
brake bands cooperating with brake drums 87 and 88 to fric-
tionally engage such drums to arrest the rotation of the
pinion shaft. The rotation of gear case 72 can be restrained
by any suitable means including a linkage, such as torque
arm 102, operatively interconnecting the gear case and the
gantry.
Loads imposed on the shovel resulting in structural
deflections of the gantry are prevented from being transmit-
ted to planetary gear sets 76 and 77 by means of several
structural features of the crowd assembly including the link-
age provided with torque arm 102, the length of drive shaft 75
which permits it to deflect, the crowned spline connection
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between the planetary gear carrier of gear set 77 and the
pinion shaft, and the length of the pinion shaft which allows
limited deflection. In essence, gear sets 76 and 77 are
isolated from the loads imposed on the machine and the re-
sulting structural deflections of the machine thus minimizingif not eliminating misalignment of the gear components there-
of.
Referring to Eigure 5, there is shown another em-
bodiment of the present invention. In particular, Figure 5
illus~rates a crowd drive assembly 103 generally consisting
of a rope drum 104, a gear case 105, a motor 105, a drive
shaft 107, a first planetary gear set 108 and a secondary
planetary gear set 109 Rope drum 104 is adapted to be
trunnion mounted in a set of bearings 110 and 111 provided in
15 gantry 55. Gear case 105 is adapted to be mounted on gantry
55 at one end of rope drum 104. Mounted on the gantry at the
opposite side of rope drum 104 is motor 106 which is provided
with an output shaft coupled to drive shaft 107. Drive shaft
107 is disposed axially relative to rope drum 104 and extends
20 into gear case 105. Planetary gear set 108 consists of a sun
gear 112 formed on the end of drive shaft 107, a ring gear
113 formed on gear case 105 and a plurality of planetary ~
gears 114. Each of the planetary gears is provided with a
shaft 115 mounted on a planetary gear carrier 116.
Planetary gear set 109 consists of a sun gear 117
connected with a spline connection with planetary gear
carrier 116 and having an axially disposed opening therein
for receiving the drive shaft therethrough, a ring gear 118
and a plurality of planetary gears 119. Each of the planet-
ary gears is provided with a shaft 120 mounted on a planetary
gear carrier 121. Carrier 121 is spline connected to a quill
shaft 122 which receives a portion of the drive shaft there-
through and is provided with crowned, e~ternal splines at the
free end thereof which are received within an end of rope
drum 104 and engage a set of internal splines thereon. Alter-
natively, quill shaft 122 may be drivingly connected to the
other side of the drum through a crowned spline connection.
In the operation of crowd drive assembly 103, when
motor 106 is operated, drive will be transmitted through
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drive shaft 107, planetary gear set 108 and planetary gear
set 109 to rope drum 104. As drive is transmitted through
planetary gear sets 108 and 109, it will undergo first and
second stage speed reductions. As stated with respect to the
embodiment shown in Figure 4, planetary gear sets 108 and 109
will be isolated from the structural deflections of the
machinP to prevent misalignment of the gears thereof. The
elongated lengths of drive shaft 107 and quill shaft 122,
allowing a certain amount of deflection, and the crowned
spline connection of quill shaft 122 with the rope drum
principally assure the isolation of the gear sets from the
structural deflections of the machine.
Figure 6 illustrates another embodiment of the
present invention which is similar in construction and opera-
tion to the embodiment shown in Figure 5 except that it pro-
vides for an additional speed reduction stage. Figure 6
illustrates a crowd drive assembly 123 generally consisting
of a rope drum 124 trunnion mounted on gantry 55, a first
gear case 125 mounted on gantry 55 at one end of drum 124, a
second gear case 126 mounted on the gantry at an opposite end
of drum 124, a motor 127 mounted on gear case 125, a first
planetary gear set 128 mounted in gear case 125 and drivingly
connected to the output shaft of motor 127, a drive shaft 129
drivingly connected to planetary gear set 128 and extending
through drum 124 into gear case 126, a second planetary gear
set 130 mounted in gear case 126 and drivingly connected to
drive shaft 129 and a third planetary gear set 131 drivingly
interconnecting planetary gear set 130 and drum 124. The
planetary gear carrier of gear set 131 is drivingly connected
to a quill shaft 132 which is drivingly connected to drum 124
through a spline connection at the free end thereof. Also,
the output shaft of motor 127 is drivingly connected to the
sun gear of gear set 128 through a crowned spline connection.
