Note: Descriptions are shown in the official language in which they were submitted.
~0~7~83
BACKGROUND OF THE INVENTION
In the firing of industrial oil burners and auxiliary
or .igniter burners associated with large utility burners, it has
been a conventional practice to employ steam as an atomizing
agent for the fuel oil. Further, the same source of steam is
conventionally employed in the purging of fuel oil lines for
safety and other considerat;ons. Three (:3~ valves are ordinarily
employed in order to accommodate the various valving functions,
e.g. closing both steam and fuel oil lines, introducing steam
to the fuel oil line ;n the purge operation, and passing steam
and fuel oïl respectively through.the steam and fuel oil lines
for a running operation.
SUMMA~RY OF:T~ INVENTION
It is the general object of tne present invention to
provide a single valve capable of fulfilllng each of the fore-
going functions and whi.ch.is yet of desirably simple construction,
highly efficient in operation, and dependable over a long service
life. -
a ~
83
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 of the drawings is a vertical sectional view
through the valve of the present invention and an illustrative
actuator associated therewith, the valve elements being illustrated
in a closed position.
Fig. 2 is a front elevation of the valve.
Fig. 3 is a vertical sectional view similar to Fig. 1
but showing the valve elements in a partially open or purge
position.
Fig. 4 is a vertical sectional view similar to Figs. 1
and 3 but showing the valve elements in a fully open or running
position.
Fig. 5 is a vertical sectional view similar to Fig. 1
but showing a second form of the valve of the present invention.
Fig. 6 is a front elevation of the valve of Fig. 5.
Fig. 7 is a fragmentary vertical section showing the
Fig. 5 valve in a purge position.
Fig. 8 is a fragmentary vertical section showing the
Fig. 5 valve in a fully open or running position.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring particularly to Fig. 1, it will be observed
that the valve of the present invention has a body, indicated
generally at 10, which comprises several discrete parts. Similar
upper and lower body parts 12, 14 take the form of blocks bored
axially and in other geometrical directions to provide various
chambers and ports. In this regard, it should be noted that
directional and geometric terminology such as "axial", "upper",
"lower", "top-to-bottom", etc. is used herein for convenience of
description only and is not to be taken as limiting the scope of
the invention in the specification or the claims which follow.
The upper body part or block 12 is provided with upper
and lower axial bores 16, 18 and a coaxial reduced diameter
cylindrical opening 20 therebetween. A top cap or plug 22 serves
37~3
as a closure member for the bore 16 to define a cylindrical
chamber above but in communication with the reduced diameter
cylindrical opening 20. The bore or chamber 16 may hereafter be
referred to as a steam discharge chamber. The lower axial bore
18 is closed by a smaller intermediate body part or block 24 to
define a second cylindrical chamber beneath the reduced diameter
opening 20. The bore or chamber 18 may hereafter be referred to
as a steam inlet chamber.
As will be apparent, fluid flow communication between
the chambers 16 and 18 can be selectively established and
controlled through the cylindrical opening 20. Preferably, a valve
seat is provided at the opening 20 and may comprise a Stainless
Steel L-shaped annular member 26 as illustrated. The seat 26,
secured in the opening 20, is provided with a central cylindrical
through opening 28 for the axial passage of fluid therethrough
from the steam inlet chamber 18 to the steam discharge chamber 16.
For a supply of steam to the inlet chamber 18, a steam
inlet port comprises a radial bore 30 and a communicating bore 32
inclined between radial and axial planes and extending to the
inlet chamber. Optionally, a tubular steam inlet fitting 34 is
provided with an inner end portion entered in an enlarged radial
bore 36. The fitting may be welded in position as indicated at
38 and provides for the remote connection of a steam supply line
or conduit not shown. Welding of the supply line or conduit to
the fitting may thus be accomplished in spaced relationship with
the upper valve body block 12.
The steam discharge chamber 16 has an associated discharge
port partially formed by an inclined bore 40 which communicates
with the chamber at its inner end. At its outer end, the bore 40
communicates with a radial bore 42 and an enlarged radial bore 44
receives an inner end portion of an optional tubular fitting 46.
The tubular fitting 46 may be welded in position as indicated at 48.
The intermediate body block 24 has a short cylindrical
~o~7~s3
projection 50 which extends axially at an upper end portion and
which enters and closes the bore 18. Similarly, a short cylindrical
and axial]y extending projection 52 at the lower end of the block
24 extends into and closes an upper axial bore 54 at an upper
portion of the lower body block 14. A centrally located cylindrical
through opening 56 in the intermediate body block 24 provides for
selective communication between the steam inlet chamber 18 and the
bore 54 in the block 14.
