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Патент USA US3075478

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Jan. 29, 1963
Filed April 6, 1960
2 Sheets-Sheet 1
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United States Patent 0 ” 1C6
Paul J. Eii'el, Chicago, Ell, assignor to Hills-McCanna
Company, Chicago, Ill., a corporation of Hlinois
Filed Apr. 6, less, §er. No. 20,462
2 Claims. (Q1. 103-44)
Patented Jan. 2a, 1953
reduction in the pressure within the actuating space below
ambient pressure conditions.
An additional object is to provide an improved dia
phragm pump as recited in the previous objects in which
reductions in the pressure Within the hydraulic actuating
space below atmospheric pressure conditions are avoided
and optimum supplementary quantities of hydraulic ?uid
are added to the hydraulic actuating space by the oper
ation of a simple reliable valve which operates independ
The present invention relates to diaphragm pumps in
which the pumping diaphragms are actuated hydrau 10 ently of mechanical connections to other working parts
lically in a manner such that the pressure on the dia
phragms of the ?uid being pumped is opposed by the
pressure of hydraulic actuating ?uid on the diaphragrns.
Diaphragm pumps, particularly hydraulically actuated
of the pump.
A further object is to provide an improved hydraulic
ally actuated pump as recited in the foregoing objects in
which the diaphragm is supported and protected against
pumps, can be used to great ‘advantage in pumping ?uids 15 excessive hydrostatic actuating pressure in a manner
which must not be allowed to escape to the external en
which obviates subjecting the diaphragm to damaging
vironment even in small quantities.
A diaphragm pump is inherently susceptible of being
Other objects and advantages will become apparent
in the diaphragm which can cause it to fail prematurely
FIG. 2 is a fragmentary, horizontal sectional view of
from the following description of the exemplary form of
completely sealed against the escape of the ?uid being
pumped as long as the diaphragm remains unbroken and 20 the invention illustrated in the drawings, in which:
FIGURE 1 is a perspective view of a pump embodying
impervious to the ?uid. However, purely mechanical
the invention;
actuation of a pump diaphragm tends to create stresses
the pump taken along the plane indicated by the line
pressure. Stresses on a pumping diaphragm caused by 25 2—2 in FIG. 1;
FIG. 3 is a fragmentary sectional view on a greatly en
the pressure of the fluid being pumped can be greatly
in service, particularly when pumping ?uid under high
minimized by actuating the diaphragm hydraulically in
a manner such that the hydrostatic pressure of the hy—
draulic actuating ?uid opposes the pressure force on the
larged scale showing the air-liquid discriminating valve
incorporated in the pump and appearing in FIG. 2;
FIG. 4 is a fragmentary sectional view of the structure
30 appearing in the central portion of FIG. 3, but showing
the valve in closed rather than open position;
However, the actuation of a pump diaphragm by hy
FIG. 5 is a horizontal sectional view taken along the
draulic ?uid presents a number of challenging problems,
line 5-5 of FIG. 3;
which are the particular concern of the present invention.
FIG. 6 is a fragmentary sectional view on a greatly
()ne object of the invention is to provide a hydrau
lically actuated diaphragm pump having a new and im 35 enlarged scale taken along the line 6-6 of FIG. 3;
FIG. 7 is an exploded perspective view of the air
proved construction and mode of operation which as
liquid discriminating valve used in the pump; and
sures maintenance of maximum operating e?iciency and
FIG. 8 is a fragmentary sectional view showing the
output capacity of the pump at all times, while at the
pump diaphragm upon completion of a discharge stroke.
same time avoiding the application of excessive hydro
The diaphragm pump 10 forming the exemplary em
static pressure to the pumping diaphragm.
bodiment of the invention illustrated comprises a pump
Another object is to provide a hydraulic-ally actuated I
body 12, mounted as shown in FIG. 1, on one end of a
diaphragm pump of improved construction which func
frame 14 that houses a power driving mechanism 16 of
tions automatically as an incident to energization of the
generally conventional construction, which reciprocates
pump to ?ll hydraulic actuating space within the pump
diaphragm of the ?uid being pumped.