Alternatively, the output shaft of the motor can be drivingly
connected to the sun gear shaft of gear set 128 through a
flexible coupling of any suitable type.
In the operation of the drive assembly shown in
Figure 6, it will be appreciated that when motor 127 is
operated, drive will be transmitted through gear set 128
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where it will undergo a first stage speed reduction, drive
shaft 129, gear train 130 where it will undergo a second
stage speed reduction, gear set 131 where it will undergo a
third stage speed reduction and through quill shaft 132 to
drum 124. In this arrangement, the elongated lengths of
drive shaft 129 and quill shaft 132 and the crowned spline
connections between the output shaft of the motor and the
sun gear of gear set 128, and quill shaft 132 and drum 124
function to isolate gear sets 128, 130 and 131 from the
structural deflections of the machine frame.
Figure 7 illustrates another embodiment of the
invention as applied to a crowd system utilizing a crowd
handle in lieu of a rope and sheave arrangement as illustra-
ted in Figure 1. The embodiment consists of a crowd drive
assembly 133 including a drive unit 134 mounted on gantry 55
and a crowd handle 135 also mounted on the gantry for fore
and aft reciprocal movement, above the drive unit. The c~owd
handle is guided on the upper end of the gantry by sets of
rollers 136 and 137, and is provided with a rack portion 138
on the underside thereof which is drivingly engaged by a pin-
ion portion 139 of a quill shaft 140 journaled in the gantry.
The crowd unit generally consists of a gear case 141 flange
mounted on one side of the gantry, a gear case 142 flange
mounted on an opposite side of the gantry, a motor 143 flange
mounted on gear case 141, a first planetary gear set 144,
second and third planetary gear sets 145 and 146, a drive
shaft 147 and a quill shaft 148.
Planetary gear set 144 is mounted in gear case 141.
Gear sets 145 and 146 are mounted in gear case 142 and are
disposed in axial alignment with gear set 144. The output
shaft of motor 143 is drivingly connected to the sun gear
shaft of gear set 144 by means of a coupling 149. Coupling
149 is connected to the sun gear shaft by means of a crowned
spline connection to provide a flexible coupling between the
output shaft of motor 143 and gear set 144. The output of
gear set 144 is connected to the input of gear set 145 by
means of elongated drive shaft 147. Shaft 147 is connected
to the planetary gear carrier of gear set 144 through a
c~Dwned spline connection. The planetary carrier of gear set
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146 is drivingly connected to pinion shaft 140 through
elongated quill shaft 148. As shown in Figure 7, the plane-
tary gear carrier of gear set 146 is drivingly connected to _
one end of quill shaft 140 through a crowned spline connec-
tion and the opposite end of ~uill shaft 140 is drivinglyconnected to pinion shaft 140 through a crowned spline connec-
tion.
In the operation of the assembly shown in Figure 7,
when motor 143 is operated, drive is transmitted to planetary
gear set 144 where it undergoes a first stage speed reduction,
through drive shaft 147 to planetary gear set 145 where it
undergoes a second stage speed reduction, to planetary gear
set 146 where it undergoes a third stage speed reduction and
through quill shaft 148 to pinion shaft 140. It will be
appreciated that upon rotation of pinion shaft 140, pinion
portion 139 thereof will engage the rack portion of crowd
handle 135 to drive the crowd handle in either a fore or aft
direction. It further will be seen that gear sets 144, 145
and 146 will be isolated from the frame deflections of the
machine caused by loads imposed upon the machine by means of
the elongated lengths of drive shaft 147 and quill shaft 148
and the various crowned spline connections in the drive train
providing flexible couplings between the gear sets and the
other drive components of the drive train.
Hoist system 24 generally includes a hoist drive
assembly 150, sheaves 151 and 152 and a hoist line 153.
