Note: Descriptions are shown in the official language in which they were submitted.
1~)433~4
Back round of the Invention
g
This relates in general to dispenser pumps, partic-
ularly to a type which is manually actuated to generate
an atomized spray of a fluid product.
Many liquid spray dispensers of the types presently
on the market use an aerosol cartridge to provide compressed
gas for atomizing the liquid product and driving it out
through the nozzle.
It has recently been found that certain of the gases
most often used in spray cartridges, such as fluorocarbons,
are highly toxic when inhaled by human beings. A fear among
scientists is that the substantial volume of these gases
being used all over the world may neutralize the ozone iayer
surrounding the earth, thereby admitting potentially cancer
causing radiation from the sun. Another problem arising in
prior art dispensers which employ cartridge carriers of
the aerosol type is that the product is diluted by the carrier.
Other problems inherent in usual types of prior art dis-
pensers are that, in general, for mechanical dispersion of
the liquid product, they require many intricate parts which
are expensive to manufacture and easily get out of order.
Some prior art dispensers include metal parts or springs
which are actually in contact with the liquid product, and
may thereby react, causing deterioration of the mechanism
and toxic by-products. In other types of prior art dispen-
sers, the product is prematurely exposed to the atmosphere,
becoming crystallized or hardened in and around the spray
orifice, causing clogging.
Summar of the Invention
y
Accordingly, it is a principal object of the
present invention to provide an improved type of liquid
dispensing device.
-- 1 -- `
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1~433~4
A more particular object of the invention is to
provide a liquid dispensing device which generates a high-
powered spray without the use of pressurized gases which may
have harmful or toxic effects.
Another object of the invention is to provide a
spray dispensing device in which the product is protected
from atmospheric contamination, and which can be readily
manipulated to produce a constant pressure, relatively dry
spray which does not clog the orifice of the spray nozzle.
Another object is to substantially eliminate "throttling"
or dripping from the spray nozzle.
Another object is to provide a dispensing device
with a minimum number of parts in order to provide fewer
mechanical problems and to minimize manufacturing and
assembly costs.
A further object of the invention is to provide a
dispenser with no metal parts exposed to the product, per-
mitting the dispenser to be used with a greater number of
liquid products.
These and oth~r objects are attained in the dis-
pensing device of the present invention which makes use of
a composite finger pump inciuding dual systems which operate
simultaneously and in synchronism, one system constructed
to pump the liquid product, while the other system provides
compressed carrier gas, which in the preferred embodiment is
compressed air which mixes with and atomizes the product into
a finely divided dry spray. Although the principal embodiment
will be described with reference to a liquid product, it
will be understood that application to other types of
products, such as gases or vapors, or particulate materials,
such as powders, are within the contemplation of the invention.
In a specific embodiment, the liquid pumping system
-- 2 --
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1~)4331)4
employs a hollow inner piston of the composite nozzle housing
which is constructed to move against the compression of a
coil spring in reciprocating relation to an axially disposed
cylindrical accumulator sleeve, the iower end of which pro-
vides at its center a seat for a mechanical valve having a
substantially elliptical valve head. The first stroke on
which the spray nozzle is compressed functions to prime the
pump, positively sealing closed the valve to the liquid
reservoir. On the up or suction stroke, pressure on the coil
spring is released permitting the hollow piston and spray
nozzle housing to return to normal position, creating a partial
vacuum in the discharge chambers surrounding the valve stem
as the valve head is lifted off of its seat. The liquid
product is lifted from its container through a dip tube
extending down into the liquid reservoir, past the valve
opening in the accumulator and into grooved discharge chambers
surrounding the valve stem. An automatic vent simultaneously
releases air into the container. On the next compression
stroke, the piston again moves against the valve head,
2C closing the valve and compressing and forcing the product
liquid from the discharge chambers up through the product
passage or duct along the axis of the hollow piston, where
the increased pressure forces the product liquid to push
up on a preloaded diaphragm dislodging a plug, causing the
liquid to break up and to enter an annular air and product
mixing chamber adjacent the spray nozzle.
The air pumping system operates simultaneously
with the liquid pumping system, making use of the annular
- chamber formed by a pair of upwardly directed sleeves of the
accumulator in which the outer wall of the tubular housing,
which includes the spray nozzle, moves telescopically. The
housing has an outwardly directed peripheral flange, having
A:'
1(~4331~4
spaced slots which engage guide lugs directed inwardly from
the outer accumulator sleeve. When the nozzle is pushed
down, after a short movement the annular air chamber in the
tubular housing is sealed and permits the enclosed air
to be compressed. This compressed air is forced past a
normally closed flexible seal, through a passage into the
air and product mixing chamber at the end of the hollow
piston where the liquid product is broken up to form a dry
spray which is forced out through the spray nozzle on the
second and subsequent compression strokes.
A particular feature of the invention is a locking
arrangement which can be used for shipping the unit and
making it resistant to use by small children. This is achieved
by a turn of the nozzle through a small angle in a counter-
clockwise direction, which disengages the lugs from the
guide slots, preventing the nozzle housing from being de-
pressed. An arrangement of dimples and matching bosses serves
to secure the spray nozzle housing in firmly latched position
for shipping and carrying.
Other features and advantages of the dispenser of
the present invention are the following:
(a) it does not require the use of carrier gas
cartridges which disseminate harmful gases into the atmosphere;
(b) the use of an air carrier, as opposed to the
usual fluorocarbon carriers, provides a more concentrated,
less contaminated product;
(c) mixing of compressed air carrier with the
product in the mixing chamber provides a constant pressure,
dry spray for the user, and tends to eliminate clogging of
the nozzle orifice;
(d) clogging of the orifice and pump chambers is
further prevented by means for retaining the stored product
11;1 433~4
closed to exposure to the atmosphere when the pump is in
neutral position so that the product is not left to crystallize
or harden;
(e) the pump combination of the present invention
includes no metal parts exposed to the product;
(f) because of (c), (d) and (e), the combination
of the present invention can be used to dispense a large
variety of products, such as salt solutions for deoderant
purposes, which prior art dispensers have not been able to
handle satisfactorily;
(g) the pump mechanism is simple and economical
to manufacture, assemble and maintain in view of the fact
that it includes only seven working parts, as opposed to
eleven or more in prior art dispensers;
(h) the mechanical check valves are designed to
provide positive opening and closing;
(i) means for automatically venting the air pre-
vents the container from collapsing, and enables the pump
to function correctly,
(j) the need for mechanical means for breaking up
the product is eliminated by forcing the product through a
series of serrations or past the annular shoulder surrounding
a diaphragm-supported plug, and exposing the product in the
mixing chamber to turbulence created by a high pressure
stream of air; and
(k) the locking means actuated by a slight rotation
of spray nozzle housing eliminates the necessity for an
enclosing cap.