with an optimum quantity of diaphragm actuating ?uid 45 a pump actuating plunger 18. The plunger 18 extends
through a sealing sleeve 20 into a horizont? bore 22 in
and to completely free the hydraulic actuating space of
the housing 12. The bore 22 is made somewhat larger
entrapped air.
in diameter than the plunger 18, thus avoiding frictional
Another object is to provide an improved, hydraulically
engagement of the plunnger with the bore. A high pres
actuated diaphragm pump which is so constructed that
an optimum volume of actuating liquid is maintained in 50 sure seal 24 supported within the sleeve 29 in encircling
relation to the plunger 18 is designed to prevent ?uid
hydraulic actuating space in the pump, even though liquid
from escaping from the bore 22 around the plunger.
may be lost from this space through leakage or other
Reciprocation of the plunger 18 is used to effect by
wise, by operation of an air-liquid discriminating valve
draulic actuation of a pumping diaphragm 26, as will
of simple, trouble free construction which serves to re
lease and replace with an optimum quantity of liquid any 55 presently appear.
The diaphragm has a circular shape and is formed of
air or other gas which for any reason may have been en
a tough, ?exible material. The circumferential mar
trapped in the hydraulic actuating space.
ginal edge of the diaphragm is tightly clamped between
A further object is to provide ‘an improved diaphragm
two sections 2%, 30, of the housing 12, which are con
pump as recited in the preceding objects in which new
and improved pump structure provides for efficient op 60 nected together by screw elements 32, FIGS. 1 and 2.
The two housing sections 28 and 30 are formed by metal
eration of the air-liquid discriminating valve, while at the
castings which clamp the diaphragm with su?icient force
same time obviating any necessity for interconnecting this
to preclude the escape of fluid around the clamped pe
valve with other working parts of the pump.
riphery of the diaphragm.
Another object is to provide a hydraulically actuated
Thus supported, the diaphragm 26 extends across a
diaphragm pump having a new and improved construc 65
circular cavity 34 formed by two complementary circular
tion which provides for e?icient high speed operation of
recesses 36, 38 de?ned in the opposed housing sections
the pump, while at the same time serving to admit sup
28 and fill in facing relation to each other, as shown in
plementary quantities of hydraulic ?uid into the hy—
draulic actuating space within the pump only as necessary 70 FIG. 2. The cavity 34 thus formed is partitioned by the
diaphragm 26 to de?ne a pumping chamber 40 and a hy
to maintain an optimum quantity of fluid in the actuating
draulic actuating chamber 42 which are alternately con
space and in a manner which substantially avoids any
varied. and. expandsdby, agtuatiqn. of the, diaphragm, as,
placement of the diaphragm 26 with a corresponding loss
will presently appear.
The pumping chamber 40 is connected through a bore
44 with inlet and. outlet check valves 46, 48. As shown,
of pumping capacity.
means for supplying make-up ?uid to the actuating space
two inlet valves 46 are used in tandem to connect the
58 to compensate for ?uid lost from this space. Because
As a practical matter, it is necessary to provide some
48 are used to connect the bore 44 with a discharge
of the cyclic lowering of; pressure in theactuating space
58, there is often a tendency foranv excess volume of ?uid
line“ 52.
Movement’ of the diaphragm 26 to expand and con~
to ?ll up in the actuating. space 53 through any means
used to add make-up ?uid to this space.
tract the pumping chamber’ 40 produces a pumping action
which, forces fluid from the intake line 50 into the dis
change line 52.
