U.S. patent number 3,768,630 [Application Number 05/199,282] was granted by the patent office on 1973-10-30 for accumulator with automatic override.
This patent grant is currently assigned to Rapistan Incorporated. Invention is credited to Russell A. Inwood, Edward G. Malone, Hardol Van Asselt.
United States Patent |
3,768,630 |
Inwood , et al. |
October 30, 1973 |
**Please see images for:
( Certificate of Correction ) ** |
ACCUMULATOR WITH AUTOMATIC OVERRIDE
Abstract
This invention relates to a powered roller accumulator conveyor
having a powered propelling member passing through a plurality of
independent accumulating zones arranged along the conveyor. The
propelled member is shiftable between driving and non-driving
positions with respect to the powered rollers by means of
vertically shiftable supporting rollers operated by pneumatically
powered actuators. Each of the actuators are controlled by means of
a series of valves connected to a source of fluid pressure. In an
accumulating position, each of the actuators are connected through
an article detecting sensor-operated valve to the source of fluid
pressure. In an override or discharge position, shuttle valves
associated with each actuator are series connected to the source of
fluid pressure through a main control valve and are operative to
direct the flow of fluid from the sensor operated valve to energize
each of the actuators in each of the zones to shift all of the
operating zones into driving position.
Inventors: |
Inwood; Russell A. (Rockford,
MI), Malone; Edward G. (Wyoming, MI), Van Asselt;
Hardol (Grand Rapids, MI) |
Assignee: |
Rapistan Incorporated (Grand
Rapids, MI)
|
Family
ID: |
22736921 |
Appl.
No.: |
05/199,282 |
Filed: |
November 16, 1971 |
Current U.S.
Class: |
198/781.06 |
Current CPC
Class: |
B65G
47/261 (20130101); B65G 2203/042 (20130101) |
Current International
Class: |
B65G
47/26 (20060101); B65g 013/07 (); B65g
013/071 () |
Field of
Search: |
;198/127R,160,203
;246/182A |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Blunk; Evon C.
Assistant Examiner: Carson; W. Scott
Claims
The embodiments of the invention in which an exclusive property or
privilege is claimed are defined as follows.
1. A conveyor having a plurality of rollers forming an article
transporting track, a driven propelling member, means effecting
driving connection between said propelling member and said rollers,
a plurality of actuator means for effecting engagement and
disengagement of the driving connection between said propelling
member and said rollers, said actuator means being arranged in
tandem along said conveyor and forming a plurality of independent
operating zones; a sensor in each zone for detecting the presence
of articles on said conveyor, one said sensor operatively connected
to one said actuator; each of said actuators having a pneumatically
actuated member; a source of fluid pressure and fluid pressure flow
control means, said control means characterized by each actuator
being connected to said source of fluid pressure through a first
conduit and a second conduit; a plurality of sensor actuated first
valves each interposed in said first conduit between said source of
fluid pressure and one of said actuators; a plurality of second
valves interposed in series in said second conduit and each
connected also to both one of said first valves and to its
associated actuator, said second valves each having a valve member
shiftable to alternately connect said actuator to said first valve
or to said second conduit; a master valve interposed between said
second conduit and said source of fluid pressure, said master valve
in one attitude admitting fluid pressure to the first actuator
adjacent the discharge end of said conveyor bypassing the first
valve therefor, said second conduit and said second valves
providing a sequential first valve bypass for fluid pressure
between said source of fluid pressure and each of said actuators to
rapidly shift said conveyor from accumulation mode to conveying
mode.
2. A conveyor as described in claim 1 wherein said master valve in
a second attitude closing said second conduit to said source to
shift said conveyor to accumulation mode.
