Hoist with oil cooled brake

A compact, lightweight, electrically powered hoist with a drum used for hoisting or lowering a payload. A vertically oriented reversible motor is controlled by a control pendant with a momentary switch to drive a helical gear reduction and a worm gear reduction. A worm shaft and a drum shaft wind wire rope on a drum. A one-way clutch and a brake on a driven shaft free-wheel during hoisting operations. A clutch and brake hold the payload in a hoisted position. Lowering of the hoisted payload is accomplished by reversal of the motor, and driving a shaft and clutch against the torque of the engaged brake. A wire rope with a swaged fitting is anchored to the drum by engagement in a keyhole. The hoist may be mounted horizontally, vertically or on a ceiling.

BACKGROUND OF THE INVENTION 
1. Field of the Invention--The present invention pertains to a reversible 
electric hoist, and more particularly, pertains to a hoist with a one-way 
clutch and brake secured over a worm shaft. The brake and clutch are not 
effectively engaged during hoisting motions, but hold a hoisted payload in 
a static position. A payload is lowered by reversed action of a drive 
motor against the clutch and brake. 
2. Description of the Prior Art--There are a number of base mounted drum 
hoists, each employing a variety of prime movers, geared systems and 
one-way clutches engaging a disc brake. 
The present invention provides a hoist which employs a one-way clutch and 
an adjustable band brake operated in an oil bath to hold a hoisted 
payload, which is lowered by motor action against the clutch and band 
brake. 
SUMMARY OF THE INVENTION 
The present invention includes a reversible motor to rotate a drum to 
either hoist, hold or lower a payload. A one-way clutch and drum on a 
driven worm shaft are inactive during hoisting motions, and requires motor 
activation against the one-way clutch and drum to lower a payload. 
According to one embodiment of the present invention, there is provided a 
reversible motor which mounts on an aluminum motor adapter, which in turn 
mounts on a lightweight aluminum frame and speed reducer housing. A 
helical pinion on the motor drive shaft drives a helical gear on a worm 
shaft located in the reducer housing. The worm shaft aligns in an upper 
bearing in the aluminum motor adapter and a lower bearing in the bottom of 
the speed reducer housing. A worm drive on the worm shaft drives a worm 
gear which in turn imparts rotary motion to a drum shaft and drum for the 
purpose of hoisting or lowering a payload. A one-way clutch affixes to the 
worm shaft and a brake drum frictionally engages over the worm shaft. An 
adjustable brake assembly, including a brake band with a brake lining, 
positions over and about the brake drum and one-way clutch. In a hoisting 
operation the clutch spins freely and free-wheels with reference to the 
brake assembly in the hoisting direction until a static hoisted position 
is attained, at which point the clutch is automatically engaged. The brake 
holds a payload in the hoisted position. The brake and clutch also prevent 
reverse drum motion during hoisting. In a lowering operation, lowering of 
a hoisted payload is accomplished by reversing the motor direction to 
overcome the friction of the clutch and brake drum against the brake band 
and brake lining to allow reverse motion of the worm shaft, worm drive and 
gear, and the drum shaft and drum. 
One significant aspect and feature of the present invention, is a one-way 
clutch and brake system which does not inhibit payload hoisting 
Another significant aspect and feature of the present invention is the use 
of a one-way clutch and brake system whose friction must be overcome to 
lower a payload. 
Still another significant aspect and feature of the present is a 
lightweight hoist system with a slim foot print which can be mounted in 
compact spaces and in various orientations. 
Yet another significant aspect and feature of the present invention is a 
hoist utilizing a lightweight casting, which serves as a hoist frame and 
enclosure for the drive components which is less expensive to manufacture, 
easier to seal and lighter in weight than separable frames and enclosures. 
A further significant aspect and feature of the present invention is a 
simplified motor reversal system eliminating the need for magnetic 
contactors while preserving the inherent safety of a momentary contact 
"dead-man" switch 
Still a further significant aspect and feature of the present invention is 
a keyhole wire rope anchor and associated ramp for the simplified 
anchoring of a wire rope to the hoist drum. 
Yet another significant aspect and feature of the present invention is a 
light weight brake which requires no electrical switches or components to 
engage and disengage. 