As previously- intimated, diaphragm pumps of this
The effect of excess?uid in the space 53 is to reduce
the intake excursion of the diaphragm 26, with a conse
quent diminution in pumping ei?ciency, and to apply ex
cessive-stress tothe diaphragmwhen the plunger 18 moves
character have special advantages in pumping corrosive
to its innermost position.
bored-‘,4 with an intake line 59‘, and two outlet check valves
chemicals and other ?uids which can not be allowed to 15
Thus, in order to- obtain maximum pumping e?iciency,
it is necessary that the diaphragm 26 move in phase with
escape even in small quantites. The space within the
the reciprocating motion of the plunger 18 through the
normal excursion of the diaphragm. between normal limits
sealed against the escape of ?uid as long as. the dia
of the diaphragm motion. It will be appreciated from
phragm 26Hremains intact: The, importance of avoiding
rupture or failue of the diaphragm 26 places a premium 20 the above that this ideal‘ phase relationship of the dia
phragm motion to the plunger motion. can be disturbed
on eliminating failure producing stresses on the dia
pump, including the pump chamber 40,: is completely
phragm, particularly in the- pumpingv of ?uids under high
'by either an increase or a decrease in the volume of
?uid in the space 58. Moreover, the problem of com
pensating for losses of ?uid from the space 5.8, whileat
The diaphragm 26 is actuated by thecyclic application
of hydraulic pressure to the diaphragm in'opposition to 25 ‘the same time avoiding a, build. up of excess ?uid inthis
space, becomes more complicated as the cyclic speed
the, pressure-on, the diaphragm of the ?uid being pumped.
of the plunger 18 is'increased. This. stemsfrom the fact
that increases in the operating speed of the pump have
Thus, the diaphragm is actuated by- a quantity. of hy
draulic ?uid contained within an enclosed pumpactuating
previously been, accompanied by increases. in the degree
space which includes the actuating, chamber 42 and a
plenum space, 54, FIG. 2, which receives the inner end 30 to which the pressure in the hydraulic actuating space
has been reduced on an intake stroke. This isparticu
of the reciprocable plunger 18. The plenum space 54,is
larlyv true whenpressure reductions inthe hydraulic actu
formed in; part by a space within the. previously men
ating space have been relied on to effect movement of
tioned bore 22. The bore 22 is concentric with the dia
the pumping diaphragm in an intake direction. To in
phragm 26 and merges withva counterboreSG which ex
tends from thebottomof tl1e,cavi_ty,38;toward the plunger 35 creaselthe speed of'the diaphragm, ithas been necessary
to increase the‘ pressure reduction inthehydraulic actu
18 through a major portion of the body'section-3il. The
ating space, as intimated.
counterborev 56 provides spacefor receiving the plunger
18, when the latter isfully advanced, together with addi
tional; space for accommodatingdiaphragm biasing struc
ture to ‘be described.
Lossesin pumping e?iciency and-other: di?iculties can
arise. due to-the ‘presence ofv entrapped air in the hy
draulic actuating’ space withinla pump. ofthischaracter.
The compressibility of theair has the e?ect of reducing
The plenum space 54, communicates, freely. with the
the excursionof the diaphragm.
actuating. chamber 42. Advancement of the plunger '18
Such dit?culties associated with the construction and
forces ?uid from the plenum space?ft into the actuating
operation of prior diaphragm pumps of thischaracter
chamber 42, creating hydrostatic pressure on the dia
phragm?26 which forces the diaphragm to the left with 45 are eliminated in the improvedgpump 10 provided by this
invention. Moreover, maximum operating ei?ciency of
respecttoFIG. 2,, to expel-?uid from the pumping cham
the improved pump, even at very high operating speeds,
ber 40.
is, assured by, the. operationof- extremely'simple and in
Retractionof the plunger lg'iremovesthe plunger from
herently reliable pump structure which functions. as an
avolume of the plenum space 54 equal ‘to-the displace
?lem Of‘the. plunger, This would, 'offitself, create a re 50 incident to energization of the pump to provide and
maintain an optimum volume of hydraulic actuating ?uid
duced; pressure condition-withinithe pumping space which
in --the.actuating space 58, whileat the sametime making
would cause movement of 'the diaphragm 26 in an in
special provision for obviating any lag inthe motion of
take direction to e?ect a corresponding expansion- of the
the diaphragm 26 relative to the reciprocating motion of
pumping chamber 40, provided the-actuating space is com
pletely ?lled with an ‘optimum volume of hydraulic ?uid 55 the plunger '18. As, will be described in further detail,
the maintenance. of, an optimum volume of liquid in- the
whichdoes not. change during operationof the pump.
