U.S. patent number 3,788,575 [Application Number 05/244,065] was granted by the patent office on 1974-01-29 for automatic and semi-automatic reel tenders.
Invention is credited to Clifford T. Boettcher, David O. Creasman, deceased.
United States Patent |
3,788,575 |
Boettcher , et al. |
January 29, 1974 |
AUTOMATIC AND SEMI-AUTOMATIC REEL TENDERS
Abstract
An automatic reel tender especially adapted for use in
underground cable laying operations employs a positive cable reel
drive whose operation is modulated as a function of varying cable
tension to match mean cable pay-out with advancement of the cable
laying equipment. A hydraulic motor is in positive driving
engagement with the cable supply reel and modulation of the same
may be effected either by varying motor speed as a substantially
instantaneous function of cable tension or by intermittant driving
of the same. In either event, a unit-handled mechanical tensiometer
is relied upon to sense cable tension. A tensiometer feedback,
which may be either mechanical or electrical, controls modulation
of the cable reel drive. The automatic reel tender also includes an
overload relief mechanism to ameliorate cable damage in the event
of an uncontrolled increase in cable tension as well as a
hydraulic, dynamic braking capability for dissipating inertial reel
rotation upon termination of the positive drive. The semi-automatic
reel tenders herein disclosed rely upon a manual control to effect
the positive cable reel drive while retaining one or more of the
automatic safety features associated with the fully automatic reel
tender.
Inventors: |
Boettcher; Clifford T.
(Asheville, NC), Creasman, deceased; David O. (Candler,
NC) |
Family
ID: |
22921242 |
Appl.
No.: |
05/244,065 |
Filed: |
April 14, 1972 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
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100059 |
Dec 21, 1970 |
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Current U.S.
Class: |
242/390.6;
242/397.2; 242/403; 242/422.2; 242/615.2; 405/177; 405/183 |
Current CPC
Class: |
H02G
1/06 (20130101); B65H 59/38 (20130101) |
Current International
Class: |
H02G
1/06 (20060101); B65H 59/38 (20060101); B65H
59/00 (20060101); B65h 075/40 (); B65h 059/00 ();
B65h 059/38 () |
Field of
Search: |
;242/86.5,86.7,75.3,75.53 ;61/72.6 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Huckert; John W.
Assistant Examiner: McCarthy; Edward J.
Attorney, Agent or Firm: Colton & Stone, Inc.
Parent Case Text
CROSS REFERENCE TO RELATED APPLICATION
This is a continuation-in-part of application Ser. No. 100,059,
filed Dec. 21, 1970, abandoned.
Claims
We claim:
1. In combination with a vehicle mounted cable layer including a
cable supply reel and a cable laying guide, the improvement
comprising; a rotary hydraulic motor for rotating said reel; geared
drive means comprising a sprocket chain and a sprocket gear
intercoupling said rotary hydraulic motor and cable supply reel; a
fluid circuit having supply and exhaust lines and a source of fluid
pressure for operating said motor; control means for controlling
rotation of said reel by said motor; said control means including
valve means for controlling said supply and exhaust lines; said
fluid circuit including first and second cross-over fluid lines
interconnecting said supply and exhaust lines at positions
intermediate said valve means and motor; said first cross-over line
including pressure relief means for short circuiting said motor to
relieve excessive pressure on one side of said motor when said
source of fluid pressure is in fluid communication with said motor;
and said second cross-over line including pressure relief means for
short circuiting said valve means to effect dynamic braking of the
motor connected reel when fluid communication between said source
of fluid pressure and motor is blocked at said valve means.
2. The combination of claim 1 including a third fluid line
interconnecting said supply and exhaust lines for short circuiting
said motor; said control means including a tensiometer for sensing
cable tension; and cable over-tension control means responsive to a
first cable tension range for blocking short circuit flow through
said third fluid line and to a higher cable tension range for
establishing short circuit flow.
3. The combination of claim 2 including fluid flow control means in
fluid circuit between said pressure source and motor; and first
feedback means interconnecting said tensiometer and fluid flow
control means for proportioning fluid flow to said motor as a
function of cable tension.
4. The combination of claim 3 including second feedback means
intermediate said tensiometer and valve means for blocking and
establishing fluid flow through said supply and exhaust lines as a
function of cable tension.
5. The combination of claim 4 wherein said first feedback comprises
a mechanical feedback and said second feedback comprises an
electrical feedback.
6. The combination of claim 1 including means for manually
operating said valve means; a third fluid line interconnecting said
supply and exhaust lines; and cable over-tension control means for
controlling flow through said third line as a function of cable
tension.
7. An automatic reel tender, comprising; a portable vehicle
supporting a cable supply reel; cable guide means mounted on said
vehicle defining at least one variable cable run between said
supply reel and a point of cable use; power means in positive
driving engagement with said reel for concomitantly varying cable
tension and the path length of said cable run; sensing means
mounted on said vehicle for sensing cable tension as an inverse
function of cable run path length; and control means responsive to
said sensing means for controlling said power means.
8. An automatic reel tending cable layer, comprising; a cable
laying vehicle including subterranean cable laying equipment; a
cable supply reel carried by said vehicle; said cable laying
equipment including cable guide means defining at least one
variable cable run between said supply reel and a subterranean
location; power means in positive driving engagement with said
supply reel; sensing means mounted on said vehicle for sensing
variations in said path length; and control means responsive to
said sensing means for controlling operation of said power means in
response to variations in said path length.