More particularly, there is provided a pressure
actuated dispenser including a spray nozzle constructed in com-
bination with the closure of a container of a reservoir of .
fluid product for dispensing said product in a carrier gas in
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lQ9~3~4
the form of high pressure spray, said dispenser comprising in
combination: means including fixed and movable elements form-
ing an annular variable volume carrier gas chamber constructed
for compression and expansion in response to pressure and
release from pressure on said dispenser; a pump for said fluid
product, said pump including a pump chamber and a hollow stem
piston mechanically coupled for reciprocating action in
synchronism with said movable elements of said variable volume
chamber; central valve means communicating between said product
reservoir and said pump chamber; means for maintaining said
reservoir at substantially ambient pressure; means for forming
a mixing chamber surrounded by said annular gas chamber, said
mixing chamber having an aperture communicating with said spray
nozzle, and comprising a first inlet means including a normally
closed flexible member of membraneous material for admitting
said compressed carrier gas from said variable volume carrier
gas chamber to said mixing chamber, and a second inlet means
including a normally closed flexible member of membraneous
material for admitting fluid product under pressure from said
hollow stem piston to said mixing chamber; a first means res-
ponsive to an initial compression stroke on said dispenser for
simultaneously depressing said hollow stem piston to close said
central valve means, compressing the carrier gas in said a
variable volume carrier gas chamber and deflecting the normally
closed flexible member of said first inlet means to admit a
blast of said compressed carrier gas into said central mixing
chamber; a second means responsive to a subsequent return
stroke of said hollow piston stem upon release of pressure on
said dispenser, to release said central valve means and to draw
said fluid product into said pump chamber; and said first means
responsive to the subsequent compression strokes of said dis-
penser for simultaneously again depressing said hollow stem
~ - 5a -
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1~!4~3~)4
piston to close said central valve means while pumping said
fluid product from said pump chamber up through said hollow
stem piston again compressing the carrier gas in said variable
volume carrier gas chamber, deflecting the flexible member of
said first inlet means to admit a blast of said compressed
carrier gas through said first inlet means and deflecting the
flexible member of said second inlet means to admit said product
through said second inlet means to mix in said mixing chamber
to form an atomized spray of said product which is propelled out
through said spray nozzle.
There is also provided a finger actuated spray pump
mechanism having neutral and compressed positions comprising a
pump cycle, for dispensing a fluid product comprising in com-
bination: a substantially cylindrical accumulator top con-
structed and arranged to be fitted in removable relation to the
top of a container of a reservoir of said fluid product; said
accumulator top substantially closed at its upper end except
for an axially disposed valve including a valve head and a
valve opening in a housing integrally formed at the center
of said accumulator, and means comprising an air vent constructed
to admit air to said container when the interior is below
ambient pressure5 said valve opening communicating with said
reservoir of fluid product; said accumulator top including a
pair of upwardly directed coaxial sleeves forming an outer
annular chamber and an inner annular chamber coaxially surround-
ing said valve; a nozzle housing comprising a hollow cylinder
having a closed upper end including a spray nozzla, the open
lower end of said nozzle housing being accommodated for tele-
scopic movement in said outer annular chamber, corresponding to
the neutral and compressed positions of said pump cycle, and
forming with means including a portion of said inner annular
chamber a variable volume air chamber constructed to expand and
~' - 5b -
1e~433~4
contract with said telescopic motion for providing compressed
air; a receptacle including a downwardly directed preloaded
spring-biased sealing element depending in axial relation from
the upper end of said nozzle housing, a hollow piston having a
grooved fitting at its upper end, said receptacle constructed
to mate with said grooved fitting so that said hollow piston
is disposed in fixed coaxial relation with said receptacle and
said outer and inner annular chambers for reciprocating motion
in conformity with the telescopic motion of said nozzle housing
in said outer annular chamber; means comprising a spring
constructed to urge said nozzle housing and said hollow piston
to the neutral position of said pump cycle; the lower end of
said hollow piston constructed to at least partially close
said valve in the compressed position of said pump cycle, and to
release said valve to open when said hollow piston is in the
neutral position of said pump cycle, said hollow piston dis-
posed to serve as a channel for fluid product passing through
said valve; said grooved fitting forming with said receptacle
a mixing chamber and intake means; a first said intake means
for compressed air connected between said variable volume air
chamber and said mixing chamber; a second said intake means
including said preloaded spring-biased sealing element for
product fluid connected between said hollow piston and said
mixing chamber, said grooved fitting constructed during at least
part of said pump cycle to maintain said second intake means in
closed position, and during another part of said pump cycle in
response to internal product fluid pressure in said hollow stem
piston to open said second intake means in response to over-
riding pressure on said preloaded spring-biased sealing element
to admit fluld product to said mixing chamber, and to simul-
taneou~ly admit compressed air into said mixing chamber through
said first intake means where~y said compressed air atomizes
~- Sc -
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~0433Q4
said fluid product and expels atomized spray through said spray
nozzle.
There is further provided a pressure actuated dispen-
ser constructed to dispense fluid product in a compressed gas
- carrier from a container comprising a reservoir of said fluid
product, said dispenser comprising in combination: a dual
cylinder pump including an annular variable volume chamber and
a central pump for the fluid product disposed axially in said
chamber, said central pump including a pump chamber and a hollow
stem piston; a centrally disposed control valve for communicat-
ing between said pump chamber and said reservoir; said variable
volume chamber being defined by fixed and movable elements which
allow the variable volume chamber to contract and expand for the
compression and intake of carrier gas upon compression and
release from compression of said dispenser; and said hollow stem
piston being coupled for movement in synchronism with the move-
ment of the movable elements of said variable volume chamber,
to cause the closing and opening of said control valve to said
fluid product reservoir; said dual cylinder pump including a
centrally disposed mixing chamber having a first normally closed
intake means for admitting compressed carrier gas from said
variable volume chamber, and a second normally closed intake
means for admitting fluid product from said hollow stem piston,
each constructed to open in response to a preselected pressure
for mixing said fluid product with said compressed gas carrier
to form an atomized spray; and means comprising a spray nozzle
connected to said mixing chamber for exhausting said spray from
said mixing chamber in a high pressure stream.