3. In an accumulator conveyor having a plurality of rollers forming
an article transporting track, a driven propelling member, means
effecting driving connection between said propelling member and
said rollers, a plurality of actuator means for effecting
engagement and disengagement of the driving connection between said
propelling member and said rollers, said actuator means being
arranged in tandem along said conveyor and forming a plurality of
independent operating zones; a sensor in each zone for detecting
the presence of articles on said conveyor, one said sensor
operatively connected to one said actuator; each of said actuators
having a pneumatically actuated member; a source of fluid pressure
and fluid pressure flow control means, said control means having a
plurality of sensor actuated first valves, each of said valves
being connected in parallel to said source and to one of said
actuators, each one of said sensors when it detects the presence of
an article operable to shift the first valve associated therewith
to a closed position, said control means characterized by a
plurality of second valves interposed in series between each of
said first valves and said associated actuators and shiftable
between accumulating and by-pass positions; a master valve between
said source of fluid pressure and one of said second valves, said
one valve being at the discharge end of said conveyor, said master
valve connected to said one valve by a first valve by-pass line;
said master valve shiftable alternately between a first position
and a second position connecting said source to said one valve
through said by-pass line, said master valve in said first position
causing said conveyor to operate in an accumulating mode controlled
by said first valves and in said second position causing fluid
pressure to be admitted sequentially to each of said actuators
through said second valves to cause all operating zones of said
conveyor to shift into article propelling mode.
4. A conveyor as defined in claim 3 wherein said plurality of
second valves is a shuttle valve having a pair of inlet ports and
an outlet port, each of said first valves connected to one of said
inlet ports of said associated second valves, said master valve
connected to the other of said inlet ports of said one valve, the
other of said inlet ports being operatively connected to the outlet
port of the shuttle valve of the next adjacent upstream zone
beginning with said one valve, and said actuators being connected
to said outlet port of said associated second valves.
5. A conveyor as described in claim 4 wherein said conveyor is
divided into a plurality of independent operating zones, said
sensor is centrally positioned within each zone, and said actuator
means in each zone is operatively connected to said sensor in said
zone.
6. A conveyor as described in claim 3 wherein said control means
includes a first valve by-pass line for each of said zones and a
primary flow line applying a constant pressure to said first valves
from said source, said master valve in said second position causing
the operating zone at the discharge end of said conveyor to release
articles accumulated thereon, said sensor then opening said
associated sensor actuated valve in said operating zone to open and
permit air through said associated by-pass line to said adjacent
actuator whereby each zone sequentially shifts into an article
propelling mode.
7. A conveyor having a plurality of independent operating zones and
a propelling member common to all of said zones; pneu-matically
controlled actuator means in each of said zones for effecting
either a driving or non-driving connection between the propelling
member and articles on the conveyor; first means connecting each of
said actuator means to a common pressure source; sensor means in
each of said zones to detect the presence of an article therein;
and sensor-operated valve means in said first connecting means to
selectively release said source of pressure on each of said
actuator means when each of said sensors detects the presence of an
article, the improvement comprising: a shuttle valve associated
with each of said actuator means, each shuttle valve having a fluid
pressure outlet port, a first inlet port and a second inlet port;
second means connecting said outlet port to each associated
actuator means; third means connecting said first inlet port to
said sensor operated valve means; a master valve connected to said
source; fourth means connecting the second inlet port of said
shuttle valve at the discharge end of the conveyor to said master
valve; fifth means connecting the second inlet port of each
upstream shuttle valve with the adjacent downstream actuator means,
said master valve shiftable to apply said fluid pressure source
from said first connecting means to said fourth connecting means to
apply fluid pressure to each of said actuator means in a next
adjacent upstream zone and bypassing the sensor operated valve
means connected to said associated actuator means.
Description
BACKGROUND OF THE INVENTION
This invention relates to accumulator conveyors and more
particularly to an accumulator conveyor in which delivery or
non-delivery of the propelling force to the articles is
pneumatically controlled. The invention constitutes an improvement
over accumulator conveyors of the type shown, for example, in
commonly assigned, co-pending United States Patent Application Ser.
No. 167,617, filed July 30, 1971, by M. J. DeGood, entitled
ACCUMULATOR WITH TRANSPORT OVERRIDE.
SUMMARY OF THE INVENTION
The improvement of this invention resides primarily in the
arrangement of the article detecting sensors located in each
accumulating zone and in the provision of a shuttle valve connected
in the pneumatic circuit controlling the actuator in each of the
independent zones. The sensors for each zone are located centrally
within each zone and serve to control a plurality of pressure
rollers both upstream and downstream of the article being sensed.