Hoist drive assembly 150 is mounted on the upper frame of the
i machinel rearwardly of the swing axis of the machine, as best
illustrated in Figure 2. Sheave 151 is mounted on the lower
30 end of stiffleg 44 and sheave 152 is mounted on an upper,
rear end of hoist frame 45. As illustrated in Figure 1,
hoist line 153 is operatively connected to hoist drive assem-
bly 150, extends forwardly and around sheave 151, extends
upwardly and around sheave 152 and extends downwardly and is
connected to a bail 154 mounted on the mounting shaft of
sheave 151. It further will be seen that by operating the
; hoist drive assembly to pay out or take in hoist line 153,
hoist frame 45, handle 46 and hoist link 48 will be caused to
pivot about head shaft 49 to correspondingly hoist and lower
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the dipper.
The hoist drive assembly consists of a hoist drum
155 disposed substantially in longitudinal alignment with the
stiffleg and a pair of substantially identical drive units
156 and 157 mounted on opposite ends of the hoist drum and
being drivingly connected thereto.
Referring to Figure 8, it will be seen that hoist
drum 155 is trunnion mounted on a support frame 158 connected
to the upper frame of the machine. Drive unit 157 consists
of a gear case 159 mounted on the support frame, a first
planetary gear set 160 mounted in gear case 159, a secondary
planetary gear set 161 also mounted in gear case 159, a motor
162 supported on the upper deck of the machine, a flexible
mechanical coupling 163 drivingly interconnecting the output
shaft of motor 162 and first planetary gear set 160 and a
drive shaft 164 drivingly interconnecting the output of gear
set 161 and hoist drum 155. Flexible mechanical coupling 163
may be of any suitable type which is capable of transmitting
torque while allowing angular and parallel displacement of
the input and output components thereof. One of such coup-
lings which can be used with the invention and which is com-
mercially available consists of a housing, a pair of axially
spaced hubs rotatably mounted in the housing and connectable
to input and output shafts and a steel spring element inter-
connecting the hubs which functions to transmit torquebetween the hubs yet has sufficient flexibility to allow the
axes of the hubs and, correspondingly, of the input and out-
put shafts to become displaced both angularly and radially.
Gear set 160 consists of a sun gear 165, a ring gear
166 and a plurality of planetary gears 167. Sun gear 165 is
formed on a shaft which is drivingly connected to the output
shaft of coupling 163. Ring gear 166 is formed as a component
part of gear case 159. Each of planetary gears 167 is pro-
vided with a shaft 168 mounted on a planetary carrier 169.
Gear set 161 consists of a sun gear 170, a ring gear 172 and
a plurality of planetary gears 173. Sun gear 170 is formed
on a shaft drivingly connected to the planetary gear carrier
169 of gear set 160 through a spline connection. Ring gear
172 is formed as part of gear case 159. Each of planetary
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gears 173 is provided with a shaft 174 mounted on a carrie.r
175. Drive is transmitted from planetary gear carrier 175 to
hoist drum 155 by means of drive shaft 164. The outer end of
shaft 164 is drivingly connected to planetary gear carrier
175 through a crowned spline connection 176. The inner end
of shaft 164 is drivingly connected to a trunnion of hoist
drum 155 through a crowned spline connection 178.
In the operation of the hoist drive assembly shown
in Figure 8, when motor 162 is operated, drive is transmitted
through flexible coupling 163, planetary gear set 160 where
it undergoes a first stage speed reduction, planetary gear
set 161 where it undergoes a second stage speed reduction and
drive shaft 164 to rotate hoist drum 155. Because of the
flexible coupling between motor 162 and planetary gear set
160 as provided by flexible mechanical coupling 163, and the
flexible coupling between planetary gear set 161 and hoist
drum 155 as provided by the crowned spline connections of
drive shaft 164 with carrier 175 and the trunnion of the hoist
drum, gear sets 160 and 161 will be isolated from the struc-
tural deflections of the machine and particularly deflectionsin the upper frame. Figure 9 illustrates an alternative hoist drive
assembly 179 which consists of a hoist drum 180 and a drive
unit 181. In such embodiment, hoist drum 180 is provided
with annular trunnions 182 and 183 which are journaled in a
set of bearings 184 and 185 mounted in a support frame 186.