The upper bore 54 in the body block 14 forms an oil
discharge chamber having an outlet port comprising inclined and
radial portions 56, 58 as described above for the ports in the
block 12. At a lower end portion of the block 14 an axial bore
60 is closed by a bottom cap or plug member 62 to form a chamber
which may hereinafter be referred to as an oil inlet chamber. The
oil inlet chamber 60 has an inlet port comprising inclined portion
64 and radial portion 66. Tubular fittings 68 and 70 may be
provided welded in place respectively at the oil inlet and discharge
ports.
As in the block-12, a reduced diameter coaxial opening ~`~
72 is provided between the oil inlet and discharge chamber 60, 54
and has an associated annular valve seat 74. The valve seat 74
preferably takes the form of a Stainless Steel L-shaped member
identical with the seat 26 and having a similar central through
opening 76. As will be apparent, communication between the oil
inlet and discharge chambers 64 can be selectively established and
controlled at the opening 76. --?
The top and bottom caps or plugs 22, 62 serve as closure
means as indicated and also serve an important assembly function.
That is, the caps or plugs are provided with similar radially
projecting annular flanges 78, 80 which are received respectively
in shallow annular grooves 82, 84 in the blocks 12, 14. The flange
78 is engaged by a top plate 86 and the flange 80 has an associated
bottom plate 88. As best illustrated in Fig. 2, the top and bottom
-- 4
~9~ 3
plates 86, 88 serve a clamping and assembly function together
with vertically extending tie rods 90, 90. Two (2) tie rods 90,
90 are shown, but it will be apparent that four (4) such rods may
be provided respectively at corners of the plates 86, 88. The tie
rods have threaded end portions and nuts 92, 92 engaged therewith
serve to secure the plates 86, 88 in clamping engagement respect-
ively with the flanges 78 and 80. Thus, it will be apparent that
the various body parts comprising plugs 22, 62, blocks 12, 14 and
intermediate block 24 can be securely clamped in vertically aligned
and assembled position as illustrated. When it is desired to
disassemble the valve body for cleaning or other maintenance
functions, it is necessary merely to remove the nuts 92, 92 and
to vertically disassemble the valve parts, the end caps or plugs
and the end plates.
In accordance with the presenl: invention, a steam valve
and actuator member is operatively associated with the valve body
and is movable therein between first, second and third positions
respectively for a closing operation, a purge operation, and a
running operation. The valve and actuator member, indicated
generally by the reference numeral 94, may vary widely in form
but preferably takes the form of a cylindrical slide valve disposed
within and guided by the wall of the cylindrical opening 56 in
the intermediate body block 24. In Fig. 1, the valve and actuator
member 94 is illustrated in its first or closed position and it
will be observed that a seating surface 96 at an upper portion
thereof is disposed in sealing engagement with the aforementioned
annular seat 26. The seating surface 96 takes a frusto-conical
form and a short diametrically reduced axial projection 98 extends
upwardly therefrom and within the central opening 28 of the
annular seat 26. A soft annular sealing member 100 is mounted in
an appropriate groove in the projection 98 and engages the wall of
the opening 28 in the seat. Thus, both hard and soft seats are
provided, metal-to-metal contact occurring between the frusto-
- 5 -
~(~97~3
conical surface 96 and the annular seat 26, and metal-to-soft seal
contact between the sealing member 98 and the wall of the opening
28.
A diametrically enlarged intermediate or body portion of
the valve and actuator member 94 is provided with first and second
radial openings 102 and 104. The openings 102, 104 shown are
spaced apart axially and, viewed axially, may take a somewhat half-
moon shape. Preferably, two (2) oppositely disposed openings 102,
102 are provided and two (2) oppositely disposed openings 104, 104.
The openings 102, 104 communicate internally of the valve and
actuator member and it will be apparent that an axial bore may be
conveniently provided to interconnect the same. Further, the
axial spacing of the openings 102, 104 is judiciously determined
in relation to the amount or degree of valve movement and the
axial dimension of the cylindrical opening 56 in the intermediate
body block 24. Further explanation is given below in this regard.
First, second and third annular sealing means are also
preferably provided and are arranged in axially spaced relationship
along the valve and actuator member 94. The sealing means may
take the form of similar annular soft seals 106, 108 and 110 in
top-to-bottom order. The first and third seals 106 and 110 are
disposed axially outwardly respectively of the openings 102, 104
and the second seal 108 is disposed therebetween. The seals 106, ~ ,
108 and 110 are each adapted to engage the wall of the cylindrical
opening 56 in the body block 24 and to prevent steam and/or oil
leakage along and between the valve and actuator member and the
wall.