The shuttle valve is connected at one side to the sensor actuated
valve and to the actuator while its opposite side is connected to
an adjacent downstream actuator. The shuttle valve associated with
the first zone at the discharge end of the conveyor is connected to
a source of fluid pressure through a main control valve which is
pro-vided to shift the conveyor between accumulating and transport
or override positions.
Through the use of the shuttle valve and the centrally located
sensors in each zone, articles on the conveyor, when the conveyor
is operating in an accumulating mode, are spaced closely adjacent
each other thereby utilizing the length of the conveyor to its
maximum. In the prior art accumulating conveyors, an undesirable
spacing exists between each of the articles in each zone and
between each zone thereby requiring conveyors considerably longer
than necessary. As an example, in the prior accumulating conveyors,
it is necessary to utilize a conveyor 95 to 100 feet in length in
order to accumulate 80 carton feet of articles. In the present
invention the spacing between the articles is minimized thereby
allowing the use of a much shorter conveyor resulting in lower
conveyor costs. This also results in conservation of plant space.
In addition, when an accumulating conveyor of the prior art type is
shifted into an override or discharge position, the articles
thereon will move out of the conveyor in batches or groups from
each zone. The spacing between the articles and between each group
or batch is essentially wasted space and contributes to overall
operating costs. The present invention overcomes many of the
problems of the prior art by closing the spacing between the
accumulated articles thereon when operating as an accumulator. When
operating as a means of conveying, all of the articles on the
conveyor simultaneously move toward the discharge end.
These and other important objects and advantages of this invention
will be readily understood by those skilled in the con-veyor art
upon reading the following specification with reference to the
accompanying drawings in which:
FIG. 1 is a plan view of a roller conveyor incorporating this
invention;
FIG. 2 is a side-elevational view of the roller conveyor shown in
FIG. 1;
FIG. 3 is an enlarged sectional elevation view taken along the
plane III--III of FIG. 2 illustrating the conveyor in an
article-propelling position;
FIG. 4 is an enlarged sectional elevation view similar to FIG. 3
showing the conveyor in an article non-propelling condition;
FIG. 5 is an enlarged elevational view similar to FIG. 2 with
portions broken away to illustrate the sensing mechanism of the
invention;
FIG. 6 is a sectional plan view of the actuator control valve;
FIG. 7 is a pneumatic control schematic illustrating the pneumatic
pressure system of the invention;
FIG. 8 is a pneumatic control schematic similar to FIG. 7
illustrating an alternate pneumatic pressure system; and
FIG. 9 is a diagrammatic view of an accumulator conveyor
illustrating the various operating zones of the conveyor.
In executing this invention, vertically shiftable supporting
rollers for the propelling member are arranged in groups of
independent operating zones, each zone being operated by a
pneumatically powered actuator. In each zone, a pressure roller
assembly is biased downwardly into a position in which the
propelling member is out of article-propelling position. When fluid
pressure is admitted to the actuator associated with each zone, the
bias is overcome and the actuator shifts the support rollers
upwardly into a position in which the propelling member is in an
article-propelling position.
An article-detecting sensor located within each zone operates a
valve interposed between the actuator and a source of fluid
pressure. In an article-propelling attitude, the actuator is
energized by the fluid pressure source through the valve. Upon the
sensing of an article positioned within that zone, the valve closes
with respect to the pressure source and opens with respect to the
actuator, releasing the pressure therein and allowing the support
rollers and propelling means to shift to an article non-propelling
position.
A shuttle valve having two inlet ports and a single outlet port is
positioned in the line between the sensor-operated valve and the
actuator with the outlet of the shuttle valve connected to the
actuator. One of the inlet ports is connected to the
sensorcontrolled valve while the other inlet port is connected to
the next adjacent downstream actuator. The shuttle valve located in
the first zone at the outlet end of the conveyor is connected to
the fluid-pressure source through a three-way main control valve
which is operative to shift the conveyor between an accumulating
function and a discharge function.