9. The cable layer of claim 8 wherein said sensing means comprises
a tensiometer mounted adjacent said cable run for deflecting
movement thereby in response to a decrease in said path length; and
said tensiometer being biased for movement in a direction opposite
to said deflecting movement whereby increases in said path length
are reflected by movement of the tensiometer in said opposite
direction.
10. The cable layer of claim 9 wherein said power means comprises a
rotary hydraulic motor; said control means including first
hydraulic and electric control circuits; and said first electric
control circuit including switch means responsive to movement of
said tensiometer for controlling said first hydraulic circuit.
11. The cable layer of claim 10 wherein said first hydraulic
control circuit includes a source of hydraulic pressure, supply and
exhaust lines interconnecting said source of pressure with said
motor, and a valve for blocking and establishing flow through said
supply and exhaust lines; a second hydraulic control circuit
interconnecting said supply and exhaust lines for short circuiting
said motor in response to uncontrolled increases in cable tension;
a valve in said second hydraulic control circuit for selectively
blocking and establishing short circuit fluid flow therethrough;
and a second electrical control circuit responsive to movement of
said tensiometer for operating said last named valve.
12. The cable layer of claim 9 wherein said tensiometer comprises a
leaf spring assembly supporting a cable guide; and said cable run
engaging said cable guide.
13. The cable layer of claim 9 wherein said tensiometer comprises a
cable guide mounted for pivotal deflecting movement about a fixed
pivot axis.
14. A reel tending cable layer comprising; a cable laying vehicle
including subterranean cable laying equipment; a cable supply reel
carried by said vehicle; a cable extending from said supply reel to
a subterranean location; said cable laying equipment including
cable guide means defining at least one variable cable run between
the supply reel and subterranean location; a rotary hydraulic motor
in positive drive transmitting engagement with said supply reel; a
source of hydraulic pressure; supply and exhaust lines
interconnecting said source of pressure and said motor; a valve
controlling said supply and exhaust lines for controlling the
operation of said motor; and at least one valved fluid conduit
interconnecting said supply and exhaust lines.
15. The cable layer of claim 14 wherein said rotary hydraulic motor
is geared to said supply reel; and at least two valved fluid
conduits interconnect said supply and exhaust lines.
16. The cable layer of claim 15 including three valved fluid lines
interconnecting said supply and exhaust lines; one valve in one of
said fluid lines being biased to open communication between the
supply and exhaust lines; sensing means mounted on said cable layer
for sensing a range of normal operating variations in the path
length of said variable cable run; and circuit means responsive to
said range of normal operating variations for overriding said bias
to maintain said one valve closed.
17. A cable layer incorporating an automatic reel tender,
comprising; a portable vehicle, a cable supply reel carried by said
vehicle, subterranean cable laying equipment carried by said
vehicle; said cable laying equipment including cable guide means
defining at least one unsupported cable run between said supply
reel and a subterranean location; power means for varying the path
length of said unsupported run; sensing means mounted on said
vehicle for sensing a decrease in said path length; means
responsive to said sensing means for activating said power means to
increase said path length and reduce cable tension; and said
sensing means including a cable engaging arm biased to a position
intersecting a vertical plane containing said run.
18. The cable layer of claim 17 wherein said power means includes a
prime mover; and a geared connection between said prime mover and
said supply reel.
19. A cable layer incorporating an automatic reel tender,
comprising; a portable vehicle, a cable supply reel carried by said
vehicle, subterranean cable laying equipment carried by said
vehicle; cable guide means for guiding a cable from said supply
reel to a subterranean location; said guide means defining at least
two spaced cable guides between said reel and said subterranean
location; a cable wound on said reel and engaging said spaced cable
guides defining therebetween an unsupported cable run; power means
for varying the path length of said unsupported cable run between a
minimal run defined by a straight line between the cable engaging
portions of said guides and a longer run as defined by a catenary
suspension of said run between said guides; sensing means including
a rigid support bracket mounted on said vehicle between said
guides; said sensing means further including a cable engaging arm
mounted for compound pivotal movement relative to said support
bracket between a first cable tension sensing position overlying
the longer catenary suspension of said cable and a second overload
relief position pivotally displaced therefrom; and control means
responsive to said sensing means for activating said power means to
increase the path length of said run.
20. A cable layer incorporating an automatic reel tender,
comprising; a portable vehicle; a cable supply reel, subterranean
cable laying equipment carried by said vehicle; cable guide means
carried by said vehicle for guiding a cable from said supply reel
to a subterranean location; a fluid motor; a positive driving
connection between said motor and said reel; tension sensing means
carried by said vehicle for sensing cable tension; and control
means responsive to said sensing means for driving said motor in
the reel pay-out direction.
21. The cable layer of claim 20 wherein said guide means include
spaced cable guides for supporting an unsupported cable run
therebetween between the supply reel and said underground location;
and said sensing means including means for detecting a decrease in
cable slack between said spaced cable guides.