Brief Description of the Drawings
These and other objects, features and advantages
will be better understood from a detailed study of the
invention with reference to the ttached drawings, wherein:
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1~433~4
FIG. 1 shows in perspective a container in com-
bination with a spray dispenser of the present invention;
EIG. 2A is an enlarged vertical section taken
through the plane 2A-2A of FIG. 1, showning the spray dispenser
of the present invention in neutral or suction position;
FIG. 2B is an enlarged fragmentary showing of the
lower end of housing 7 of FIG. 2A, in telescopic
engagement with sleeve 3;
FIG. 3 is an enlarged top view of the spray dis-
penser shown in FIG. 2A of the drawings;
FIG. 4 is an enlarged vertical section similar to
FIG. 2A, except that the pump is in compressed position;
FIG. 5A is an enlarged perspective showing of the
valve head of FIGS. 2A and 4, including the stem;
FIG. SB is a plan view of the valve stem through
the section 5B-5B of FIG. 5A;
FIG. 5C is a showing of the valve head of FIG. 5A
turned through an angle of 90 degrees;
FIGS. 5D and 5E disclose a variation of the valve
.stem shown in FIG. 5A, in extended and retracted positions;
FIG. 6A is an enlarged vertical sectional showing
of the upper end of the spray nozzle housing in neutral
position, showing the grooved plug and channels leading from
the interior of hollow piston 14 into the mixing chamber 23;
FIG. 6Bis a view looking up from the bottom of
plug 26 of FIG. 6A disposed in the bore of ring 25b;
FIG. 6C is a cross-section through the plane
6C-6C of FIG. 6A;
FIG. 6D is an enlarged sectional showing similar
to FIG. 6A in which the plug 26 is raised to admit liquid
product to the mixing chamber; and the co~pressed air intake
is alternatively in closed and open positions;
'A
i~4;~3~4
FIG. 7A shows a modification of the spray dispenser
of the ~resent invention in enlarged vertical section similar
to FIG. 2A;
FIG. 7B is an enlarged top view of the modified
spray dispenser shown in FIG. 7A;
Fig. 8A is an enlarged vertical sectional showing
of the upper end of the modified spray noæzle housing of
FIG. 7A with the diaphragm in neutral position, the interposed
plug having been substantially eliminated;
FIG. 8B is an enlarged vertical sectional showing
Of the modified spray nozzle housing corresponding to FIG. 8A
with the diaphragm deflected;
FIG. 8C is a detail, showing the relationship
between the annular edge 66a and the bevelled ring 65b;
FIG. 9A is an enlarged perspective showing of the
valve head assembly shown in FIG. 5A, modified to permit a
slight drainback into the reservoir when the valve is closed;
FIG. 9B is a view of the valve head of FIG. 9A
looking up from the bottom;
FIG. 9C is a view of the valve head assembly of
FIG. 9A, looking down from the top; and
FIG. 9D is an enlarged fragmentary view of the
lower end of the valve head assembly along the plane 9D-9D
of FIG. 9B.
Detailed Description
FIG. 1 of the drawings is a perspective showing
of a conventional bottle or container for a liquid product
on which is mounted a spray nozzle in accordance with the
present invention. In the present example, a small plastic
container 1 has a body portion which measures about 0.875"
in maximum outer diameter and is 11" tall, terminating at
its upper end in a conventional screw-threaded neck of reduced
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1(~433~)4
diameter, above which is an open mouth, the outer diameter
of which measures 0.775" in the present embodiment. The
bottle or container 1 may be formed of any type of rigid
plastic, glass or other suitable material.
The finger pump or dispenser of the present invention,
in accordance with a first embodiment of FIG. 2A, under descrip-
tion, comprises seven princ~pal parts, indicated by the following
lettered paragraphs:
a. The screw cap accumulator 2 includes in integral
relation a lower cylindrical skirt 2a and an annular closure
4 which fits onto the top of container 1 and is in coaxial
relation with a central valve housing 8. The upwardly directed
annular sleeve 3 coaxially surrounds spring housing 6, forming
part of the air intake chamber 18 coaxial with the upper
end 8a of valve housing 8 (see FIG. 2A).
b. The spray nozzle housing 7, the lower end of
which is accommodated telescopically in annular sleeve 3,
is integrally formed to include the laterally directed spray
nozzle 5 and an inwardly directed axially disposed spring
plug 26, surrounded coaxially by a downwardly directed tubular
recepta`cle 11. A slotted flange 7b on the lower periphery
of housing 7 is constructed to engage lugs 3a on the inside
of cylindrical sleeve 3 to maintain the housing and sleeve
in the proper orientation. Each of lugs 3a has a slightly
recessed portion 3c at one end to provide a locking mechanism
when housing 7 is slightly rotated relative to sleeve 3.
(See FIG. 3.)
c. Coil spring 13 is constructed to fit into
spring housing 6.
d. Piston tube 14 is constructed so that its lower
end fits inside of coil spring 13 and includes partway along
its length an annular flange 22 which bears on and serves
'A;
104~3~4
to compress coil spring 13. The fitting 25, which comprises
a complex hollow molding at the top of piston tube 14, i5
constructed for fixed engagement with receptacle
11, surrounding spring plug 26.
e. Valve head 10, formed integrally with valve
stem 20, which may be of cruciform section, is mounted
longitudinally in the valve housing 8, so that valve head
10 is disposed to seat in the valve opening 8e. The upper
end of valve stem 20 fits slidably into the bore 14b of tube
14, which in turn fits slidably into the upper chamber 8a
of the valve housing 8, so that the lower end of tube 14
is constructed to move against and bear on valve head 10.
f. A diaphragm 28 is constructed to seal and un-
seal a small opening 29 in the annular closure 4 to maintain
the reservoir in container 1 at atmospheric pressure.
g. Dip tube 17 is constructed to communicate
between the lower end 9 of the valve housing 8 and the
reservoir in container 1.
When the nozzle housing 7 is depressed, compressing
tube 14 and flange 22 against the coil spring 13, the lower
end of tube 14 is forced against the valve head 10, sealing
the valve closed.
In the embodiment under description, screw cap
accumulator 2 and all of its integrally molded parts may
comprise any rigid or semirigid plastic material well-~nown
in the art such as, for example, injection molded polypropylene.