Referring specifically to FIGS. 1 and 2 of the drawings, the
numeral 10 generally indicates a conveyor track of conventional
design having a pair of side rails 12 and 13 and article-supporting
rollers 14 at spaced intervals therebetween forming an
article-supporting and conveying surface. An endless propelling
member or belt 16 is located below the transport rollers 14. It
will be recognized that the propelling member passes over terminal
pulleys at each end of the run and has some type of conventional
equipment to drive it. This equipment is not illustrated as it is
conventional in design and many types of equipment are available
for that purpose.
The belt 16 is supported for engagement with the transport rollers
by support or pressure rollers 18. Each of the support rollers is
rotatably mounted on a shaft 20. The rollers are supported at one
end by the shaft 20 in a hole 22 (FIG. 3) formed in the side rail
12. The opposite ends of the pressure rollers are supported by the
shaft 20 on an interior support rail 24 (FIG. 3). The interior
support rail 24 is provided with a plurality of equally spaced
elongated openings 26 which receive the pressure roller shafts 20.
The openings 26 extend vertically in the interior support rail,
allowing vertical movement of the shaft therein. The interior
support rail 24, illustrated in greater detail in FIG. 3, is
generally formed as a channel 28 partially closed at the top on the
side opposite the openings 26. The channel 28 runs parallel to side
rail 13 and is fixed to the inside of the side rail 13 such that
the openings 26 are in alignment with the holes 22 in the opposite
side rail 13.
An inflatable elongated tube-like member 30 is positioned inside
the channel 28 within each operating zone. In its inflated
condition, the tube 30 holds the pressure rollers in an upward or
article-propelling position. As illustrated, this is accomplished
by means of a flat support plate 32 positioned inside the closed
channel 28. When the tube is inflated, the support plate 32 is
urged upwardly against the shafts 20 moving them upwardly within
the confines of the slots 26. The shafts 20 on one side and the
inwardly turned lip 34 on the opposite side of the closed channel
confine the plate 32 and prevent it from being lifted out of the
channel when the tube is inflated.
The tube-like member 30 may be made of a fabric reinforced neoprene
rubber. The member is closed at one of its ends 36 (FIG. 2) in any
convenient fashion such as by vulcanizing. The opposite end 38 is
similarly closed and is provided with an inlet fitting 40 which is
connected by means of suitable tubing 42 (FIGS. 2, 3, and 4)
through an actuator control valve 44 to a source of fluid
pressure.
A plurality of article-sensing assemblies 46 are positioned along
the length of the conveyor 10 at predetermined intervals and
provide the control means for each of the accumulating zones.
Referring to FIGS. 2, 3, and 5, each sensor assembly 46 comprises a
pair of spaced-apart bracket members 48 and 50 mounted on pivot
pins 54 which are fixed to the side rails 12 and 13 of the
conveyor. At their upper ends, the brackets 48 and 50 are provided
with hex holes 52 (FIGS. 2 and 5) for engagement with the shaft 55
of a sensor roller 49. In its sensing position, the roller 49 is
supported slightly above the level of the transport rollers 14 of
the conveyor surface. The brackets extend downwardly from the
roller. In the case of the bracket 50 on the side 12 of the
conveyor having the interior support rail 24, the bracket curves
inwardly to allow clearance for the support rail and actuator
mechanism. The brackets are connected together by means of a tube
56 fixed at each of its ends to the lower ends of the brackets 48
and 50. The brackets 48 and 50, the tube 56 and the sensing roller
49 on its shaft 54 move together and form an integral sensing
assembly 46. Bracket 50 is provided with an outwardly turned flange
58 for engagement with the plunger 66 of the actuator control valve
44 which will be more fully described hereinafter.
A resilient bias spring 62 is fixed at one end 64 to the conveyor
side rails 12 and at its other end to the bracket 48. The spring 62
biases the sensor assembly 46 into an upper or sensing position.
THe upper limit of travel of the sensor roller is established by
the limit of travel of the plunger 66 of the valve 44.
The actuator control valve 44 controls the fluid pressure supply to
the pneumatic actuator 30 and also, in response to an input from
the sensor, closes the input from the fluid supply source and vents
the pressure in the actuator to the atmosphere. In an
article-propelling position, the valve is open with respect to the
fluid pressure source and closed with respect to the atmosphere to
thereby apply the source of pressure directly to the pneumatic
actuator 30.