22. The cable layer of claim 21 wherein said fluid motor includes
pressure and exhaust lines; a fluid pump; said control means
including valve means for selectively communicating pump pressure
to said pressure line and blocking said pressure and exhaust lines;
and cross line relief means for intercommunicating said pressure
and exhaust lines between said valve means and motor whereby said
motor may act as a pump to recycle fluid under the influence of
inertial reel rotation when said pressure and exhaust lines are
blocked at said valve means.
Description
BACKGROUND OF THE INVENTION
The manufacturers of underground cable laying equipment wherein
cable is buried simultaneously with the formation of a slit trench
have long taken advantage of the fact that the buried cable will
provide sufficient anchorage to unreel the supply cable.
Unfortunately, this same anchorage is normally sufficient to resist
the imposition of cable breaking tensions. Such tensions may be
applied, for example, in overcoming initial reel inertia or in the
common occurrence of an idling supply reel commencing to rotate in
the rewind direction as permitted by a slack run between the reel
and trench. Additionally, many cables and particularly telephone
cables are highly sensitive to applied tensions below the breaking
point.
The long standing solution to the problem of excessive cable
tension has been the use of an extra man riding with the equipment
to manually pay-out the supply reel, as required. Recent attempts
to automate this function have involved the use of frictional
drives applied, on the one hand, to the cable itself which merely
transfers the overtension or cable breakage point and, on the other
hand, to the reel rims which not only requires adjusting mechanisms
to accommodate different size reels, but, also, fails to take into
account the fact that cable reel rims in actual use are seldom
round by reason of damage, breakage and the like. In this latter
respect, wooden cable reels are normally constructed of the
cheapest quality lumber and are routinely handled in a rough manner
both in storage and deployment. Cable reels are frequently designed
to be reusable and the pick-up and handling of spent reels,
particularly as they are dropped onto the ground from a truck,
provides almost complete assurance that their most vulnerable
portions, the rims, will not present a smooth, circular
circumference. Thus one or more "flats" and/or missing rim slats
providing a break of several inches in the circular continuity of
one or both reel rims, are quite common. Steel reel rims are
similarly subject to damage as by peripheral indentions due to
droppage.
An even greater deficiency in any frictionally driven supply reel
whether the frictional drive be applied to the cable or reel is the
practical impossibility of using such a system with the larger type
reels where the likelihood of cable breakage is also present.
Exemplary are some of the larger cable laying reels in common use
which have a wound supply weight of 10,000 pounds on a 9 foot reel.
In the case of certain lead sheathed 4 inch diameter 3/0 electrical
conductor cable; a loaded 9 foot supply reel weighs 17,000 pounds.
The application of a sufficient starting torque through a
frictional drive to overcome the stationary inertia of a reel of
this size is simply not practical and, in the case of the
frictional drive being applied directly to the cable, it will be
appreciated that even if the reel inertia could be overcome within
practical time limits the total starting torque would be applied to
the reel via the cable which is precisely the circumstance to be
avoided.
Prior to the instant invention it was thought to be necessary to
employ a frictional reel drive as opposed to a positive drive if
the obvious disadvantages inhering in the use of an automatic heavy
duty clutch were to be avoided. This for the reason that
uncontrolled reel rotation, as by its own inertia, must not be
allowed to damage the driving mechanism. Similarly, in the case of
an uncontrolled increase in cable tension it is desirable that the
mechanism for sensing such tension not be damaged.
SUMMARY OF THE INVENTION
The invention, as related to fully automatic reel tenders, is
broadly directed to a positive drive mechanism for a supply reel
operable as a function of paid-out cable tension. More
specifically, a unit-handled tensiometer which may be readily
attached to existing equipment provides a mechanical or electrical
feedback indicative of cable tension which feedback controls the
operation of the drive mechanism.
It will thus be immediately apparent that the broad inventive
concept, particularly as regards the unit-handled tension sensing
unit per se, possesses obvious utility far beyond the specific
environment herein illustrated.
Inasmuch as the massive tension forces involved in commercial cable
laying operations present a number of problems not normally
associated with other environments where the invention finds
utility such as in the recovering of overhead cables or the like;
the application of the invention to cable laying equipment has been
chosen for illustration.
It is the primary object of the invention to provide a positive
pay-out drive for a cable reel which may be operative as a function
of cable tension in a fully automatic manner or under the manual
control of an operator.
Secondary aspects of the invention reside in the details of
driving, sensing, and safety systems as applied to automatic reel
tenders while a tertiary aspect relates to semi-automatic reel
tenders employing sensing and safety features similar to those
utilized with the automatic reel tenders.
The positive drive derives from a hydraulic motor and related
circuitry, including a hydraulic overload relief with dynamic
braking capability, which may be installed directly on existing
cable laying equipment. The unit-handled tensiometer may also be
installed on existing equipment and the incorporation of these two
subassemblies with conventional idle reel cable layers may thus be
economically effected to convert the same into either automatic or
semi-automatic reel tenders as disclosed herein.
A preferred embodiment of the invention includes a hydraulic, cable
over-tension relief feature while in an alternate construction a
mechanical, cable over-tension relief is incorporated with the
mechanical tensiometer.