Still another significant aspect and feature of the present invention is an 
oil bath enhancing smooth motion, long brake lining life and removal of 
heat from the brake lining. 
Having thus described the embodiments of the present invention, it is a 
principal object hereof to provide a reversible, lightweight, electric 
hoist and control system with a one-way clutch and a brake mechanism. 
Another object of the present invention is to provide an improved method of 
attachment of a wire rope to a hoist drum.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
FIG. 1 illustrates a perspective view of a hoist 10, the present invention. 
The exterior components of the hoist 10 include a hoist drum 12; a 
configured frame 14; a sealed box like speed reducer housing 16 which is 
cast with and is an integral part of the frame 14; a bearing holder 18 
secured to the sealed speed reducer housing 16 by a plurality of machine 
screws 20a-20n; an aluminum motor adapter 22 secured to the sealed speed 
reducer housing 16 by a plurality of screw fasteners 24a-24n; and 
vertically aligned reversible motor 26 secured to the motor adapter 22. 
The configured frame 14 and sealed speed reducer housing 16 are a common 
aluminum casting for weight reduction. Internal rotating components are 
lubricated by and operate in an oil bath in the sealed speed reducer 
housing 16. A power cord 28 and connector 30 secure to the reversible 
motor 26. A control pendant 32 including a power switch 34 and a rocker 
switch 36 for direction control attaches to the reversible motor 26 by a 
cable 38 and a connector 40. A plurality of drain/level plugs 42a- 42n 
position at strategic points about the sealed speed reducer housing 16 to 
accommodate vertical alignment of the hoist 10 as illustrated, as well as 
other positional alignments such as a ceiling mount. A plurality of 
mounting holes 44a-44n position on the configured frame 14 for securement 
of the hoist 10 to an external mounting base. 
FIG. 2 illustrates a cross-sectional view taken along line 2--2 of FIG. 1 
of the hoist 10 with components contained in the sealed speed reducer 
housing 16. All numerals correspond to those elements previously 
described. A vertically aligned keyed motor shaft 50 aligns in a hole 52 
in the motor adapter 22, in a shim 53, in a porous oil impregnated motor 
pinion thrust washer 54, and within a seal 59 in the hole 52. A cap screw 
56, a washer 58, and a key 60 engage in the keyed motor shaft 50 and 
secure a helical pinion 62 to the keyed motor shaft 50. A vertically 
oriented multi-radiused worm shaft 64 secures between an upper bearing 66 
in the motor adapter 22 and a lower bearing 68 in a bearing housing 70 on 
the inner lower surface of the sealed speed reducer housing 16 whose 
bottom is integral to the horizontal configured frame 14. A helical gear 
72 secures over and to the multi-radiused worm shaft 64 with a retainer 
ring 73 and by a key 74. A brake assembly 75 includes a one-way clutch 76, 
a brake drum 81, a brake band 82, and a brake lining 84 and other 
components as described later in detail. The one-way clutch 76, with 
spacers 78 and 80 align over each clutch end, and frictionally engages and 
secures over and to the multi-radiused worm shaft 64. The brake drum 81 
frictionally engages over and to the one-way clutch 76. A brake band 82, 
including a brake lining 84, positions over and about the brake drum 81. 
The one-way clutch 76 is further described in detail in FIG. 4. A worm 
drive 86 on the multi-radiused worm shaft 64 drives a worm gear 88 secured 
to a horizontally aligned drum shaft 90 by a key 92. Ultimately, the drum 
shaft 90 and drum 12 are driven by action of the reversible motor 26 upon 
and through the helical pinion 62, the helical gear 72, the multi-radiused 
worm shaft 64, worm drive 86, and the worm gear 88. 
During hoisting operations, the multi-radiused worm shaft 64 is driven as 
previously described and free-wheels and turns freely within the one-way 
clutch 76 and the brake band 82 and the brake lining 84 have no effect on 
the mechanical drive components. In the static hoisted position, the 
clutch is automatically engaged as it is against reverse motion during 
hoisting. The brake drum 81, over the engaged clutch 76, is held by action 
of the brake band 82 and lining 84. The clutch also prevents any lowering 
motion should power to the motor be interrupted. During lowering, the 
multi-radiused worm shaft 64 is driven by reverse motor action against the 
brake assembly 75, and must overcome the brake torque caused by the brake 
action of the brake band 82 and brake lining 84 against the brake drum 81 
and engaged one-way clutch 76 to cause the hoisted payload to be lowered. 