Referring now to FIG. 6, the valve assembly 44 is seen to comprise
a main body portion 70 having mounting holes 72 therein for
mounting on a downwardly extending flange 25 of the interior
support wall 24 by means of conventional fastening means 27 (FIGS.
3, 4, and 5).
The main body 70 of the valve is provided with a pair of
communicating passageways 80 and 90. The first opening or
passageway 80 extends along the length of body 70 and is tapered
outwardly and undercut at one end to form an internal valve seat
82. The inlet to the valve seat 82 has a diameter slightly larger
than that of the valve seat 82 and is threaded to receive an inlet
fitting 74 provided for connection to a source of fluid pressure.
An "O" ring 84, a spherical bearing or ball valve 86 and a bias
spring 88 are positioned within the enlarged portion of the opening
80. The "O" ring 84 is placed in the undercut groove and forms a
resilient seat surface for the ball valve 86 when it is urged
forwardly (to the left as viewed in FIG. 6) by the bias spring 88.
As illustrated in the figure, the valve is closed with respect to
the fluid pressure source which enters through the fitting 74.
A primary outlet 90 in the valve extends transversely of the
opening 80 and opens through a side wall of the body 70. The
primary outlet 90 is threaded at an enlarged end to receive a
fitting 76 which may be connected by means of tubing 42 (FIGS. 3
and 4) to the pneumatic actuator 30. A piston control assembly 66
is slidably positioned in the opening 80 opposite the inlet end.
The piston is provided with an enlarged head portion 94 and an
extending reduced diameter shank portion 99. When the piston is
positioned in the opening 80, the shank portion 99 extends along
the length of the opening 80 to control the ball valve 86 as will
be more fully described hereinafter. The shank is provided with a
pair of spaced-apart enlarged diameter portions 92 and 93
positioned below the head and midway along the length of the shank
respectively. The outer diameter of these enlarged portions is
slightly less than that of the passageway 80 through which they
pass. A screw 89 is threaded into the body 70 and extends into the
opening 80 between the enlarged diameter portions 92 and 93
sufficiently to be engaged by the enlarged portion 93. This
prevents the piston from being pushed out of the opening 80 by the
force of the pressure. This screw is sufficiently spaced from the
enlarged portion 92 to eliminate contact with it at all times.
The piston head 94 is provided for engagement with the flange 58 on
the sensor bracket 50 (FIG. 2). An "O" ring 96 surrounds the
enlarged portion 92 of the piston body adjacent the head and forms
(when the piston is moved to the right) a pressure-tight seal
between the head of the piston and a recess 97 formed in the
housing 70. The annular space between the outer diameter of the
enlarged portions 92 and 93 and the wall of the opening 80 provides
a secondary outlet port 98 for fluid pressure when the piston is
shifted to the left as illustrated in FIG. 6.
As illustrated in FIG. 6, the valve is in the position it assumes
when an article is present on the sensor, that is, the bracket as
shown in FIGS. 2 and 5, is moved away from the valve when the
piston is thus shifted to the left as illustrated, the fluid
pressure is being exhausted from the actuator to the atmosphere
through the secondary outlet port 98. Fluid from the actuator 30
flows back through the fitting 76, the opening 90, and through the
opening 80 along the sides of the enlarged diameter portions 92 and
93 where it is vented to the atmosphere through the secondary
outlet port 98. In this position, the flow of fluid from the source
is effectively blocked by the ball valve 86 which is held against
the valve seat 84 by both the bias spring 88 and the force of fluid
pressure cooperating with the spring.