The use of a hydraulic motor insures that sufficient torque will be
available to overcome stationary reel inertia. The hydraulic
overload relief is constituted by a cross-over relief which not
only dumps excessive system pressure to reservoir during normal
motor operation but, also, permits the motor to act as a pump and
provides dynamic braking for inertial reel rotation following
termination of the positive drive in response to a cable slack
condition as sensed by the tensiometer.
DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side elevation of a trailing cable layer incorporating
an automatic reel tender in accordance with one embodiment of the
invention;
FIG. 2 is a detail perspective illustrating the tensiometer
mounting of FIG. 1;
FIG. 3 is a similar perspective view taken from the opposite side
of FIG. 1;
FIG. 4 is a schematic representation of the tensiometer, cable reel
drive and associated circuitry for converting an idle reel cable
layer into an automatic reel tending cable layer in accordance with
one aspect of the invention;
FIG. 5 is an elevational depiction of a tractor mounted cable layer
in accordance with a second modification of the invention;
FIG. 6 is a side elevation of a trailing cable layer employing a
tensiometer similar to the type shown in FIG. 5;
FIG. 7 is a hydraulic diagram of the reel driving circuit of FIGS.
5 and 6;
FIG. 8 is a simplified hydraulic circuit lacking the hydraulic
cable over-tension relief feature that may be substituted for the
circuit of FIG. 7;
FIG. 9 is a side elevational view of a tractor mounted cable layer
incorporating a further embodiment of the invention;
FIG. 10 is an elevational view of the tensiometer as viewed along
line 10--10 of FIG. 9 illustrating a slack cable condition;
FIG. 11 is a similar view illustrating, in solid lines, a normal
tensioned cable position for actuating the reel drive mechanism
and, in phantom, the operation of the mechanical cable over-tension
relief mechanism; and
FIG. 12 is a schematic representation of the sensing unit, cable
reel drive and associated circuitry necesssary to convert an idle
reel cable layer into the automatic reel tending cable layer of
FIG. 9.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
A preferred embodiment of the automatic reel tender wherein both
the cable supply reel and tensiometer are mounted on a towed cable
layer is illustrated in FIGS. 1-4.
In FIG. 1 is illustrated, in cable laying position, a trailed cable
layer 10 adapted to be towed in conventional manner by a traction
unit, not shown. Cable layer 10 includes a cable supply reel 12
from which cable 14 is paid out to pass over idle pulley 16 of a
unit-handled tensiometer 18 and thence through a conventional cable
guide 20 trailing a conventional slit trencher 22. The run of cable
14 across tensiometer pulley 16 is desirably maintained between the
solid and dotted line positions of FIG. 1 through the coaction of
tensiometer 18 and a positive cable reel drive 24. The cable reel
is driven by an hydraulic motor 26 whose maximum cable pay-out
capacity, as determined by the drive chain connected sprockets 28,
30, exceeds the cable laying rate of the equipment.
Reel 12 is illustrated in FIG. 1 as comprising a conventional
wooden reel from which one tie bolt 32 has been removed for receipt
in a tie bolt opening thereof a reel pin adapter 34 whose outer
threaded end is removably secured to a reel anchor bar 36 rigid
with sprocket 30. Motor output sprocket 28, drive chain 38 and reel
anchor sprocket 30 are mounted within housing 40 rigidly supported
at the outer end of one of lift arms 42 just outboard of reel 12.
Reel 12 is, of course, mounted for rotation on the usual reel axle
shaft bridging the ends of lift arms 42 but the rotation thereof
about the axis of the axle shaft is positively controlled by cable
reel drive 24 through the interconnection of reel anchor bar 36
with the reel via reel pin adapter 34.
Tensiometer 18 includes an upstanding, rigid mast 44 to the lower
end of which is secured a normally bowed leaf spring assembly 46
mounting, at the upper free end thereof, the idle pulley 16. The
unit handled tensiometer may be secured to the cable layer frame as
by welding or the like of mast 44 adjacent the lower end thereof,
to frame structure 48 to position idle pulley 16 in spaced relation
to the cable supply reel. A chain 49 interconnected between the
upper end of mast 44 and the cable layer frame completes the
tensiometer mounting. A rigid guide loop 50 constrains cable 14 to
a desired path across pulley 16 enroute to cable guide 20. The
unstressed condition of leaf spring 46 is illustrated in solid
lines in FIGS. 1 and 4, while the phantom line position indicates
the usual relationship of parts during a cable laying operation
wherein the degree of rearward spring assembly flexure is a
function of cable tension. Thus, as will be apparent from FIG. 1,
idle pulley 16 is biased by leaf spring assembly 46 to guide cable
14 in an arcuate path from supply reel 12 to cable guide 20. As
cable tension increases, the path of the cable run starts to
straighten between the supply reel and cable guide with a
concomitant flexure of the leaf spring assembly toward the phantom
line position of FIGS. 1 and 4. Thus, leaf spring assembly flexure
is a direct function of cable tension and, in the embodiment of
FIGS. 1-4, both electrical and mechanical feedbacks from the
varying positions of the leaf spring assembly are used to control
cable pay-out.