During hoisting, the reversible motor 26 must do work against the payload 
in order to increase its potential energy. When the payload is stationary, 
the brake assembly 75 supplies torque to counter the payload's 
gravitational pull. In order to lower the payload, the reversible motor 26 
must work against the brake assembly 75, the energy converted to heat, in 
order to cause the drive train rotation that lowers the payload and 
reduces the potential energy. 
The one-way clutch 76 allows the brake assembly 75 to always be in the 
system, and yet the brake friction does not inhibit the motor's ability to 
hoist a payload. 
FIG. 3 illustrates a cross-sectional view taken along line 3--3 of FIG. 1 
of the hoist 10, the support, the drum and the bearing members where all 
numerals correspond to those elements previously described. The configured 
frame 14 and sealed box like speed reducer housing 16 are a common 
lightweight aluminum casting. A vertical bearing support member 100 
extends upwardly from the configured frame 14 to house a horizontally 
aligned outboard bearing 102. The outboard bearing 102 prevents cantilever 
loading of the drum shaft 90. A horizontally aligned bearing 104 mounts in 
a cavity 106 in the bearing holder 18, and a similar bearing 108 is 
mounted in a cavity 110 in a side wall of the sealed speed reducer housing 
16 to accommodate the opposite end of the drum shaft 90. A spacer 112 is 
positioned between bearing 104 and the worm gear 88, and a drum shaft seal 
114 positions over the drum shaft 90 and in a seal cavity 116. A 
connecting pin 118 secures through holes 120 and 122 in the drum collar 
124 and through hole 126 in the drum shaft 90 to positionally secure the 
hoist drum 12 to the drum shaft 90. Bores 128 and 130 in the sidewalls of 
the hoist drum 12 align over and about the drum shaft 90. A retaining ring 
132 secures in an annular groove 134 in the drum shaft 90 to secure the 
drum shaft 90 to the outboard bearing 102. The worm gear 88 is secured to 
the drum shaft 90 by a key 92 and by a set screw 135. The hoist drum 12 
also includes side walls 136 and 138 and an integral ramped surface 140 on 
the inner end of the hoist drum 12 to serve as a guide to orient a wire 
rope correctly on the drum. A wire rope key hole 142 in the side wall 136 
of the hoist drum 12 accommodates a wire rope with a swaged fitting as 
later explained in detail. The ramped surface 140 adjacent to the wire 
rope key hole 142 directs wire rope in the correct direction and fills the 
void behind the first wrap of wire rope. The reversible motor 26 is 
secured to the motor adapter 26 by a plurality of machine screws 
144a-144n. A plurality of 0 ring seals 145a-145n secure beneath machine 
screws 144a-144n to provide for housing 16 sailing. 
FIG. 4 illustrates a cutaway top view of the hoist 10 illustrating elements 
of the brake assembly 75 as previously described and additional elements 
as now described herein where all numerals correspond to those elements 
previously described. Bushings 150 and 152 mount in holes 154 and 156 in 
the sealed speed reducer housing 16 to accommodate threaded brake band 
connectors 158 and 160. A brake tension spring 162 and a brake tension nut 
164 fit over the threaded shaft portion 158a of the brake band connector 
158, and a brake tension nut 166 fits over the threaded portion 160a of 
the brake band connector 160. Nut and bolt assemblies 168 and 170 align in 
holes 172 and 174 of the brake band connectors 158 and 160 and also in 
holes 176 and 178, common to the brake band 82 and brake lining 84, to 
secure the brake band 82 and brake lining 84 to the brake band connectors 
158 and 160, respectively. Brake band tension about the brake drum 81 is 
adjusted to the proper tension increment by adjusting brake tension nuts 
164 and 166. Elastomeric 0-ring fittings 180 and 182 position in grooves 
on the brake band connectors 158 and 160 and against the interior surfaces 
of bushings 150 and 152 to further provide oil sealing for the speed 
reducer housing 16. 