When the conveyor is in an article-propelling attitude, the sensor
46 is in its upwardly biased position and fluid pressure is
admitted to the actuator 30 through the valve 44 in the following
manner. The bias spring 62 urges the sensor roller 49 upwardly with
the sensing assembly 46 and the flange 58 on bracket 50 presses
against the head 94 ofthe valve moving the piston assembly 66, as
shown in FIG. 5, to the right. As the piston is moved to the right,
the end of the shank 99 of piston 66 moves through the area of the
valve seat 82 and displaces the ball valve 86 by compressing spring
88. At the same time, the "O" ring 96 positioned below the head 94
around the piston body 92 is compressed between the head 94 and the
valve body 70 in the recess 97, closing the secondary outlet port
98. The fluid from the source is then allowed to flow through inlet
fitting 74 through ports 80 and 90 and fitting 76 to the pneumatic
actuator 30 causing it to inflate and position the support rollers
in an article-propelling position.
A shuttle valve 100 is connected between each sensor valve 44 and
each actuator 30 (FIG. 7). The shuttle valve is of a type commonly,
commercially available and basically is a double-check valve having
a pair of oppositely directed inlet ports 102 and 104 and a
centrally located outlet port 106. Referring now to FIG. 7, a
plurality of shuttle valves 100 are illustrated, one in each
operating zone. Each is connected between the sensor valve 44, the
actuator 30, and also to a source of fluid pressure through a main
three-way control valve 131. For ease of illustration and to
facilitate a better understanding of the invention, the
illustration of FIG. 7 is divided into three zones A, B, and C
representing several of the various operating zones of the
conveyor. The component parts located in and operating within each
zone are of similar construction. The connection of the valves will
be described relative to several of the zones, it being understood
that any number of operating zones may be similarly interconnected
as required.
As previously mentioned, the shuttle valves 100 have a pair of
inlet ports 102 and 104 and a centrally located outlet port 106. A
ball valve 108 located within the shuttle valve 100 is shiftable
with the application of fluid pressure to open one of the inlet
ports while at the same time effectively blocking the other. The
flow of fluid within the valve may be from inlet port 104 to the
outlet 106 or from inlet port 102 to outlet 106. Fluid pressure can
never flow from one inlet port to the other. Exhaust or reverse
flow from the outlet 106 is through either the inlet ports 102 or
104 depending upon the position of the ball valve. The ball valve
will always be closing the port opposite the one which last served
as the inlet for fluid pressure. As will be more fully described
hereinafter, this is an important feature of the present
invention.
Referring now briefly to FIG. 9, a conveyor having a plurality of
independent operating zones designated A through E, is
schematically illustrated. Each zone is controlled by a sensor
assembly 46 centrally located in each zone which serves to control
the actuator means for each zone. In the present invention, the
sensing rollers 49 for each zone are centrally located above each
zone. When operating in an accumulating mode, an article coming to
rest on a sensor in a first zone, for example zone A, shifts the
actuator to an article non-propelling position. As articles
accumulate on that section of the conveyor by the pressure of
articles upstream therefrom, the next adjacent section of the
conveyor, zone B for example, is then similarly shifted to a
non-propelling position and so along the conveyor.
Turning again to FIG. 7, the pneumatic pressure system and valve
arrangement of the invention is schematically illustrated. An
actuator 30 in each zone is connected to a sensor controlled valve
44 through a shuttle valve 100. Each of the valves 44 are connected
to a source of fluid pressure 122 by means of lines 124 and 134.
The valve 44, as schematically illustrated, is identical to that
previously disclosed in connection with FIG. 6 with the reference
numerals 74, 90 and 98 representing the input, the primary outlet,
and the secondary outlet respectively.
The primary outlet 90 from valve 44 is connected via line 126 to an
inlet port 102 of shuttle valve 100 and through the shuttle valve
outlet port 106 via line 127 to the actuator 30. In an accumulating
attitude as illustrated in FIG. 7, fluid pressure from the source
passes through line 134 to line 124 where it is connected to the
primary inlet 74 of each of the sensor controlled valves 44 and
thence to the actuators 30 through the inlet port 102 and outlet
port 106 of shuttle valve 100.
Inlet port 104 of the shuttle valve 100 in zone A is connected via
line 140 to the main control valve 131 where it may selectively be
connected to the fluid pressure source 122 through the main control
valve and line 134. The inlet ports 104 of the shuttle valves
located upstream of a particular zone are each connected by lines
142 to the outlet port 106 of the next downstream actuator. This
connection may be made through the use of a conventional fitting
connected in the line 127 between the outlet port 106 of shuttle
valve 100 and an individual actuator 30.