Skirt 2a of accumulator 2 is one inch in outer diameter,
0.875" in inner diameter and 0.850"in vertical extent, having
inwardly directed screw-threaded grooves or, alternatively,
metal crimping, formed to accommodate the screw threads on
the container neck. Formed in integral coaxial relation
with screw top accumulator 2 is a hollow cylindrical sleeve
'A g
1~433~)4
3 of the same material, having an outer diameter of 0.775"
and an inner diameter of 0.6875" and extending upward 0.4"
above the closure 4 which forms an annular shoulder 0.1"
wide. Protruding in a horizontal plane from the inner wall
of sleeve 3 are a plurality of symmetrically spaced flanges
3a, each of which extends about 0.02" around the periphery
and which are separated by intervening slots 3b. (See FIG.
3.) At the clockwise end of each of flanges 3a is a recessed
area 3c, about 0.06" in a peripheral direction and 0.04"
wide, which functions as part of the mechanism for locking
the spray housing 7 against compression. This combination
of elements 3a, 3b and 3c cooperates with matching lugs
7b on the interior of spray cylinder 7, as will be presently
explained. This structure is indicated in detail in FIG. 2A,
which shows a vertical section through the plane 2A-2A of
FIG. 1, and in FIG. 3, which is a top view of FIG. 2A.
From FIG. 2A it is seen that the annular shoulder
4 at the top of the cylindrical accumulator 2 is a continuation
of a horizontal annular partition 0.08" thick, which extends
from the outer wall of accumulator skirt 2a to the outer
wall of coaxial valve housing 8, integrally supported at
its center.
Located coaxially inside of the outer cylindrical
sleeve 3 is the hollow inner sleeve 6, which is 0.5" in
outer diameter and 0.42" in inner diameter, extending ver-
tically upward 0.82" from the upper face of partition 4 and
terminating in an inwardly directed, curved bead 6a, 0.03"
from the top, which has a radius of 0.015". Inner sleeve
6 houses the coil spring 13. In the embodiment described,
this comprises, say, 20 coils of galvanized music wire,
wound helically to an outer diameter of 0.36". Spring 13
must be sufficiently resilient to return the nozzle 5 to its
'A- - lo
11~433~4
original position when compression is released.
The annular lateral flange 22, which is 0.06"
thick and extends 0.1" out from the cylindrical surface of
the 0.19" diameter piston tube 14, is located 0.69" above
the lower end of the latter. When tube 14 is in place, flange
22 bears against the upper end of coil spring 13, which is
disposed in the annular chamber between tube 6 and the outer
wall of tube 14.
Piston tube 14, which may be formed, for example,
of injection molded polyethylene, extends at a uniform
diameter 0.26" vertically upward from the upper surface of
flange 22 to an annular horizontal shoulder 14a, on which is
mounted end fitting 25 of reduced diameter which will be
described subsequently. The inner bore 14b of piston tube
14 extends vertically upward 1.06", at a uniform diameter
of 0.1", from the lower end of piston tube 14 in contact
with valve stem 20, forming at its upper end an internal
annular shoulder 14c, 0.02" wide, terminating in a cylindrical
chamber 24, to be described in detail later with reference
to FIG. 6A et seq.
Also, it will be seen from FIG. 2A that the upwardly
directed outer sleeve 3 and coaxially disposed inner sleeve
coil spring housing 6 form between them an annular air
intake chamber 18, 0.09" wide in a radial direction and 0.4"
deep, which cooperates with the cylindrical spray nozzle
housing 7. At the lower end of spray nozzle housing 7 which,
together with its parts, is of injection molded polypropylene,
is one of four symmetrically spaced, outwardly directed
peripheral annular lugs 7b of rectangular section, each of
which protrudes 0.03" in a radial direction, extends about
0.025" around the periphery and is 0.06" deep. (See also
FIG. 3.) ~hese cooperate with flanges 3a and intervening
'A-
10433~4
slots 3b, as previously described, to guide the telescopic
movement of cylinder 7 in sleeve 3, and with recessed areas
3c for locking against vertical motion, when cylinder 7
is turned a few degrecs on its axis.
The lower end wall of spray nozzle housing 7 has a
vertical split 7e, 0.125" long, which tapers in width from
0.02" at the lower open edge to 0.01" at the top. This
provides flexibility to the wall. Near the peripheral edge
of 7 is an inwardly directed annular bead 7c which is
centered 0.05" above the lower edge and directed 0.01"
inward. The lower edge of spray nozzle housing 7, including
outer lugs 7b and inner bead 7c, is accommodated in the
annular air intake chamber 18 between outer sleeve 3 and
inner sleeve spring housing 6. Three symmetrically spaced
vertical slots 6b, 0.05" deep and extending 0.4" down from
the top edge of housing 6 accommodate the inner bead 7c
for a vertical distance 0.1" below the upper end of chamber
18, serving as air intake valves into chamber 19. When housing
7 moves down, bead 7c seals against the wall of spring housing
6, closing the air intake slots into chamber 19.
It will be noted that at one place on the external
circular junction between spring housing 6 and partition 4
is a kickout contact button 7d which is shown in enlarged
detail in FIG. 2B. The button 7d is of substantially tri-
angular cross-section, 0.03" high and about 0.03" around
the base, having a curvilinear surface. This functions at
the end of the down stroke of the hollow piston tube 14
to raise the lower end of spray nozzle housing 7 to provide
clearance for air intake into chamber 19, and to facilitate
the return of housing 7 to its initial position.
The downwardly projecting central portion of
axially supported cylindrical valve housing 8 has an outer
- 12 -
A~-
lQ4~3~)4
diameter of 0.27" and an inner diameter of 0.19" and extends
0.26" below the lower surface of partition 4. The lower
end of valve housing 8 is partially closed by a partition
8e, 0.04" thick, which projects inwardly to form an annular
surface 0.035" wide on its upper face, operating as a cir-
cular valve seat. This provides an opening 0.12" in diameter
at its upper end which narrows to a diameter of 0.06" at
its lower end, the upper inner surface being slightly
spheroid to accommodate the valve head, which will be described
presently.