~he drive assembly consists of a motor 187, a gear case 180,
a drive shaft 189, a flexible mechanical coupling 190, a first
planetary gear set 192 and a second planetary gear set 193.
Motor 187 is mounted on one side of the hoist drum and is
supported on the upper deck of the machine. Gear case 188 is
mounted on the opposite side of the hoist drum and is support-
ed on a frame mounted on the deck. Drive is transmitted frommotor 187 to gear case 188 by drive shaft 189 which extends
through trunnions 182 and 183. Flexible mechanical coupling190 is similar in construction and function to.¢oupling 163
described in connection with the embodiment shown in Figure 8
to transmit torque from the motor output shaft to drive shaft
189 while permit~ngangular and parallel displacement of such
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shafts.
Planetary gear sets 192 and 193 are mounted in gear
case 188. ~ear set 182 consists of a sun gear 194, a ring
gear 195 and a plurality of planetary gears 196. Sun gear
194 is formed on the free end of drive shaft 189. Ring gear
195 is formed as a component of the gear case. Each of
planetary gears 196 is provided with a shaft 197 mounted on
a rotatable carrier 198. Gear set 193 similarly consists of
a sun gear 199, a ring gear 200 and a plurality of planetary
gears 201. Sun gear 199 is spline connected with planetary
gear carrier 198 and is provided with an axial passageway for
receiving the end of drive shaft 189 therethrough. Ring gear
200 is formed as a component of the gear case. Each of plane-
tary gears 201 is provided with a shaft 202 mounted on a
rotatable carrier 203. Gear carrier 203 is drivingly connec-
ted to trunnion 183 of the hoist drum by means of a crowned
; spline connection 204. It further will be noted that trunnion
183 is drivingly connected to the main body of the drum through
a spline connection 205.
In the operation of the hoist drive assembly shown
in Figure 9, when motor 187 is operated, drive is transmitted
through flexible coupling 190, drive shaft 189, planetary
gear sets 192 and 193 and trunnion 183 to hoist drum 180. As
in the previously described embodiments, it will be seen that
the effect of flexible mechanical coupling 190, the elongated
length of drive shaft 189 and crowned spline connection 204
will be to isolate gear sets 192 and 193 from the adverse
effects of the frame deflections of the machine.
The system for swinging the upper frame relative to
the lower frame on the live roller circle consists of a number
of swing assemblies 206. Each of the swing assemblies is
mounted on the upper frame and is provided with a pinion
; drivingly engaging ring gear 37 on the lower frame. Any suit-
able number of such assemblies can be used although an even
number of such assemblies symmetrically positioned should be
used. In the machine shown in the drawings, four of such
assemblies are used, arranged symmetrically to provide a uni-
form load on the machine.
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Referring to Figure 10, there is illustrated a
swing drive assembly 206. Basically, the assembly consists
of a pinion shaft 207 drivingly connected to ring gear 37
and a drive unit 208 drivingly connected to the pinion shaft.
Pinion shaft 207 is disposed vertically and is journaled in
a pair of bearings 209 and 208 mounted on a support frame 210
rigidly secured to a portion of upper frame 36. The lower
free end of the pinion shaft is provided with a pinion 211
having crowned teeth drivingly engaged with ring gear 37.
The drive unit of the assembly consists of a gear
case 212 mounted on support frame 210, first and second
planetary gear sets 213 and 214 mounted in the gear case and
a motor 215 mounted on the gear case and drivingly connected
to the first planetary gear set through a flexible mechanical
coupling 216. Planetary gear set 213 consists of a sun gear
217, a ring gear 218 and a plurality of planetary gears 219.
Sun gear 217 is drivingly connected to an output shaft of
flexible mechanical coupling 216 which is similar in construc-
tion and operation to couplings 163 and 190 of the embodiments
of the invention described in connection with Figures 8 and 9.