A switch mounting bracket 52, rigid with mast 44, mounts a pair of
microswitches 54, 56 whose actuation is controlled by flexing
movement of leaf spring assembly 46 into and out of engagement with
switch actuators 58, 60. Switch 54 is the hydraulic motor control
switch and is a normally closed switch held open by leaf spring
assembly 46 engaging switch actuator 58 in the unstressed solid
line position of FIGS. 1 and 4. Thus, with insufficient tension in
cable 14 to flex the leaf spring assembly, switch 54 remains open
and hydraulic motor 26 is not energized. This would be the
situation upon cessation of cable laying operations. Switch 56 is
normally open with respect to its motor control terminals 57 (FIG.
4) but is held closed with respect to terminals 57 by leaf spring
assembly 46 engaging switch actuator 60 in all positions of leaf
spring flexure falling within normal cable laying operating
parameters. Switch 56 will not go closed until actuator 60 has
rotated approximately 30.degree. from the position of FIG. 2 as the
leaf spring assembly flexes beyond the phantom line position of
FIGS. 1 and 4 which would indicate some emergency condition wherein
cable tension is increasing without limit. Such a condition would
be exemplified by a failure of the hydraulic control circuit to
supply fluid to motor 26 so that continued forward movement of the
cable layer would impose supply reel pay-out forces directly on
cable 14. When this occurs, switch 56 goes open and the hydraulic
motor is short circuited so that the motor simply acts as a
recycling pump as will be more fully explained in connection with
the circuit diagram of FIG. 4.
In one exemplary application the leaf spring assembly is
constructed to yield to the approximate phantom line position of
FIG. 1 under an applied cable tension of approximately 4 pounds
under which conditions switch 54 is closed and motor 26 is driving
supply reel 12 in the pay-out direction. It is only upon a
substantial further increase in applied cable tension, as on the
order of 10 pounds for example, that leaf spring assembly 46 flexes
well beyond the phantom line position of FIG. 1 to allow switch 56
to open and short circuit the motor.
A third feed-back from the flexed position of leaf spring assembly
46 is effected, mechanically, through a sprocket chain 62 which has
one end anchored to the leaf spring assembly while the other end
thereof is interconnected with a rigid anchor adjacent mast 44
through a tension spring 64. Sprocket chain 62 is in driving
engagement with a sprocket 66 rigid with adjusting shaft 68 of a
conventional priority type, pressure compensated flow regulator 70
which is in hydraulic circuit with motor 26. Rotation of adjusting
shaft 68 as a consequence of leaf spring flexure modulates fluid
flow to motor 26 thus adjusting the pay-out speed of supply reel 12
as will be more fully explained in the description of FIG. 4.
A one-way damping cylinder 72 is interconnected between mast 44 and
leaf spring assembly 46 to damp movement of the leaf spring
assembly toward the mast while permitting free, undamped flexing
movement of the leaf spring assembly away from the mast (to the
right as viewed in FIG. 1).
The complete motor control circuit and the manner in which the same
is related to tensiometer 18 is illustrated in FIG. 4. The existing
hydraulic circuitry normally associated with a conventional cable
layer is indicated in dotted lines and the priority type flow
regulator 70 is in circuit therewith to divert variable proportions
of the output from pump 74 to a conventional solenoid operated
valve 76 controlling the input to motor 26 and to reservoir 78.
When valve 76 is closed, as shown in FIG. 4, flow through the valve
is dumped to reservoir. Upon closure of switch 54, valve 76 is
activated to pressurize line 80 and communicate line 82 with
reservoir to rotate motor 26 in the pay-out direction.
A cross-line relief 84 is connected across lines 80 and 82 to
provide a hydraulic pressure relief and dynamic braking feature for
the positive drive system. The cross-line relief includes
differentially biased relief valves 88, 90 which may, for example,
be set to relieve 400 p.s.i. and 1,500 p.s.i., respectively, as
applied from the motor side of the valves. Relief valve 90 is
operative when motor 26 is being driven to dump excessive pressure
surges in line 80 to reservoir via cross-over line 92 and conduit
82. When cable tension decreases to open switch 54 and block the
motor control circuit at valve 76; reel 12 continues to rotate
under its own inertia which, of course, rotates the rotor of motor
26 causing the same to act as a pump. It is at this point that
relief valve 88 comes into play by yielding to recycle pressurized
fluid from line 82 through cross-over line 94 and back to the
intake of the motor/pump. This has a dynamic braking effect on reel
12 as the kinetic energy of rotation is dissipated, primarily
through heat losses, at relief valve 88.
A further advantage in the cross-line relief arrangement is that it
permits cable to be manually unreeled at a controlled tension
which, in the case of the illustrated parameters, would be
approximately 12 pounds. In such situation, the motor again acts as
a pump and is relieved through cross-over line 94. This is
particularly advantageous in certain emergency situations such as
in the case of a complete power loss.
A conventional double pole, double throw toggle switch 96 and
manually operable rewind and pay-out switches 98, 100 are provided
whereby valve 76 may be manually rather than automatically
controlled. As will be apparent, switches 98 and 100 may be brought
into circuit for manually controlling the reversible operation of
motor 26.