space 58 is achieved through a functional‘ cooperation
However, severe problems canarise during operation
of diaphragm biasing and stop means with anextremely
of the pump, due to di?iculties involved-in maintaining
simplev air-liquid discriminating check valve to release
an ‘optimum quantity of‘ hydraulic ?uid in the hydraulic
actuating space, which is designated" generally in FIG. 60 entrapped air from the space 58 andsupply an optimum
quantity of liquid to the space asan incident toenergiza
2 by the number 58. In thel?rst place, it is impossible
as a practical matter to prevent leakage of hydraulic
?uidfrorn the actuatingspaceSS past the movable plunger
18. Such leakageof actuating ?uidv can produce an out
tion of the pump.
Thus, as illustrated in FIG. 2' provision is made for
maintaining a positive pressure within the actuating
of phase relationship of the diaphragm movement to the 65 space 58 during an intake stroke of the pump until the
diaphragm 26 has been retractedto itsextreme intake po
plunger movement. ‘
sition. The diaphragm 26 is moved in its. intake direc
When an optimum volume of hydraulic ?uid is present
tion not by the force of di?erential ?uid pressure on the
in the‘, actuating space 58, advancement of the plunger
diaphragm but by the action of a biasing spring 6G,con
18 toits innermost positiondisplaces the diaphragm 26
to its’ extreme discharge position. In the event the volume 70 tinuously applied‘to the central portion of the diaphragm.
Preferably, the central portion or" the diaphragm 26
of hydraulic ?uid in the actuating space 58' has been
isclamped between two pressure disks 62, 64, which are
diminished by leakage, the diaphragm 26 does not move
fully through its normal excursion inits discharge direc
tion upon movement of, the plunger 18 'to its innermost
attached by, a screw fastener 66 to an adjacent end of a
hollow spring support sleeveié? which extends from the
The result is a diminution in the active dis 75 disk 64 into the counterbore 56, as shown in FIG. 2:‘
The biasing spring 60 is a coiled compression spring.
It is disposed in encircling relation to the sleeve 68 be
tween the periphery of the valve element and the cylin
drical wall of the cavity 88. This provides a restricted
flow passage extending axially past the valve element 102
to connect the bottom of the cavity 88 with the top of
the cavity. A small axial bore 186 is formed in the plug
tween a radial ?ange 70 on the plunger end of the sleeve
and an annular spring seat '72 anchored in the counter
.bore 56 against axial movement by an expandible snap
ring 74 seated in the wall of the counterbore.
element 92 in concentric relation to the cavity 88 to con
Movement of the diaphragm 26 in its intake direction
is positively terminated, when the diaphragm reaches its
extreme intake position, by abutting engagement of the
nect the actuating space 58 with the bottom of the cavity
ates to maintain a positive pressure on ?uid within the
of the cavity 88.
88 below the valve element 182. The reservoir 82 com
municates with the valve cavity 88 through an outer bore
sleeve ?ange 70 with the bottom of the counterbore ‘56. 10 108 formed in the valve housing element 86 in coaxial
The force of the spring 6% on the diaphragm 26 oper
relation to the inner bore 186 and opening into the top
actuating space 58 until the sleeve 68 bottoms in the
An upwardly extending stem, tang or pintle 110 cen
counterbore 56 as recited. Normally, the intake move
trally formed on the upper side of the valve element 102
ment of the diaphragm 25 will be positively terminated 15 projects ‘a substantial distance upwardly into the outer
in this manner simultaneously with movement of the
bore 108. The stem or tang 110 is ?attened on three
plunger 18 to its fully retracted position. In the event
longitudinal sides, as shown in FIG. 6, to have a triangu
there is a de?ciency of liquid in the space 58, the sleeve
lar shape in transverse section and to provide three re
68 will bottom in the counterbore 56 before the plunger
stricted fluid flow passages 112 extending through the
reaches its fully retracted position. Continued movement 20 bore 1108 alongside the stem.