Integral with and extending coaxially downward
0.35" below the lower end of valve housing 8 is a tube 9
which is 0.19" in outer diameter and 0.125" in inner dia-
meter at its lower end. This is constructed to accommodate
dip tube 17 which may, for example, be of extruded poly-
ethylene, which is slightly less than 0.125" in outer dia-
meter and 0.060" in inner diameter and is constructed to
extend down into the bottle or container 1. At a vertical
distance 0.075" from the upper inner end of downwardly ex-
tending tube 9 is a slight shoulder 9a, 0.01" wide, which
holds the end of dip tube 17 in place. Above this shoulder
is provided a small chamber 0.11" in diameter and 0.08"
in vertical depth, functioning as a reservoir for operation
of the valve head 10.
The spray nozzle housing 7, which includes at its
upper end the laterally directed spray nozzle 5, is 0.61"
in outer diameter, 0.52" in inner diameter and 1.05" in overall
vertical extent. The wall of the housing diametrically
opposite spray nozzle 5 is 0.92" high, and the wall height
on the other side up to the lower end of the spray nozzle
opening measures 0.83".
The upper end of cylindrical spray nozzle housing 7
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.
104;~3n4
is closed except for spray nozzle 5, with a circular top
15 which is 0.04" in overall thickness, and substantially
flat, except for a series of parallel serrations 15a which
serve to provide a good grip for the user. (See FIG. 3.)
At the center of the top 15 is a tiny spheroid depression
27, about 0.1" in diameter and 0.04" deep, which functions
as a diaphragm, and has at its center a small raised contact
point 27a. Centered internally and formed integrally
with diaphragm 27, which is 0.015" thick, is spring plug
26, as will be described. The details of these elements
are more clearly shown in FIGS. 6A, 6B, 6C and 6D.
The spray nozzle 5, of injection molded polypro-
pylene, is formed integrally at one side of top 15 and takes
the form of a laterally directed frustrum of a hollow cone
with walls 0.03" thick, having a lateral opening extending
0.25" in outer diameter. The opening is rounded off at the
top and forms an upwardly directed angle of 30 with the
horizontal plane of top 15. An arrow 30 is embossed on the
top to indicate the spray direction. The maximum inner dia-
meter at the outer end of spray nozzle 5 is 0.175", decreasing
conically to 0.05" in diameter at the inner end, forming
a small cylindrical chamber 5a which is 0.03" deep, bounded
at its inner end by a wall 0.015" thick. ~his has a central
aperture 5b which is 0.015" in diameter.
Adjacent to and integral with the inner end of
the spray nozzle 5, and projecting downwardly from the center
of top 15, coaxial with internal plug 26, is a tubular
receptacle 11 having an outer diameter of 0.22" and an
inner diameter of 0.16". This is coaxially surrounded by
the outer wall of spray nozzle housing 7. On the side opposite
spray nozzle 5, the external shell of receptacle 11 extends
0.15" from the lower face of the housing top 15. At a
'~''
1(~4~3Q4
distance 0.02" below the top, at one place around its periphery,
as shown in FIGS. 6A and 6C, receptacle 11 is slotted internally
to form a channel 16 which is 0.01" square in section, and extends
0.13" vertically down, forming at its lower end a right angle
bend providing an opening which continues for 0.02" to an
outlet into annular variable volume air chamber 19. (See FIGS
6A and 6C.) Chamber 19 is formed between the inner wall of
spray nozzle housing 7 and the outer wall of piston tube 14. The
upper end of slot 16 terminates in an inwardly directed shoulder
16a located 0.06" below top 15, and cut back about 0.01"
relative to the contacting inner ring 25a, which in neutral
position bears against the interior wall of 11 about 0.01" above
shoulder 16a. As shown in the second position of FIG. 6D, the
presence of compressed air in channel 16 deflects ring 25a, letting
air into mixing chamber 23.
On the side adjacent the spray nozzle 5, receptacle 11
extends 0.16" below the floor of nozzle chamber 5a, having a
uniform wall thickness of 0.03". Receptacle 11 is adapted to
accommodate in fixed relation the upper end fitting 25 of the
tubular piston 14. The latter projects above shoulder 14a; and,
the manner in which it is fitted into the receptacle 11 is
shown in enlarged longitudinal sectional detail in FIG. 6A. End
fitting 25 comprises a pair of concentric annular rings 25a and
25b, separated by an annular groove 23. The outer peripheral edge
of end fitting 25 is 0.016" in outer diameter and projects 0.15"
vertically above shoulder 14a, terminating in external outer annular
ring 25a which is 0.01" wide. On the inner periphery, annular
inner ring 25b, also 0.01" wide, has an outer diameter of 0.01"
at its top edge and extends 0.02" above 25a. Annular groove 23,
between projecting rings 25a and 25b, is 0.06" deep, measured
from the top of 25b, and 0.01" across the bottom.
rA ~ - 15 -
~ 4~3!r)4
The internal bore 14b of piston tube 14 is 0.1" in dia-
meter and extends at uniform width 0.05" above the shoulder 14c,
at which plane it is narrowed to coaxial chamber 24 which is 0.06"
in diameter and extends 0.06" along the axis. At the upper end
of end fitting 25, above cylindrical chamber 24, is another chamber
24a of inverted conical shape, which extends 0.05" vertically,
and is concentric with the rings 25a and 25b, widening out into a
receptacle of slightly enlarged diameter, 0.07" at its upper end.
This accommodates the frustroconical spring plug 26, which, as
previously stated, protrudes downward from the semispherical
diaphragm 27, preloaded at, say, 30 pounds. The plug 26 is 0.06"
across its upper end and extends vertically down 0.04", having a
slightly smaller diameter of 0.05" at its lower end.
As shown in FIG. 6B, which is a view looking up from
the bottom, the plug 26 is fluted in a substantially vertical
direction aro~lnd its periphery to provide small channels for the
escape of liquid from the tube 14 into the chamber formed by
groove 23. Alternatively, the inside wall of chamber 24a can also
be fluted in a substantially vertical direction instead of the
fluting on plug 26. It will be seen that concentric with plug
26 on the inner surface is an annular internal shoulder 27b which
is 0.07" in outer diameter and 0.001" wide, and which fits snugly
against the upper internal side walls of ring 25b. Shoulder 27b
is held in position against the annular ring 25b until the
internal pressure of liquid passing up through the bore 14b and
accumulating in chamber 24 exceeds a given amount, causing plug
26 to move upward, disengaging shoulder 27b and thereby providing
an opening to the chamber provided by groove 23.