A hydraulic cable over-tension relief 102 is built into the motor
circuit to provide an unrestricted short circuit across the motor
in contradistinction to the cross-line or hydraulic overload relief
84 which includes resistances in the cross-over lines. A
conventional solenoid operated valve 104 alternately blocks and
opens a short circuit 106 across motor supply and exhaust conduits
80, 82 on the motor side of the cross-line relief 84. Valve 104 is
spring biased toward the open, dotted line position of FIG. 4 but
is held in the upper closed position of FIG. 4, blocking short
circuit flow through lines 106, by the energization of solenoid 108
controlled by microswitch 56. Thus should cable tension increase
beyond normal limits, i.e., sufficient to flex leaf spring assembly
46 past the dotted line position of FIGS. 1 and 4; the leaf spring
moves out of engagement with switch actuator 60, switch 56 opens
across terminals 57 to deenergize solenoid 108 and valve 104 opens
(dotted line position of FIG. 4) to short circuit motor 26 so that
continued reel rotation simply pumps fluid about circuit 106.
In operation, and assuming the solid line position of FIGS. 1 and 4
wherein cable layer 10 is stationary and cable 14 is under
substantially zero tension; as cable layer 10 starts to move
forwardly, cable tension increases to flex leaf spring assembly 46
toward the dotted line position of FIGS. 1 and 4.
Immediately upon movement of leaf spring 46 away from the solid
line position; switch 54 goes closed to energize solenoid 110 and
communicate motor 26 with pump 74 via valve 76 and motor supply
line 80 while exhausting motor 26 via line 82 to reservoir.
Simultaneously, flow control valve 70 is adjusted via sprocket 66
to deliver a greater proportion of the pump output to motor supply
line 80. Flow control valve 70 is a commercially available unit
known as a priority type flow regulator and manufactured by Fluid
Power Systems, a division of AMBAC Industries, Inc. of Wheeling,
Illinois under Model designation 13-15-3.
Under normal operating conditions of less than 10 pounds cable
tension for example, flexure of leaf spring assembly 46 past the
dotted line position of FIGS. 1 and 4 does not take place and
actuator 60 of switch 56 remains in contact with the leaf spring to
keep switch 56 closed across terminals 57 energizing solenoid 108
and blocking short circuit flow around motor 26 at valve 104. As
the cable laying operation proceeds, instantaneous increases in
cable tension are reflected by an increased input to motor 26 as
the deflection of leaf spring 46 rotates adjusting shaft 68 to
direct a greater proportion of pump flow through control valve 76
to the motor. One-way damping cylinder 72 damps the return of leaf
spring 46 toward the solid line unstressed condition while tension
spring 64 insures that valve control adjusting shaft 68 will
faithfully reflect the damped return of the leaf spring to decrease
fluid input to the motor as cable tension decreases. If the advance
of cable layer 10 be terminated, the unwinding inertia of reel 12
slacks cable 14, leaf spring assembly 46 returns to the solid line
position of FIGS. 1 and 4 to open switch 54 deenergizing solenoid
110 and allowing self centering valve 76 to divert all flow to
reservoir thus blocking motor lines 80, 82. The inertial movement
of reel 12 is then damped by recirculation flow through cross-line
relief 84 as already explained. This is the normal mode of
operation.
Under conditions of increasing cable tension beyond normal
operating parameters such as, for example, if a failure of solenoid
110 should result in blocking flow through motor lines 80, 82 while
the cable layer is still advancing; leaf spring assembly 46 will
deflect beyond the phantom line position of FIGS. 1 and 4 thus
allowing switch 56 to open terminals 57 to thereby deenergize
solenoid 108 and permit valve 104 to assume its normal open
position opening short circuit 106 around motor 26. Continued
advancement of the cable layer will then result in continued
unwinding movement of reel 12 via the tension applied thereto
through cable 14 while motor 26 acts as a recirculating pump. This
short circuit 106 allows the continued advancement of the cable
layer with the imposition of a lesser cable tension than would be
realizable if the cross-line relief section of the circuit were
relied on for the function since it includes the previously
discussed resistance factors desirable for dynamic braking.
Simultaneously with the opening of terminals 57 in switch 56,
auxiliary terminals 107 are closed to sound an alarm, herein
illustrated as a horn 109, to alert the operator to stop
advancement of the traction unit.
In the absence of the wiring for an alarm circuit, as just
described, switch 56 may simply include a pair of stops at the
position of terminals 107. It will be apparent that the wire
trigger switch actuator 60 and its interconnected rotary actuator
111 are biased for movement toward the dotted line position of FIG.
4 and so dimensioned that recess 113 permits the contacts 57 to be
opened only after the deflection of leaf spring assembly past the
phantom line position of FIG. 4.
The semi-automatic reel tenders shown in FIGS. 5 and 6 retain the
positive cable reel drive feature as well as the cross-line and
cable over-tension relief feature described in connection with
FIGS. 1-4 but rely upon manual control of the hydraulic motor
driving the supply reel as will be apparent from the abbreviated
circuit configuration of FIG. 7.
The semi-automatic reel tender shown in FIG. 5 includes a tractor
112 having a forwardly mounted supply reel 114, a rearwardly
mounted slit trencher 116 and a trailing cable guide 118. During
the course of a normal cable laying operation as illustrated in
FIG. 5, the run of cable 120 is desirably maintained deflected from
a straight line run between supply reel 114 and idle pulley 122 by
an idle sensing pulley or tensiometer 124 which is biased to
deflect cable 120 by a tension spring 126. A normally open
microswitch 128 is held closed by the idle sensing pulley support
arm 130 within the normal cable tension operating parameters as
selected by the bias of spring 126 and permitted to go open as arm
130 moves upwardly in response to increasing cable tension to
approach a straight line run between reel 114 and idle pulley 122.