of the plunger in an intake direction then causes an im
The valve element 18-2 has an axial length somewhat
mediate reduction in pressure within the space 58, to
shorter than the axial length of the cavity 88, thus pro
allow entry of additional liquid into the space through a
viding for limited axial movement of the element 102 be
special air-liquid discriminating checir valve 8% communi
tween an upper, valve closed position, shown in FIG. 4,
cating with the upper extremities of the space 58 through
and a lower, valve open position, shown in FIG. 3. The
passages which provide for free rise up to the valve of
?at bottom surface 1% of the bore 96 forms a valve seat
any air entrapped in the actuating space.
encircling the bore 108, which is engaged by an O-rin-g
Preferably, the valve 8th is mounted, as shown, in
seal 114, carried on the upper side of the valve element
the housing section St) at the bottom of a reservoir 82 for
102, to close the valve 80 ‘against the escape of ?uid from
hydraulic actuating ?uid formed in the upper portion 30 the space 58 upon movement of the valve element 102
of the housing 12. The valve 89' is covered with hy
against the force of gravity to its upper position.
draulic ?uid and opens automatically in response to a
A transverse kerf or slot 116 cut into the lower 'face
drop in the pressure within the space 58 below ambient
of the valve element 192 extends across the adjacent end
pressure conditions to admit liquid into the space 58.
of the inner valve bore 1% to connect the bore 106
After stopping in its fully retracted position, the
with the restricted cylindrical passage 104 around the
plunger 18 accelerates from a standing start in an ad
valve element 1tl2 when the latter is in its lower, open
vancing direction which tends to force ?uid from the
valve position, shown in FIG. 3.
space 58 out through the valve 80. During the period
Upon lowering of the pressure within the actuating
when the plunger 18 is near the retracted end of its stroke,
space 58 below ambient pressure conditions, due to a
any air in the space 58 rises into underlying relation to
de?ciency of ?uid within the space 58, a differential pres
the valve 80 through either a vertical internal bore 84
sure force is applied to the valve element 107. which is
communicating with the counterbore St’: or a generally
supplemented by the force of gravity on the valve element
horizontal bore 86 communicating with the upper ex
to cause it to move downwardly to its open position. A
tremity of the actuating chamber 42.
quantity of liquid ?ows through the passages 112 along—
By virtue of its capacity to discriminate between air 45 side the stem 119, through the flow passage 104 around
and liquid, the valve 88 will remain open during initial
the valve element and through the slot 116 and inner
advancement of the plunger 18, to allow air to escape
from the space 58 while responding to an incipient dis
charge of liquid through the valve to immediately close
and preclude loss of actuating liquid from the space 58.
It should be appreciated, in this connection, that the
release of air from the space 58 during advancement of
the plunger 18 serves to create reduced pressure condi
tions in the space 58 during the subsequent retraction of
the plunger 18, with the result that the displaced air is
replaced with liquid from the reservoir 82.
The construction of the air-liquid discriminating valve
8t), which enables it to discriminate between air and liquid
in allowing the escape of air while precluding the escape
bore 106 into the space 58.
In the event air is entrapped in the space 53, the air
rises through the bore 106 and upon advancement of
the plunger 18 from a standing start ?ows around the
valve element 182 and out through the restricted passages
The movable valve element 182 is rather light in
weight and will respond to a rather small upward force
55 to rise to its closed position.
However, the valve element 102 will remain in its
open position to allow ‘a substantial quantity of air to
escape during initial advancement of the plunger 18. Be
cause of its compressibility, and ‘because of its very low
of liquid, is illustrated in FIGS. 3 to 7.
60 viscosity and its inherently low ?uid friction upon mo
As shown in FIG. 3, the valve 80 comprises a small
tion, ‘air can ?ow at a substantial rate through the re
valve cavity 88 of generally cylindrical shape located cen
stricted pass-ages around the valve element 162 without
trally within a valve housing 98. Preferably, the valve
forcing the valve element into its closed position. Thus,
housing 90 is formed by a cylindrical plug element 92
the valve 88 permits a substantial quantity of air to es
threaded into a downwardly open central bore 934 in a 65 cape from the space 58 during each successive advancing
bushing element 96, which is removably threaded into the
upper end of the housing bore 84-. A cylindrical well 918
in the upper end of the plug element 92 coacts with the
?at bottom 100 of the bushing bore 94 to de?ne the valve
cavity 88.