Ring gear 218 is formed as a component of the gear case. Each
of planetary gears 218 is provided with a shaft 220 mounted on
a rotatable carrier 221. Planetary gear set 214 consists of
a sun gear 222, a rin~ gear 223 and a plurality of planetary
gears 224. Sun gear 222 is mounted on a sun gear shaft 225
which is drivingly connected to planetary gear carrier 221
through a spline connection. Ring gear 223 is formed as a
component of the gear case. Each of planetary gears 224 is
provided with a shaft 226 which is mounted on a rotatable
carrier 227. Carrier 227 is drivingly connected to the upper
end of pinion shaft 207 by means of a crowned spline connec-
tion 228.
In the operation of the assembly shown in Figure 10,
when motor 215 is operated, drive will be transmitted through
coupling 216, gear sets 213 and 214 to pinion shaft 207. As
the pinion shaft is rotated, the interaction of pinion 211
with ring gear 37 will cause support frame 210 and corres-
pondingly upper frame 36 to rotate or swing relative to lower
frame 34 about live roller circle 35. As in previous embodi-
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ments of the invention, it will be noted that flexible coup-
ling 216, crowned spline connection 228 and the crowned teeth
of pinion 211 will function to isolate gear sets 213 and 214
from the deflections of the upper and lower frames of the
machine.
Crawler drive assemblies 26 and 27 mounted on the
rear end of the main support unit and the rear ends of craw-
ler units 21 are substantially similar in construction and
operation. Crawler drive assembly 27 consists of a drive
sprocket 29 and a drive unit 229. Sprocket 29 is drivingly
mounted on a quill shaft 230 through a spline connection.
Shaft 230 is journaled in the rear end of crawler frame 28.
Drive unit 229 consists of a gear case 231 mounted on the
outboard side of the crawler frame, a gear case 232 mounted
on the inboard side of the crawler frame, a parallel gear set
233 and planetary gear sets 234 and 235 mounted in gear case
232, a drive shaft 236 extending from year case 232 into gear
case 231, a planetary gear set 237 mounted in gear case 231,
a quill shaft 238 mounted concentrically with drive shaft 236
and quill shaft 230 and a motor 239 mounted on the rear end
of the lower frame and drivingly connected to parallel gear
set 233 through a flexible mechanical coupling 240.
Parallel gear set 233 consists of a pair of gears
241 and 242 journaled in year case 232. Gear 241 is driving-
ly connected to coupling 240 which is substantially similar
in construction and function to couplings 163, 190 and 216
described in connection with the embodiments shown in Figures
8 through 10. Gear 242 is drivingly connected to a sun gear
shaft 243.
Planetary gear set 234 consists of a sun gear 244,
a ring gear 245 and a plurality of planetary gears 246. Sun
gear 244 is formed on one end of shaft 243. Ring gear 245
is formed as a component of gear case 232. Each of planetary
gears 246 is provided with a shaft 248 mounted on a rotatable
35 carrier 249. Planetary gear set 235 consists of a sun gear
250,a ring gear 251 and a plurality of planetary gears 252.
Sun gear 250 is formed on a sun gear shaft 253 drivingly
connected to rotatable carrier 249 through a spline connec-
tion. Ring gear 251 is formed as a component of gear case
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232. Each of planetary gears 252 is provided witll a shaft
254 which is mounted on a rotatable carrier 255.
Planetary gear set 237 consists of a sun gear 256,
a ring gear 257 and a plurality of planetary gears 258. Sun
gear 256 is formed integrally with the outer end of drive
shaft 236 which is drivingly connected at the inner end
thereof to rotatable carrier 255 through a spline connection.
Ring gear 257 is mounted on gear case 231. Each of planetary
gears 258 is provided with a shaft 259 mounted on a carrier
260. Quill shaft 238 is drivingly connected at the outer end
thereof through a crowned spline connection 261 with rotatable
carrier 260. At the inner end, shaft 238 is drivingly con-
nected to quill shaft 230 by means of a crowned spline con-
nection 262.