The shuttle valves 100 are series connected to each other and to
each of the actuators 30. Fluid pressure applied from the source
122 travels through line 134 through the control valve 131 and line
140 to the inlet 104 of the shuttle valve 100 in zone A. The
pressure applied to the shuttle valve through the inlet port 104
displaces the ball valve 108 in the shuttle valve, closing the
inlet 102, allowing the pressure to pass through the outlet port
into line 127. Pressure from the source is applied to the actuator
30 in zone A while simultaneously also traveling along line 142
where it is applied to the inlet port 104 of shuttle valve 100 in
zone B. Similar movement of the ball valve 108 occurs in zone B
moving the ball valve to the left to block the flow of fluid from
the inlet port 102. Fluid pressure inflates the actuator 30
associated with zone B while simultaneously applying pressure in a
similar fashion to the shuttle valve and actuator located in zone
C. This cycle repeats throughout the length of the conveyor.
The main control valve 131 is a three-way valve of conventional
construction and may be either manually operated or controlled
remotely by suitable electronic circuitry (not shown). In either
event, it is desirable to provide a case stop 150 movable into or
out of the line of the conveyor at its discharge end. The case stop
150 may be of any suitable construction as is well known to those
skilled in the art and serves to interrupt the flow of articles
along the conveyor. The case stop 150 is operatively connected to
the main control valve 131 so that when the case stop is in a
raised position to prevent the flow of articles along the conveyor,
fluid pressure will be applied from the source 122 and line 134 to
line 124 and through each of the sensor control valves 44 in the
manner previously described.
When the case stop 150 is lowered, the source of fluid pressure is
applied by valve 131 from line 134 to line 140, and through shuttle
valves 100 to the actuators 30 in each zone as described above to
simultaneously shift all of the zones into an article-propelling
position.
OPERATION
In an accumulating mode of operation, as case stop 150 is raised
above the level of the conveyor fluid pressure is applied to each
valve 44. All ofthe valves 44 will be open.
The article contacting the case stop then initiates the
accumulation cycle in zone A. As the sensor 46 in zone A is
actuated, valve 44 closes with respect to the source of pressure
(by movement of ball valve 86 against the seat 84, FIG. 6) and
vents the pressure in the actuator 30 through the shuttle valve
ports 106 and 102, the outlet 90, and valve 44 to the atmosphere
through the secondary outlet port 98. Articles continue to move
from the adjacent upstream zones of the conveyor toward and into
zone A until sensor 46 in zone B is actuated. When the sensor 46 in
zone B is depressed, pressure in the actuator 30 associated with
zone B is released and vented to the atmosphere through the shuttle
valve 100 and outlet port 98 of the sensor valve 44 associated with
zone B. Articles moving in zone C continue to fill the conveyor
located in zone B and a similar pressure release occurs in zone C
when the sensor 46 associated therewith is contacted. This can
continue from zone to adjacent zone along the length of the
conveyor until the length of the conveyor 15 shifted to article
nonpropelling attitude or the case stop 150 is retracted.
When accumulation is completed and the zones have all been filled,
the conveyor surface may be cleared by shifting valve 131 to apply
the flow of fluid pressure from line 134 to line 140 while
simultaneously lowering the case stop 150. Pressure is applied to
line 140 and shuttle valve 100 in zone A, to the actuator 30
associated therewith and to each shuttle valve and actuator in all
adjacent upstream zones. Each of the zones are then shifted into
article propelling position simultaneously without regard to the
position of the sensor 46 on the conveyor track surface. When all
of the articles clear the conveyor, valve 131 may be shifted to the
accumulating position again by raising the case stop 150 and the
actuators will be controlled by the sensor control valve 44 as
previously described.
This rapid clearing feature also increases the versatility of the
conveyor. By simply placing the valve 131 in the position to apply
the fluid pressure source into line 140, all of the actuators in
each zone are energized and the conveyor will operate as a
conventional powered roll conveyor and the effect of the articles
passing over the individual sensor will be negated.
An alternate arrangement providing a progressive discharge of
articles from the conveyors is illustrated schematically in FIG. 8.