This cavity encases and provides limited clearance
around a short, generally cylindrical valve closure ele
ment 102.
stroke of the plunger 18 until the space is completely
purged of air.
At the same time, the valve 80 is sensitive to an incipi
ent out?ow of liquid through the valve to e?’ect an imme
70 diate closure of the valve, which prevents loss of liquid
from the space 58. in contrast to the physical character
istics of air, liquid is not only virtually incompressible,
but it has a very high viscosity and a very high ?uid fric
tion upon ?owing as compared to air. Hence, an incipi
The valve closure element 182 is dimensioned dia
metrically to provide limited radial clearance 104 be 75 ent out?ow of liquid out through the inner bore 106
brings this relatively viscous ?uid intoengagement with
when the disc is in thelower position thereof passage
the under side ofv the-valve-eleinent 12%}. This impinge
ment of the liquid on the valve element, together with
the frictionaldrag onithe valve element of liquid begin
ningto ?ow through the restrict-ed passage 184 around
the valveelementandthrough the restricted passages 112‘
space around the valve disc for the in?owof ?uid from
said outer passage into said ‘hydraulic actuating space,
a valve actuating tang on said valve discextending into
one of said passages for both the upper» and lower posi
alongside the stem 110 snaps the valve element 102mm
in transverse section ‘to provide limited'pass'ageway space
uid which may for any reason have become entrapped in
disc is in its lower position and to respond to an‘ incipient
tions of the valve disc, and said. tang being'dirnensioned
extending through said one passage, past‘ said tang for
itsaclosed position.
allowing either the in?ow of liquid through said check
While the air-liquid discriminating valve 89 operates
to» admit only an optimum volume of liquid into the 10 valve into said actuating space or theescape ofgas from
said actuating space through said check valve when said
space 58, provision is made for-releasing any excess liq~
the space 58,
Anexcessofiliquid in the space 58:will causethe dia
phragmsupport disk ‘62 to bottom against the ?oor of
the housingrecess 36. The disk. 62 substantially covers
the bore44 and'serves, in conjunction-with the curved
peripheral edge 12%} of the recess 36, to provide. strong
out?ow of liquid from said actuating space through said
check valve to move-said valve-disc tosaid‘upper position
2. A hydraulically actuated-diaphragm pump compris
ing, in combination, housing means de?ning a pressure
cavity, a pumping diaphragmextending‘across said cavity
to form a ?exible partition separating the cavity-into a
supportito- the-"diaphragm, seeFIG. 8. During contin
ued advancing movement of -;the ‘plunger 18, excess liq 20 pumping chamberv and a hydraulic actuating- chamber,
uid is released fromthe space 53- by opening of a pres
sure release valve 122 connectedbetween;theicounterbore
56 and the reservoir 82-,‘as shown’ in FIG.’ 2.
In general, the pressure relief valve l22’comprises ‘a
compression-springl24 housed within a sleeve 126 to
urge a \pointedlplug 128 against ‘aseatil?ti. Fluid escap
ing past the plug 12% is discharged'into' the reservoir 82
through a port-132 in the vsleeve 126.
The -level=of;hydraulic liquid in the reservoir 82 can
he observed in‘a transparent?ller-stem»134- connected
vvith the reservoir 82wbelow the normal level v.of liquid in
the reservoir.
IlZ‘Will be appreciated that the invention is not neces—
sarily limited to the illustratedembod-iment, but includes
variants and'al-ternatives withinth-e spirithand scopeof
the‘ invention expressed in the claims.