The cable reel mounting to the ends of lift arm 132 and the
positive drive thereof by hydraulic motor 134 is identical to that
described in connection with FIGS. 1-4. The control of power fluid
to motor 134 is via a manually controlled, normally centered valve
136 as shown in FIG. 7. Thus, manual actuation of valve 136 to move
the control spool downwardly from the position of FIG. 7 places
motor supply conduit 138 in communication with pump 140 and vents
exhaust line 142 to reservoir. The configuration and operation of
cross-line relief 144 is identical with that described in
connection with FIG. 4 as is the operation of the cable
over-tension relief defined by the short circuit conduit 146 which
is normally blocked by solenoid operated valve 148 whose operation
is identical to that of valve 104 in FIG. 4. In further
explanation, the cable over-tension relief valve acts, in effect,
as a "deadman" control in that it is a biased, normally open valve
to establish flow through short circuit 146 and is held closed by
the energization of solenoid 150 when cable tension is normal (as
in FIG. 5) and switch 128 is held closed by arm 130. When cable
tension increases to elevate arm 130, as when the operator holding
valve 136 to establish flow communication with motor 134 fails to
take note of increasing cable tension, switch 128 opens
deenergizing solenoid 150 and valve 148 goes to the dotted line
position of FIG. 7 thus short circuiting the reel drive motor.
The semi-automatic control features of the trailed cable layer 152
shown in FIG. 6 are identical with those of FIG. 5 and the
hydraulic circuitry is that shown in FIG. 7. The only distinction
is in the rearward mounting of the supply reel and the positionment
of idle sensing pulley 154 to hold the normally open switch 156
closed under condition of normal cable tension. Switch 156, of
course, controls the energization of the cable over-tension relief
solenoid 150 (FIG. 7).
A hydraulic schematic of a further simplified semiautomatic version
of the invention is illustrated in FIG. 8 wherein the cable
over-tension relief has been omitted and the cross-line relief 158
performs this function in addition to its dynamic braking function,
as previously described. The circuit of FIG. 8 may be substituted
for that of FIG. 7 as applied to either of the embodiments shown in
FIGS. 5 and 6 with the obvious modifications that the cable tension
sensing pulleys 124, 154 and their associated switches 128, 156 are
eliminated.
In operation of the embodiment shown in FIG. 8, positive reel
rotation is effected by manual manipulation of control valve 160
and cable over-tension is relieved via the cross-line relief 158
albeit at the sacrifice of relieving at a lower tension through a
short circuit across the motor which does not include the
resistance built into the cross-line relief as will be explained in
greater detail with regard to an identically functioning cross-line
relief in FIG. 12.
A further embodiment of a fully automatic reel tender is
illustrated in FIGS. 9-12 and differs from that of FIGS. 1-4
primarily in the details of the tensiometer and the substitution of
a mechanical cable over-tension relief. The mechanical over-tension
relief is primarily to protect the tensiometer from damage rather
than to effect continued cable over-tension relief which is
provided for by a hydraulic cross-line relief.
The automatic reel tender depicted in FIG. 9 includes a tractor 162
having a forwardly mounted cable supply reel 164, a rearwardly
mounted slit trencher 166 and a trailing cable guide 168. During
the course of a normal cable laying operation as illustrated in
FIG. 9, the run of cable 170 between idlers 172, 174 is desirably
maintained between the solid and dotted line positions through the
coaction of a tensiometer 176 and a positive cable reel drive 178.
The cable reel is driven by a single speed hydraulic motor 180
whose cable pay-out capacity, as determined by the drive chain
connected sprockets 182, 184 exceeds the cable laying rate of the
equipment. Reel 164 is herein illustrated as a conventional steel
reel having the usual aligned diametral straps 186 having aligned
openings formed therein for the receipt of reel mounting shaft 188.
Drive mechanism 178 is mounted in housing structure 190 rigidly
supported on one lift arm 192 just outboard of one reel strap 186.
A drive strap 194 is integrally secured to driven sprocket 184 as
by an integrally related sleeve or the like for rotation therewith
and includes means for securing the same to the adjacent reel strap
186 which is herein illustrated as a chain 196 having one end
thereof secured to the distal end of drive strap 194. Chain 196 may
be wrapped about reel strap 186 and secured in any desired manner
to positively couple reel 164 to the output shaft of hydraulic
motor 180.
Tensiometer 176 includes a support frame 198 adapted for rigid
securement to tractor 162, as by welding or the like, intermediate
idlers 172, 174. A generally L-shaped bracket 200 including a
depending switch mounting arm 202 and a generally horizontal arm
204 extending beneath cable 170 is mounted for limited pivotal
movement about the axis of pivot 206 between the positions shown in
FIGS. 10 and 11 under the opposed influences of the varying tension
in cable 170 sensed as a function of the variable catenary path
between idlers 172, 174 and a return compression spring 208.