As previously indicated, FIG. 6A shows this internal
structure in detail when the pump is in neutral position; whereas,
FIG. 6D shows the change in the position of the elements during
the second or subsequent pressure strokes, following the suction
- 16 -
A`
11)43304
part of the pump cycle, when the internal pressure of the rising
liquid lifts the shoulder 27b off of the ring 25b. FIG. 6D also
shows shoulder 16a in both closed and open positions for the
flow of compressed air from channel 19 to mixing chamber 23.
The body portion of inner piston tube 14 has an outer
diameter of 0.19" and an inner bore diameter of 0.1", and is dis-
posed axially within the spray nozzle housing 7, extending ver-
tically down one inch below shoulder 14a. Returning to FIG. 2A,
when the outer wall of 7 is accommodated in air chamber 18,
between the outer cylindrical sleeve 3 and the inner sleeve compris-
ing spring housing 6, the lower open end of piston tube 14 is
slidably accommodated in the upper open end 8a of valve housing
8. In neutral or extended position of the pump, the external
surface of 14 extends down into 8 about 0.1" and is in contact
with the bead 8b, which protrudes inwardly about 0.01" and is
centered 0.04" from the upper end of the inner surface of 8a.
Simultaneously, 0.1" of the lower end of the internal bore 14b
of piston tube 14 is in contact with the peripheral edges of
cruciform valve stem 20.
The valve head 10 and cruciform valve stem 20, pre-
ferably of low density polyethylene, are shown more clearly in
FIGS. 5A, 5B and 5C, the latter figure showing the combination
turned through 90 degrees in a horizontal plane. The upper end of
valve head 10 comprises a cylindrical wafer 10a, 0.15" in diameter
and 0.03" thick. Formed coaxially with the lower surface of
cylindrical wafer 10a is a truncated spheroid 10b, 0.125" in dia-
meter which extends 0.04" along the axis, and appended in coaxial
relation to which is a frustrum of a cone 10c extending 0.03"
along the axis and decreasing from a diameter of 0.075" at its
upper end of 0.05" at the lower end. This terminates in a
cylinder 10d, 0.05" in diameter and 0.015" thick in a vertical
direction. On the lower end of the latter is mounted a cone 10e
.~ s-
A 17 -
lC~!4~3~4
of elliptical cross-section, extending 0.04" downward to an apex,
having at its upper end a maximum diameter of 0.08" and a minimum
diameter of 0.05".
The valve stem 20, which is 0.415" in maximum vertical
length, extends up vertically in coaxial relation to the center
of cylindrical wafer lOa of valve head 10. As clearly shown in
FIG. 5B, the cross-section is cruciform, 0.10" in maximum width,
the legs of the cross being 0.04" wide and projecting out 0.04".
At the top of the stem, one pair of legs is recessed 0.015"
relative to the other, to aid in initially orienting the valve head
10 in the valve seat 8e.
It will be understood that instead of being cruciform
in cross-sectional shape, as shown in FIGS. 5A, 5B and 5C, the
valve stem 20 can assume other forms. For example, as shown in
FIGS. 5D and 5E, the valve stem 20' is substantially round in
cross-section, except for an indentation 32 which extends several
mils in a vertical direction and is recessed about one mil into
the lateral wall of 20', and extends down to the upper face
lOa of valve head 10. Correlative to the indentation 32 is an
indentation 31 in the inner bore 14b at the lower end of the
piston 14. -The indentation 31 is similar in vertical extent and
depth to indentation 32 and is about one mil up from the
bottom end of piston 14. It will be apparent that when the
piston 14 is in raised or neutral position, the lower end 14d of
the bore 14b is sealed against the cylindrical periphery of the
valve stem 20'. When the piston is lowered, during the compression
strokes, the indentations 31 and 32 are ad~acent, as shown in
FIG. 5E, permitting liquid to pass around the valve head 10 and
into the piston bore 14b.
Drilled in the top 4 of screw cap accumulator 2 (see
FIGS. 2A and 4) is an opening 29 which is 0.02" in diameter,
leading down into the liquid reservoir in the container 1, from
A` - 18 -
lU433~4
the air intake chamber 18. The annular diaphragm 28, which is
formed of a sheet elastomer such as, for example, neoprene, is
0.02" thick. It adheres frictionally to the outer wall of the
valve housing 8, with its lower end 0.15" below the inner sur-
face of 4, forming an angle of substantially 45 degrees with
the side wall. The flat annular upper surface of diaphragm 28
is 0.13" in radial width, its inner edge 0.12" from the wall
of the housing 8. Diaphragm 28 is heId in place at its outer
end by the top of the container on which the accumulator cap
is screwed, so that it just covers the opening 29, which is
sealed closed when the pressure in chamber 33 is greater than the
pressure in air intake chamber 18 and which opens to admit air
when there is a pressure differential.
Operation of Embodiment of FIGS. 2A et seq.
FIG. 2A shows the pump in neutral position; whereas,
FIG. 4 shows the pump in completely compressed position.
On the first down stroke the spray nozzle housing 7 is
pressed down, forcing piston tube 14 by means of its flange 22,
to compress spring 13. The lower end of piston tube 14 moves
against the annular flange 10a of valve head 10, forcing the latter
into a positive seal with valve seat 8e. This closes the valve
and forces any liquid in the valve housing 8 into the grooves
of cruciform valve stem 20, or the recesses 31, 32, if a round
valve stem is used. Simultaneously, air is compressed in
variable volume air chamber 19 and forced through slot 16,
forcing ring 25a to deflect off of shoulder 16a, admitting air into
the mixing chamber 23.
On the up stroke the spring 13 returns from its com-
pressed position, shown in FIG. 4, simultaneously causing the
piston tube 14 and the nozzle housing 7 to move back to
neutral position, as shown in FIG. 2A. During this stroke,
the valve head 10 is released from valve seat 8e, and the
A -19
~0433Q4
product liquid is pumped up into the upper section 8a from the
container reservoir through the dip tube 17, through the
grooves of the cruciform valve stem 20 and the bore 14b of
piston tube 14. The diaphragm 28 ' L flexed, automatically
admits air into the container through opening 29.
On the second down stroke, when spray nozzle housing 7
is pushed down, the outwardly directed lugs 7b act as guides,
riding in slots 3b to prevent lateral motion. At the top of
the stroke, through a vertical excursion 0.1" down into chamber
18, the air intake slots 6b are open to admit air to chamber 19.