At its lower end portion, the valve and actuator member -
94 has an axially projecting actuating pin 112 which cooperates
with a flat surface 114 at an upper end portion of an oil valve
member indicated generally at 116. The oil valve 116 is preferably
of the poppet type and has a frusto-conical seating surface 118
engageable in sealing contact with the aforementioned annular valve
7~L~3
seat 74. A diametrically reduced axia:L projection 120 extends
upwardly from the frusto-conical surface 118 and carries an
annular soft seal 122. The soft seal 122 engages the surface of
the through opening 76 to provide a second seat. Thus, as above,
both hard and soft seats are provided, the former between the
frusto-conical surface 118 and the annular seat 74 and the latter
between the soft seal 122 and the wall of the opening 76 in the
seat.
The oil valve member 116 is urged toward the closed
position of Fig. 1 by a biasing means which may vary in form
within the scope of the invention. As shown, the biasing means
comprises a coil spring 124 disposed within and seated at its
lower end on a lower end wall of a cup-shaped member 126. The
member 126 is threadably engaged at 128 with a dependi.ng reduced
diameter axial projection 130 on the lower cap or plug 62. At
i.ts upper end, the coil spring 124 is seated on an adjustment nut
132 threadably engaged with a lower end portion of a valve stem
134. The valve stem 134 projects axially downwardly from the oil
valve member 116 and is slidably received in a suitable opening
136 in the end cap or plug 62. A packing 138 is preferably
provided about the stem 134 and secured in position by a retainer
140.
From the foregoing, it will be apparent that the oil
valve member 116 can be engaged by the actuating pin 112 to urge
the same downwardly from its first or closed position illustrated
to a second or open position. In the open position of the valve
member, communication is established between the inlet and
discharge chambers 60, 54 for flow of fuel oil through the opening
76 in the valve seat 74.
Reverting to the steam valve and actuating member 94,
it will be observed that an axially projecting stem is also
provided therefor at 142. The valve stem 142 is slidably received
within a suitable through opening 144 in the top cap or plug 22
-- 7 --
~L~97~83
and extends upwardly therebeyond. A packing for the valve stem
is preferably provided at 146 and secured in position by a retainer
148. As~will be apparent, the position of the valve and actuator
member 94 can be readily controlled from a remote location above
the cap or plug member 22.
Actuating means for the steam valve and actuator
member may vary widely within the scope of the invention. An
illustrative actuating means is indicated generally at 150 and is
of the pneumatic type. A two-part housing for the actuator 150
comprises a lower cup-shaped member 152 secured in upright
position by a nut 154 threadably engaged with a stud 156 projecting
axially upwardly ~rom the cap or plus 122. An upper housing
member 155 ta]ces an inverted cup-shape and may be secured to the
lower member 152 as by means of suitable annular flanges 157, 158
disposed respectively on said upper and lower members and secured
together by appropriate screws or bolts and nuts 160, 160. An
atmospheric port or vent 162 is provided in the lower housing
member 152 and a port 164 in the upper member 155 may be connected ,
with a controlled source of air under pressure. Disposed within ~ -
the housing of the actuator 150 is a diaphram 166 peripherally
clamped between the flanges 157 and 158 and secured to an upper
end portion o~ the stem 142 by means of suitable nuts 168 and 170.
A return spring 172 may be of the coil type with an upper end
portion seated beneath the diaphram 166 and a lower end portion
thereof seated on the bottom wall of the cup-shaped housing
member 152.
As will be apparent, air under pressure may be supplied
through the port 164 for actuati.on of the diaphram 166, the stem
142 and its valve and actuator member 94, the spring 172 supplying
the necessary biasing or return force. Moreover, it will be
apparent that appropriate control or regulation of air pressure
will result in initial movement of the valve and actuator member
to an intermediate or purge position as illustrated in Fig. 3. On
-- 8 --
7~ !51;~
an increase in regulated pressure supplied through the port 164,
further downward movement of the valve and actuator member 94 will
occur to the running position of Fig. 4. Subsequently, an approp-
riate reduction in supply pressure will allow the return spring
172 to urge the diaphram, stem and the valve and actuator member
upwardly to the closed posïtion. Alternatively and if desired, a
step reduction in pressure can be employed to move the valve and
actuator member sequentially from the running position to the
purge position and then to the closed position.
Referring now to Fig. 3, it will be observed that the
valve and actuator member q4 is illustrated in the purge position
as indicated above. ~he frusto-conical seating surface 96 is
displaced axially downwardly from the annular seat 26 whereby to
open the steam inlet chamber 18 to the steam discharge chamber 16
through the opening in the valve seat. Thus, a first passageway
is provided interconnecting the steam inlet and discharge ports.