Normally open microswitch 210, carried on bracket arm 202, is
adapted to be closed upon counter-clockwise rotation of bracket 200
to the FIG. 11 position by engagement with an arm 212 depending
from frame 198 which engagement, also, limits the permissible
counterclockwise movement of bracket 200. An adjustable stop 214
limits return clockwise movement of the same under the bias of
spring 208 to that position shown in FIG. 10. The outer end of arm
204 includes an integral U-shaped cable guide 216 upon one leg of
which is pivotally mounted, at 218, an L-shaped overload release
member 220 one of whose arms 222 is biased to bridge the open end
of cable guide 216 by a tension spring 224 reacting between the
other leg 226 thereof and an extension of fixed pivot 206.
Springs 208 and 224 are differentially biased to yield upon the
application of upward force components as transmitted thereto by a
decrease in the path length or slack condition of cable 170 between
idlers 172 and 174 which decrease in slack condition or path length
is a direct function of increasing cable tension. In one exemplary
application, springs 208 and 224 are selected to yield in response
to applied cable tensions of 4 and 10 pounds, respectively, as
applied thereto by cable 170 moving upwardly against overload
release arm 222. Thus, assuming the solid line, cable slack
condition of FIGS. 9 and 10, the reel 164 stationary and a
trenching operation in progress; the slack run will be taken up and
cable 170 will move upwardly toward the dotted line position of
FIG. 9 and the solid line position of FIG. 11 as a function of
increasing cable tension. As cable tension reaches 4 pounds, the
upward force component acting through overload release member 220
overcomes the bias of spring 208 to pivot bracket 200
counterclockwise about pivot 206 and close switch 210 to drive reel
164 in a manner which will be subsequently explained. Since the
driven pay-out speed of reel 164 exceeds trenching speed, the solid
line slack condition of FIG. 9 will be restored allowing spring 208
to return bracket 200 to the position of FIG. 10 thus opening
switch 210 and stopping the reel drive until cable tension again
increases to 4 pounds. Because of its much higher bias, spring 224
acts as a rigid link in the sequence of movements just described
and only comes into play should some emergency condition, such as
failure of the reel drive circuit, produce an uncontrolled increase
in cable tension. Upon such an occurrence, as cable tension passes
4 pounds the tensiometer is in the solid line position of FIG. 11
and, in the absence of an overload release feature, the tensiometer
would ultimately be destroyed. When cable tension reaches 10
pounds, spring 224 yields and overload release member 220 assumes
the dotted line position of FIG. 11 releasing cable 170.
The motor control circuit and the manner in which the same is
related to tensiometer 176 is illustrated in FIG. 12. The existing
hydraulic circuitry normally associated with a conventional cable
layer is indicated in dotted lines and a flow control valve 228 is
positioned in circuit therewith to divert flow to a conventional
solenoid operated valve 230 which controls the input to hydraulic
motor 180. When valve 230 is closed, as shown in FIG. 12, flow
through valve 228 is dumped to reservoir. Upon closure of switch
210 carried on tensiometer 176, valve 230 is activated to
pressurize line 232 and communicate line 234 with reservoir 236 to
rotate motor 180 in the pay-out direction.
A cross-line relief 238 is connected across lines 232 and 234 to
provide a pressure relief and dynamic braking feature for the
positive drive system. The cross-line relief includes
differentially biased relief valves 240, 242, which may, for
example, be set to relieve 400 p.s.i. and 1,500 p.s.i.,
respectively, as applied from the motor side of the valves. Relief
valve 242 is operative when motor 180 is being driven to dump
excessive pressure surges in line 232 to reservoir via cross-over
line 244 and conduit 234. When cable tension decreases to open
switch 210 and block the motor circuit at valve 230; reel 164
continues to rotate under its own inertia which, of course, rotates
the rotor of motor 180 causing the same to act as a pump. It is at
this point that relief valve 240 comes into play by yielding to
recycle pressurized fluid from line 234 through cross-over line 246
and back to the intake of the motor/pump. This has a dynamic
braking effect on reel 164 as the kinetic energy of rotation is
dissipated, primarily through heat losses, at relief valve 240.
A further advantage in the cross-line relief arrangement is that it
permits cable to be manually unreeled at a controlled tension
which, in the case of the illustrated parameters, would be
approximately 12 pounds. In such situation, the motor again acts as
a pump and is relieved through cross-over line 246. This is
particularly advantageous in certain emergency situations such as
in the case of a complete power loss.
A conventional double pole single throw toggle switch 248 and
manually operable rewind and pay-out switches 250, 252 whereby
valve 230 may be manually rather than automatically controlled
completes the circuit description of FIG. 12. As will be apparent,
switches 250 and 252 may be brought into circuit for manually
controlling the reversible operation of motor 180.
In operation, and assuming the solid line position of FIG. 9 and
the circuit condition of FIG. 12, as cable tension increases
tensiometer bracket 200 pivots counterclockwise to close switch 210
and energize solenoid valve 230 whose spool moves downwardly, as
viewed in FIG. 12, to pressurize line 232. Motor 180 then rotates
reel 164 to restore the slack condition of FIG. 10 at which time
switch 210 opens to block lines 232 and 234. The inertial rotation
of reel 164 is dynamically braked by the pumping action of motor
180 recycling fluid through relief valve 240 and cross-over line
246 and, thereafter, when cable tension again increases the
sequence of events just described is repeated.
* * * * *