When the inwardly directed bead 7c moves below the bottom of slots
6b, the variable volume air chamber 19 is sealed and the air
in it is compressed. The increased pressure forces air up
through the slot 16, deflects the ring 25a from shoulder 16a
and causes air to be admitted to mixing chamber 23. At the
end of the downstroke, button 7d is contacted, raising the
lower end of spray nozzle housing 7, causing air to again be
admitted into air chamber 19.
Simultaneously with the downward motion of spray
nozzle housing 7, the tubular piston 14 compresses the product
in the grooves of cruciform valve stem 20 and the pressure
automatically seals valve head 10 into valve seat 8e. The
increased product pressure forces product from chamber 24 up
through slots 24a, forcing the shoulder 27b to be ~aised off
of ring 25b. (See FIG. 6D.) Thus, product liquid is forced
into the mixing chamber 23, breaking up in the process and
mixing with the compressed air which is admitted from the
opposite side of the chamber, creating a swirling motion and
substantial turbulence which serve to further break up and
atomize the product mixture, which is then dispensed as a
dry mist through the orifice 5b of spray nozzle 5.
For locking purposes of the embodiment of FIGS. 2A
20 -
1043;}~4
et seq., the spray nozzle housing 7 is lifted slightly and
turned clockwise 0.05" to provide a secure locking position,
causing lugs 7b to engage the recesses 3c. (See FIG. 3.)
This serves to secure the pump against compression for shipping
purposes and to render it resistant to operation by small
children.
Modified Embodiment
Referring to FIGS. 7A and 7B of the drawings, there is
shown, in vertical section and top view, a modification of the
embodiment disclosed in FIGS. 2A et seq. For convenience of
description of FIGS. 7A, 7B, 8A, 8B, 9A, 9B and 9C, components
similar to FIGS. 2A et seq. are indicated by numbers to which
40 has been added; thus, screw cap accumulator 42 of FIG. 7A
corresponds to screw cap accumulator 2 of FIG. 2A, etc. Unless
otherwise indicated, correspondingly numbered parts in the
embodiment of FIGS. 7A, 7B et seq. may be assumed to be sub-
stantially similar to those described with reference to FIGS. 2A
et seq., and to cooperate in a similar manner.
The principal differences between the embodiment pre-
viously described and the embodiment of EIGS. 7A, 7B, underdescription, are the following.
l. The serrated plug 26 of FIG. 2A has been nearly
eliminated in the embodiment of FIG. 7A, being replaced by a
slight central protuberance 66 having an annular shoulder 66a,
say, two or three mils thick. Diaphragm 67 is under preload
tension of, say, 30 pounds, to provide for the top seal against
shoulder 65b. (See FIGS. 8A, 8B and 8C.) The diaphragm 67,
which may be, for example, 10 mils thick, is formed of low
density polyethylene, whereas the slightly bevelled annular
shoulder 65b is formed of high density polyethylene. In
sealed relation annular shoulder 66a digs into the bevelled
surface of shoulder 65b, causing the seal to improve with time.
- 21 -
'A~
1~433~)4
The function of this change in the shape of the diaphragm 67
from the previous embodiment, and elimination of the plug
in favor of the slight protuberance 66, is to render spray
delivery more uniform and constant. Deflection of diaphragm
67 and shoulder 65a to admit liquid and a blast of air into
the mixing chamber 63 is shown in FIG. 8B. Otherwise, the
operation is substantially similar to that disclosed with
reference to the embodiment of FIGS. 2A et seq.
2. The locking feature described specifically with
reference to FIG. 3 of the drawings has been changed in the
embodiment of FIGS. 7A, 7B to substitute two circumferentially
extended lugs 47b, plus a third smaller lug 47k, all centered
120 degrees apart, instead of the four symmetrically disposed
lugs 7b of FIG. 3. In FIG. 7B, the tip of arrow 70 points,
in operating position of the pump, to the center of short lug
47k, which ~xtends about 0.14" around the periphery, on an arc
having a radius of 0.34". The 'lugs 47b comprise arcs extending
0.43" around the periphery. Each of lugs 47b and 47k protrudes
0.03" in a radial direction, being separated by intervening
slots. It will also be noted from FIG. 7A that the profile
of these lugs is slightly changed from the corresponding lugs
of FIG. 2A. Referring to FIG. 7B, the flanges 43a extend
inwardly 0.03" from the inner periphery of the cylindrical
accumulator 43 in interlapping relation with lugs 47b and 47k.
Flanges 43a are centered at angles of 20 degrees, 160 degrees
and 300 degrees, respectively, moving clockwise from the
zero position indicated by the arrow 70, the first flange
extending approximately 0.08", and the latter two extending 0.1"
around the inner periphery of a circle having a radius f
0.32". ~ecessed adjacent thereto, and about 3/64" below flanges
43a, are the annular planes 43c which 'are centered from the
reference point at angular clockwise positions of approximately
A -22-
~43304
50 degrees, 190 degrees and 330 degrees, respectively, each
extending approximately 0.2" around the periphery on a circle
having a radius of about 0.31". Near the centers of each of the
lugs 47b is a dimple 72 which is respectively designed to
accommodate a small bead 71, just above the clockwise end of
adjacent ones of the recessed flanges 43c, so that when the
cylindrical housing 47 is rotated in a counterclockwise
direction, lugs 47b engage flanges 43c and the beads 71 are
accommodated in dimples 72, firmly locking against rotation.
When the housing 47 is rotated to open position, as shown in
FIG. 7B, one of the flanges 43a on the clockwise side, and
bead 71a on the counterclockwise side act as stops, engaging
lug 47k to maintain housing 47 in proper operating position.
Stop 71a is overridden when spray housing 47 is turned to
locking position.
3. Another change in the embodiment of FIGS. 7A,
7B, relative to that of FIG. 2A, is in the shape and thickness
of the wall of piston 14, and in the relationship between the
lower portion of the piston wall and the upper end of the
tubular valve housing 8. In FIGS 7A, 7B the thickness of the
upper portion of piston wall 54 (corresponding to piston 14 in
FIG. 2A) has been nearly doubled between the upper face of
annular flange 62 and shoulder 54a. Also, for a vertical
length 0.12" from the bottom of the tube, the wall thickness
of 54 has been cut back to 0.015"; and an annular 'bead 54d,
centered 0.04" above the bottom and having a maximum thickness
of 0.02", is imposed on the outer periphery. This bead bears
against the inner wall of the tubular valve housing 48. The
latter has also been modified so that the bead corresponding to
8b of FIG. 2A has been omitted. From about 0.075" below the
~043304
top, 48 is internally tapered from a wal~, thickness of 0.05"
to about 0.025" at the rounded top edge. Thus, the lower end
wall or "skirt" of the tube 54 has been made more flexible than
in the previous embodiment, the annular bead 54d pressing
against the inner wall of tubular valve housing 48 to provide
a better seal.