Said passageway comprises the steam inlet port, the inlet chamber
18, the seat opening 28, the steam discharge chamber 16, and the
steam discharge port and flo~ will occur therethrough for the
introduction of steam to a steam line which may be connected with
the fitting 46. Purging of steam lines is not ordinarily required
and accordingly, such flow may be regarded as merely incidental.
Steam flow through a second passageway is, however,
significant and results in the necessary purging of the oil line
or conduit. Said second passageway comprises the steam inlet
port, the steam inlet chamber 18, the cylindrical opening 56, the
oil discharge chamber 54, and the oil discharge port. More
particularly, the intermediate portion of the passageway is formed
by the radial openings 102 and 104 in the valve and actuator
member 94 and the internal interconnecting valve passageway. As
stated above, the axial spacing of the radial openings 102, 104 is
judiciously selected in relation to the axial dimension of the
opening 56 and, as will be observed in Fig. 3~ the axial spacing
~97~183
of the openings is slightly greater than the axial dimension.
Thus, free communication is established between the steam inlet
and oil discharge chambers for the purge operation. The inter-
mediate seal 108 prevents the reverse leakage of steam between and
along the valve and actuator member and the wall of the cylindrical
opening 56.
Reverting now to Fig. 1, it will be observed that the
axial spacing of the radial openings 102, 104 is such that the
lower opening 104 is closed by the wall of the opening 56 when the
valve and actuator member is in its closed position. Thus,
steam is not permitted to lea~ from the steam inlet chamber to the
oil discharge chamber. Lower seal 110 serves to prevent steam
leakage to the oil discharge chamber S4.
In Fig. 4, the valve and actuator member 94 is shown
in its third or running position. Steam is free to flow as above
through the steam inlet port, the steam inlet chamber 13, the
valve seat opening 28, the steam discharge chamber 16 and the
steam discharge port. Further, the actuating pin 112 engages the
surface 114 in this position and the oil valve member 116 is urged
to its open position against the biasing force of the spring 124.
Fuel oil flow thus occurs through a third passageway interconnecting
the oil inlet and discharge ports, said passageway comprising the
oil inlet port, the oil inlet chamber 60, the valve seat opening
76, the oil discharge chamber 54 and the oil discharge port.
Simultaneous outflow of steam and oil thus results respectively
through the steam and oil discharge ports.
The f~lnction of the uppermost or first seal 106 is also
to be observed in Fig. 4. Oil which is permitted to enter the
radial openings 10~, lQ4 and pass upwardly through the internal
valve passageway is blocked from flowing outwardly through the
radial openings 102, 102 by the wall of the cylindrical opening 56
Moreover, the seal 106 prevents such oil from passing upwardly
between the valve and actuator member and the wall of the opening
-- 10 --
97~1~3
to the steam inlet chamber. Conversely, steam in the inlet chamber
18 is prevented from flowing downwardly along the wall of the
opening 56 and adjacent the valve and actuator member so as to
~nter the radial openings 102, 102, exit from the radial openings
104, 104 and intermix with oil in the oil discharge chamber 54.
In a valve forming an alternative embodiment of the
invention in Figs. 5 through 8, valve operation is substantially
identical with that described above but valve construction varies
somewhat from that above. A valve 200 has a central or inter-
mediate body part 202 which takes a cylindrical form and which
has associated upper and lower closure members or plugs 204, 206.
The plug 204 may be secured to the body 202 by means of approp-
riate screws or bolts 208, 2Q8 and the plug 206 may be secured by
appropriate screws or bolts 210, 210. The screws 210, 210 may
also secure a housing 212 for a biasin~ means comprising a spring
214 associated with an oil valve member 216.
A steam inlet port is shown at 218 and a steam
discharge port at 220. Oil inlet port 222 has a corresponding
discharge port at 224. Steam inlet chamher 226 communicates with ~`
the inlet port 218 and a cylindrical opening 228 forms a steam
discharge chamber in communication with steam discharge port 220.
Oil inlet chamber 230 communicates with oil inlet port 222 and
oil discharge chamber 232 communicates with oil discharge port 222.
A first passageway for the flow of steam from the
steam inlet port 218 to the steam discharge port 22~ thus
comprises steam inlet cham~er 226 and steam discharge chamber 228
and communication is established between said two chambers by an
opening 234 in a first valve seat 236. A second valve seat 238
has an opening 240 which establishes communication between steam
discharge chamber 228 and oil discharge chamber 232. A third
opening 242 in a third valve seat 244 establishes communication
between oil inlet chamber 230 and oil discharge chamber 232.