In this embodiment, the primary outlet port 90 of sensor valve 44
is connected to both the inlet port 102 of shuttle valve 100 in the
zone associated therewith and also to the inlet 104 of the shuttle
valve 100 in the next adjacent upstream zone.
In an accumulating attitude, case stop 150 is raised, and pressure
in the actuator 30 in zone A exhausts through the shuttle valve
port 104 into the atmosphere through line 140 in the opened port
141 of three-way valve 131. The remaining actuators are vented to
the atmosphere through the sensor valves 44 in the manner
previously described, i.e., through secondary outlet port 98.
To discharge articles on the conveyor, the case stop is lowered and
valve 131 applies pressure from the source 122 through line 140 and
shuttle valve 100 in zone A to the actuator 30 causing articles in
that zone to move toward the discharge end of the conveyor. As zone
A clears and articles pass off the sensor 46 in zone A, pressure is
applied through the sensor valve 44 in zone A and line 126 to
shuttle valve 100 in zone B and through it to the actuator 30
associated with zone B thereby causing the articles in zone B to
discharge from the conveyor. The clearing of zone B causes this
cycle to repeat in zone C and so on along the length of the
conveyor with the sensor associated with each zone controlling the
next adjacent upstream actuator through its associated shuttle
valve. The conveyor so arranged will also function satisfactorily
as a conventional power roll conveyor, when no accumulation is
required. The exhaust ports 98 of the valves 44 are designed with
sufficient restriction that insufficient air can escape from the
actuator during the time interval necessary for passage of a single
article over a sensor to permit the actuator to react. However,
should the articles be traveling in groups without spacing between
them, there will be an accumulation reaction in the arrangement of
FIG. 8. However, this will not occur in the arrangement of FIG. 7
because the effect of the sensors on the valves 44 is completely
negated so long as the valve 131 is open to line 140.
To provide the proper centering of the drive belts 16 along the
length of the conveyor, it is desirable to alternate the location
of each actuator mechanism 30 along its length. The actuator
mechanism for each adjacent zone may be positioned on opposite
sides of the conveyor. Zones A, C, and E may be positioned adjacent
side rail 12 while zones B and D may be positioned adjacent side
rail 13. As the belt is moved to a non-driving position as
illustrated in FIG. 4 from a driving position as illustrated in
FIG. 3, the belt 16 in the next zone will tilt in the opposite
direction thereby eliminating any tendency of the belt to shift to
one side or the other of the conveyor.
It will be seen from the preceding description in both embodiments
as illustrated in FIGS. 7 and 8, the second conduit 140 and its
segments extending from one shuttle valve to another constitutes a
secondary fluid pressure supply line bypassing the individual
actuator control valves 44. In the embodiment of FIG. 7, this
conduit is in effect unitary and continuous, passing through the
shuttle valves in series and this acts to charge the actuators in
series but practically simultaneously. In the embodiment of FIG. 8,
the bypass line is segmented with each segment except the first
being controlled by the preceding actuator control valve, the
bypass line serving to shift the control effected by the actuator
control valve from its own actuator to the adjacent upstream
actuator and effectively bypass the control valve for that
actuator. Thus, once again the actuators are charged in series but
the control valves are utilized to provide a progressive shift of
the conveyor from accumulation mode to conveying mode.
From the foregoing description and drawings, it will be readily
apparent to those skilled in the art that the present invention
provides an extremely versatile conveyor wherein when accumulating,
there is a full closing between packages thereby allowing the
utilization of the full length of the conveyor. The positioning of
the sensors in the central portion of each zone rather than in a
next adjacent zone as found in the prior art, reduces the
immobilized increment of packages on the conveyor. The conveyor is
further constructed of relatively simple and inexpensive component
parts which may be readily adapted for use as a conventional
powered conveyor.
While a preferred embodiment and a modification of this invention
have been illustrated and described, it will be recognized that
other embodiments and modifications of this invention incorporating
the teachings hereof may be readily made in the light of this
disclosure. All modifications embodying the principles of this
invention are to be considered as included in the appended claims
unless these claims by their language expressly state
otherwise.
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