4. Further salient features of the embodiment of
FIGS. 7A, 7B, particularly as indicated with reference to
FIGS. 9A, 9B, 9C and 9D, are several slight but significant
changes made in the shape of the valve head 50 which replaces
the valve head 10 of FIG. 2A. The overall length of the valve
head assembly, including cruciform valve stem 60, has been
reduced to 0.430" to increase the capacity of the pump. Valve
stem 60 is centered on the upper face of cylindrical
wafer 50a, which is 0.14" in diameter and 0.03" thick. On
the under surface of the latter is mounted a spheroid section
50b, 0.045" along its axis, and having a radius 0.065"
centered 0.01" above the lower face of 50a. Centered on the
plane circular face on the bottom of 50b is a cylinder 50f
which is 0.01" thick and 0.078" in diameter, the lower end
being tapered conically along an axial distance 0.021",
terminating in a cylindrical wafer 50d having a thickness of
0.004" and a diameter of 0.05". On the latter is centered the
base of the tip portion comprising a cone of which the circular
sides have been flattened to make it substantially elliptical
in shape, as indicated in FIG. 9B, having a miximum diameter
of 0.078", a width of 0.050", and extending 0.05" along its
axis, terminating in an apex at the bottom. The side elevation
is shown in FIG. 9D.
In order to prevent what is termed "throttling" or
dribbling from the spray head between blasts of spray~ it is
deslrable to provide a clearance between the valve head 50 and
-- 24 --
"~
104;~;~04
the valve seat 48e, so that when the valve is closed a Qmall
amount of liquid is dumped back into the container through the
tube 57. One method of providing such a clearance is by means
of a vertical slot 50g, which may be, as a maximum, say, 10
mils wide and 5 mils deep, extending tllrough the thickness of
spheroidal member 50b. Another alternative is to reduce the
diameter of spheroidal member 50b so that when valve head 50
is seated in valve seat 48e (FIG. 7A) a slight clearance
allows some liquid to pass through. Thus, when the spray
nozzle housing 47 is depressed quickly to operate the pump and
the valve seats, a small proportion of the liquid passes back
into the container; whereas under slow finger compression all
the liquid returns to the container. In the latter case high
pressure is prevented from building up in the internal chamber
of piston 54 which would tend to override the force of 30
pounds on the diaphragm 67, causing it to unseal and le~k
liquid out of the spray nozzle between pump strokes. With the
modified valve head, as shown in FIGS. 9A, 9B, 9C and 9D, the
spray emerging from the nozzle tends to be more uniform and
constant in volume than in the case in which the valve head
seats tightly.
5. Another modification in the embodiment shown in
FIGS. 7A, 7B is provided by replacing the molded rubber gasket
28 of FIG. 2A with a substantially flat die-cut gasket 68 of
natural or synthetic rubbers such as, for example, neoprene or
the material known by the trademark "Buna", or other flexible
material. The gasket 68 is flat, 3/4" in outer diameter and
1/2" in inner diameter and about two mils thick. In the cover
of the accumulator, the opening 29, as shown in FIG. 2A, has
been replaced in FIGS. 7A, 7B by a substantially larger
circular opening 69 in the cover 44, which communicates between
chambers 58 and 73. The upper portion of opening 69 is
- 25 -
-A~
1043~04
substantially equal in diameter and depth, being about 0.06";
and it narrows down to about 0.025" across at the lower end.
Gasket 68 is friction fit so that it seals to the wall of housing
48d, its inner end extending 0.06" below the under face of
partition 44. The flat annular upper surface of diaphragm 68
is secured in place by the neck of the container 1 ~(FIG. 1)
when the cap is fastened in place thereon, so that it just
covers the opening 69, which seals closed when the pressure in
the chamber 73 is greater than the pressure in air intake
chamber 58 and which opens to admit air when the pressure in
the container falls below atmospheric pressure. This serves
to replace air which has been removed from the container
through pumping, or normal atmospheric pressure changes, main-
taining the product liquid at substantially atmospheric pressure
in the container.
The following are salient features of the present
invention.
a. The top seal is preloaded, allowing the valve to
open only when in use, eliminating crystallization and clogging
or dripping at the orifice.
b. The pump can be securely latched in an inoperative
position for shipping or carrying.
c. A blast of compressed air mixes with the fluid
product to produce atomization without a mechanical swirl
chamber, and serves to clean the orifice after each stroke.
d. There is no metal in contact with the product,
and the check valves are of plastic characterized by positive
opening and closing, so that corrosion is substantially
eliminated.
e. The product delivery rate can be increased or
decreased by merely increasing the capacity of the piston, or
by changing the sizes of the orifices.
~h 26 -
1043304
f. The spray is delivered at a constant pressur~, and
throttling and dribbling from the nozzle are substantially
elimil ted.
g. The automatic vent from the accumulator cap
substantially eliminates the problems of leakage from the
nozzle and collapse of the container.
h. The combination of the present invention has
many fewer parts than similar prior art devices.
For the purposes of the present invention, the term
"fluid" may be defined as a mass of material which readily
flows and changes shape. Although a preferred application of
the invention is to dispense a high pressure spray of a liquid
product, which may include oil, it will be understood that the
principles of the present invention can also be applied to
dispense certain types of gaseous or vapor products, or
alternatively, powdered or particulate products, in a compressed
gas carrier. Whereas in the preferred embodiments of the
invention, it is contemplated that compressed air will be
used as the carrier gas, it will be understood that the principles
of the present invention can be applied to any gas in the
environment surrounding the dispenser which can readily be
compressed to serve as a carrier for the product.
It will be further understood that this invention is
not limited to devices of the specific materials, forms or
dimensions of the disclosed examples or to the specific features
or advantages set forth. It will be understood that the parts
could be made from any semirigid plastic material which is
impervious to air and does not react in a manner to produce
toxic by-products with the liquid product of the container. The
present examples are submitted for the purposes of illustration
only, and are not to be construed as limiting the scope of
the invention, which is defined by the appended claims.
'A~
- 27 -