The invention, is claimed as follows:
1.1 A hydraulically actuated diaphragm pump compris
ing, in combination, housing means tde?ning-apressure
cavity, a'diaphragmextending across said cavitytoform 40
ineans de?ning an enclosed plenum ‘space communicat
ing with said actuating chamber‘ and forming-therewith
a pump actuatingspace, a'displacementelement vcoacting
with said plenum spaceto effect-alternate contraction and
expansion thereof, a- ges-liquid discriminating check
valve including means de?ning a valve cavity located
above said actuatingtspace, means de?ning an inner valve
passage having an-inner end opening into thei-uppermost
portion of said hydraulic actuating space» and having an
outer end opening into'saidvalvecavity, saidtinner valve
passage’ being positioned so that the elevation: of! every
portion of the inner valvepassage is at least equal‘to that
of said inner end of theinner valve passage, means-de
?ning an outer valve‘ passage opening into said valve
cavity, a liquid reservoir extending above'saidcheck
valve and being connected tosaid outer valve passage
for continuously supplyingfliquidvto said outeri-valve pas
sage, said, checkfvalve including a ‘check valve element
movably disposed-in said'valve-cavity and'biased to-move
from a valve closed‘position- in which. the? valve element
closes said outer- ‘passage against'the out?ow of; ?uid
a ?exible ‘partition separating, thecavity into a pump~
therethrough to an open‘ position; said check valve ele
ing chamber and a hydraulic actuating chamber, a pump
mentand said valve cavity de?ning means-ibeingrshaped
intake spring connected to act on said diaphragm. to urge
and dimensioned in relation to each other-to de?ne, when
the latter in a direction ‘to expand vsaid pumping cham
ber and contract- said actuating chamber, positive stop 45 the check valve element is inthe o'pen-positionthereof,
‘an intermediate passage space connecting said.outer-valve
means coacting with said diaphragm to positively limit
passage with said innervalve passage to provide forthe
motion thereof in pump chamber contracting and ex
in?ow of ?uid from said outerv passage into 'saidrhy
panding directions, means- defining .anenclosed plenum
:draulic actuating space; a valvelactuating tang on-said
space communicating, with said actuating chamberv and
valve element extending into 'one‘of said'inner andouter
forming therewith a pump actuating space, a reciprocable
valve passages for both the open ‘and. closed, positions
displacementelemen-t movablewithin said plenum space
of the valve elements, and said tang- being-dimensioned
to effect alterntae contraction and expansion thereof, a
in transverse section to provide limited-passageway space
pressure relief valve‘ communicating with said pump actu
extending through said'one valve-passage past said? tang
a'ting spaceto relieve-excess pressure therein, a gas-liquid
discriminating check valve including, means. de?ninga 55 when said valve’ element is in the open positon thereof
to provide for both the intake of liquid into said by!
valve cavity locatedabove said‘ actuating‘space, means
draulic actuating space through said valve and the escape
de?ning an inner valve passage having an inner. end
of gas from said hydraulic actuating space through said
opening into the. uppermost portion. of said hydraulic actu
valve when the latter is- openv and to respond toan in
ating, space. and-havingan- outer. and opening 'into the
bottom of said valvecavity, said inner valve passage 60 cipient out?ow of liquid from-‘said hydraulictactuating
being positioned iso-thattheelevation of every portion
thereof is at leastiequal to that of said ‘inner end thereof,
means de?ning an outer valve passage opening into the
top of said .valvecavity, a liquid reservoir extending above
said check-valve, and being, connected ‘to said outer valve 65
passagefor continuously. supplying vliquidzthereto; said
check valve including a check valve disc movab'ly dis?
posed int-said‘ valve'cavity. and :biased ‘by gravity .to move
between anmupper, valve closed position in which the
valve discscloses said outer passageagainst'the outflow 70
of ?uid therethroughanda lower, valve .open position;
saiddisc ‘being slotted on the underside thereof and be
ing dimensioned inrelation to . said; cavity to provide
space through said valve tomove saidivalve-element to
the closed position thereof.
References Cited in the ?le-ofthis patent
Nixon _______ _,__,__..____‘ Nov. 22, 1927
S-herer et al. ______ _V_____ Sept. 1, 1959
Germany ____________ __ May 21, ,1959
Sampietro ___________ __ Sept.20, 1960
Bennett ______________ _.. Mar, 21, 1961
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