In the operation of the crawler drive assembly
shown in Figure 11, whenever motor 239 is operated, drive
will be transmitted through flexible coupling 240, parallel
gear set 233, planetary gear sets 234 and 235, drive shaft
236, planetary gear set 237 and quill shaft 238 to drive
sprocket 29 through shaft 230. As drive is transmitted from
the motor to the sprocket, it will undergo a first stage
speed reduction by parallel gear set 233, a second stage
speed reduction by planetary ~ear set 234, a third stage
speed reduction by planetary gear set 235 and a fourth stage
speed reduction by planetary gear set 237. The various gear
sets further will be isolated from loads applied to the craw-
ler frame and lower frame resulting in structural deflections
by means of flexible coupling 240, the elongated lengths of
shaft 236 and quill shaft 238 and crown spline connections
. 30 261 and 262.
At the beginning of each digging cycle of the
machine as described, the crowd system is operated to fully
retract the front end assembly and the hoist system is opera-
ted to lower the dipper so that the dipper is positioned
adjacent the lower end of the stiffleg. Suitable resilient
pads are provided at the lower end of the stiffleg to prevent
damage to the stiffleg by the dipper. To commence the opera-
ting cycle of the machine, the operator manipulates appropri-
ate controls at the operator's station on the machine to
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permit the crowd rope to pay out. Under such conditions, the
weight of the front end assembly will cause the stiffleg to
pivot forwardly, simultaneously crowding the dipper into the
material being excavated or loaded. Simultaneously with the
commencement of the crowding action of the dipper, appropri-
ate controls are operated on the machine to effect limited
hoisting motion of the dipper. This is accomplished by
operating hoist drum 155 to take up hoist line 153. As the
dipper is crowded into the bank of material being excavated
or loaded, the combined crowding and hoisting action causes
it to make a flat pass. At the same time, pitch control
system 53 causes the pitch of the dipper to remain constant
relative to the ground. At the end of the crowd phase of the
cycle, the pitch control mechanism is released to cause the
dipper to pitch upwardly and thus assure a full load of
material in the dipper. The upward pitch of the dipper is
restricted by the pitch stop system 54 in a manner as
described in the aforementioned patent relating to such
system.
After the dipper has been pitched upwardly, controls
for the crowd and hoist systems and the swing machinery are
operated to position the dipper above the dump body of a
hauling vehicle or another suitable repository for the
material, where the door of the dipper is tripped to cause
the door to open and the material to be unloaded. The de-
sired retracting motion of the front end assembly is effected
by operating crowd motor 74 to rotate crowd drum 71 and take
in crowd rope 61. Under such conditions, mast 58 will be
caused to pivot rearwardly and such motion will be transmitted
to the front end assembly 22 causing stiffleg 44 to pivot up-
wardly.
As soon as the material has been dumped, the swing
machinery can be operated to rotate the front end of the
machine back to the embankment, the crowd system can be
operated to continue to retract the front end assembly and
the hoist system can be operated to permit the dipper handle
to swing downwardly at a controlled rate until it again is
positioned at the lower end of a stiffleg, ready to begin
another operating cycle. To re-position the machine, the
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propel system is operated in the conventional manner to move
the machine.
It will be appreciated that during the corwding,
retracting, hoisting or lowering of the dipper, the swinging
of the upper frame and the propelling of the entire machine,
the machine will be subjected to a multitude of loads which
result in structural deflections of the frames of the machine.
In conventional shovels of the type described, such deflec-
tions would be transmitted to the various gear trains for the
various machinery on the machine, resulting in misalignment
of the gear train components thereof. In the present inven-
tion, the transmission of such deflection to the various gear
trains of the machine is at least substantially minimized,
thus assuring full contact between mating gear teeth during
the various work functions of the machine. The result of
such consistent and uniform gear tooth contact is more
efficient torque transmission and less tooth wear and break-
age.
From the foregoing detailed description, it will be
evident that there are a number of changes, adaptations and
modifications of the present invention which fall within the
province of those persons having ordinary skill in the art to
which the present invention pertains. However, it is intended
that all such variations not departing from the spirit of the
invention be considered as within the scope thereof as limited
solely by the appended claims.
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