FIG. 5 illustrates a cross-sectional view of the drum looking toward the 
sealed speed reducer housing 16 taken along line 5--5 of FIG. 1, 
illustrating the method of wire rope attachment to the hoist drum 12 and 
where all numerals correspond to those elements previously described. A 
wire rope key hole 142 in the sidewall member 136 of the hoist drum 12 
includes a hole 142a and a down sized slotted hole 142b. A wire rope 180 
with a swaged fitting 182 affixed to its end, also illustrated adjacent to 
the drum 12, passes first within the larger hole 142a and then positions 
into the slotted hole 142b where it is frictionally engaged by the swaged 
fitting 182 within the smaller dimensioned slotted hole 142. The hoist 
drum 12 is rotated to wrap the wire rope 180 about the cylindrical surface 
of the drum 12 and is assisted by the ramped surface 140. 
FIG. 6 illustrates an electrical diagram 190 of the motor control system 
for the hoist 10 where all numerals correspond to those elements 
previously described. Power is delivered to the reversible motor 26 by 
power cord 28 and to the control pendant 32 by cable 38. A first momentary 
contact power switch 34 delivers electrical power to a second rocker 
switch 36. The second switch 36 is used to select clockwise or counter 
clockwise rotation of the reversible motor 26 for hoisting a payload or 
lowering a payload against the torque of the brake assembly 75. The 
momentary contact power switch 34 is depressed for hoisting or lowering. 
Power is applied to the rocker switch 36, which has been preselected for 
hoisting or lowering, by activating the momentary power switch 34. Switch 
34 also acts as a "dead-man" safety switch in that if the hoist operator's 
finger is removed from the switch, all power is interrupted to the motor, 
and the payload is held in position by the one-way clutch and brake. The 
rocker switch 36 provides electrical current to motor coils 200 and 202, 
motor capacitors 204 and 206, and motor contactors 208 and 210 in 
conjunction with activation of switch 34 to provide for motor directional 
control to hoist or lower a payload. 
MODE OF OPERATION 
The hoist 10 is mounted vertically or horizontally on an appropriate 
mounting surface such as including mounting on a ceiling or any other 
predetermined location. The reversible motor 26 is activated by a hoist 
operator by first selecting the direction the drum is to rotate by 
depressing switch 36 on the control pendant 32 and then depressing the 
momentary power switch 34, also called a dead-man safety switch, to 
deliver electrical power to the reversible motor 26. Helical pinion 62 is 
rotated by the motor shaft 50 to turn the helical gear 72 and the worm 
shaft 64. 
In a hoisting operation the worm drive 86 on the worm shaft 64 turns the 
worm gear 88, the drum shaft 90 and the drum 12. The one-way clutch 76 
free-wheels within the brake drum 81, and the brake drum 81 is held 
stationary by the brake band 82 and brake lining 84. The clutch 76 is 
always ready to be automatically engaged against motion reversal when the 
worm shaft 64 motion ceases, either during a mid-hoisting operation to 
hold the payload in a static position should electrical power be 
interrupted by electrical failure or operator diversion, a safety 
function, or when the operator normally releases switch 34 when the 
payload reaches its desired level. Friction between the worm gear 88 and 
the worm drive 86 also assists in holding of a hoisted payload. 
Lowering of the payload is accomplished by activating switch 36 and 
subsequently switch 34 to reverse the motor direction, and thus, the 
rotational direction of the drum 12. At this time, the free-wheeling 
motion of the one-way clutch 76 ceases and the shaft 64 is frictionally 
engaged to the brake drum 81 through the one-way clutch 76. The worm shaft 
64, the one-way clutch 76 and the brake drum 81 turn as a unit to overcome 
the friction caused by the brake band 82 and brake lining 84 against the 
brake drum 81, allowing the worm drive 86 to drive the worm gear 88, drum 
shaft 90 and drum 12 to lower a payload. 
The clutch and brake system provide for braking which is more positive than 
brake systems which rely upon worm gear friction exclusively. The swaged 
fitting 182 on the wire rope 180 is frictionally engaged in the wire rope 
key hole 142 as opposed to pinching and weakening the wire rope 180 under 
a clamp arrangement. The ramped surface 140 adjacent to the wire rope key 
hole 142 assist in orienting of the wire rope 180 around and about the 
drum 12. 
Various modifications can be made to the present invention without 
departing from the apparent scope thereof.