A steam valve and actuator member indicated generally
~IL097~1~3
at 246 has an upper or actuating stem 248 which may have an
associated actuator, not shown, as in the valve embodiment
illustrated and described above in Figs. 1-4. Sealing means
for the stem 248 are indicated generally at 250 and may have a
biasing spring 252 associated therewith. A lower steam or
actuating pin 254 of the steam valve and actuating member extends
through the opening 240 in the second valve seat 238 and is of
reduced diameter with respect to the opening to provide for the
downward flow of steam thereabout from the steam discharge chamber
228 to the oil discharge chamber 232. The lower stem or actuating
pin 254 cooperates with the oil valve member 216 in the manner
described above for the valve of Figs. 1 through 4.
At an intermediate portion thereof r the steam valve
and actuator member 246 has a reduced diameter valve element 256
which is movable in one and an opposite direction in the cylin-
drical opening or chamber 228 and which cooperates with the first
and second valve seats 236, 238. A first annular seating surface
258 at an upper portion of the valve element 256 cooperates with
the valve seat 232 and a second annular seating surface 260 at a
lower portion thereof cooperates with the valve seat 238.
Preferably and as shown, the upper and lower portions of the valve
element 256 and the annular seating surfaces 258, 260 are of a
parti-spherical configuration.
The oil valve member 216 has a flange 262 providing a
seating surface cooperating with the valve seat 244 and a soft
seal may also be provided at 264 for preliminary closing. A stem
266 for the oil valve member 216 extends through sealing means
268 and 270 and downwardly into the housing 212 for connection
with biasing spring 214. As described above for the valve of
Figs. 1-4, the biasing spring 214 normally maintains the oil
valve member 216 in the closed position shown for the first and
second positions of the steam valve and actuator member 246. In
the third position of the steam valve and actuator member 246 the
- 12 -
~09~7~8,3
oil valve 216 is opened by the stem or pin 254 against the urging
of the spring 214.
In operation, the valve of Figs. 5-8 assumes a first
position as illustrated ;n Fïg. 5 under the command of its
actuator which ma~ be of an electrical or pneumatic type or of
the exemplary type of Fîgs. 1-4. In this position of the steam
valve and actuator member 246, the first, second and third passage-
ways are closed.
In a second or purge position of the valve of Figs. 5-8
the element 256 of the steam valve and actuator member 246 is moved
downwardly to the position shown in Fig. 7. Steam flowing inwardly
through the inlet port 218 passes through the steam inlet chamber
226 the opening 234 .in the valve seat 236 and enters the steam
discharge chamber 228. Steam in chamber 228 flows to the steam
line through the steam d;scharge port 220 and also flows downwardly
about the valve element 256 and the stem or pin 254 and through
the opening 240 in the second valve seat 238 to the oil discharge
chamber 232. From the oil discharge chamber 232 the steam flows
through the oil disc~arge port 224 for the required purging of `
the fuel oil line~.
In Fig. 8 the valve is shown in its operating or running
condition. In this position the valve element 256 seats at the
second valve seat 238 whereby to close the opening 240 to the
downward flow of steam to the oil discharge chamber to 232. Thus,
steam flows through the first passageway comprising the inlet port
218, the chamber 226~ the seat opening 234, the chamber 228 J and
the steam discharge port 220 and steam is supplied as required for
combustion. The necessary supply of oil occurs through the third
passageway comprising the oil inlet port 222, the oil inlet
chamber 23Q, the seat opening 242, the oil discharge chamber 232
and the oil discharge port 224. Thus r both steam and oil are
supplied as required eor combustion and the second passageway of
the valve is positively closed at the valve seat 238 to prevent
~L0~71~3
steam leakage to the oil supply line.
Assembly and disassembly of the valve of Figs. 5-8 for
cleaning or other purposes is readîly achieved on removal of the ;~
plugs 204 and 206. The valve seats 236, 238 and 244 are threaded
into their assembled positions and can be readily removed. The ;
various sealing means associated with the stems of the steam valve
and actuator member 246 and the oil valve member 216 may be removed
and the valve members themselves may be readily removed, cleaned,
replaced~ etc.
From the foregoing, it will be apparent ~hat a valve
of a relatively simple construction has been provided. A desirably
simple and straightforward three-position mode of operation is
employed and yet the necessary selective switching of fluid flow
is efficiently achieved. Positive sealing functions are achieved
throughout and a hiyh degree of each and convenience is provided
for in disassembly and maintenance.
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