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Патент USA US2129828

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.Sept. 13, 1938.
w.'1-. bu-NN-
Filed July 5, 1935
4 Sheets-Sheet l
Mllr'am 7.’ Dan’?
Sept. 13, 1938..
~ 7150MBv
Y Filed July 5, 1955 ‘
4 sneeté-sheet 2
/44 _ M21121?” Z'Dzlzzn
Patented Sept. 13, 1938
Mich., assignor to
William T. Dunn,
Chrysler Corporation, Highland Park, Mich., a.
corporation of Delaware
Application July 5,_ 1935, Serial No. 29,777
2 Claims. (01. 103-162)
showing a. modi?ed arrangement of springs for
This invention relates to pumps and’ refers operating the pistons.
more particularly to improvements in pumps _ Fig. 5 is a similar view of a further modi?ca
adapted to produce and maintain pressure on a
?uid, such as oil, suitable for use in systems of
tion of my invention.
Fig. 6 is a sectional elevational view of another 5
modi?cation of my invention, the view being
taken along line 1-1 of Fig. 6.
Fig. 7 is a sectional plan view along line 1-—'I
of Fig. 6.
Fig. 8 is a'sectional elevationalview of a fur
ther embodiment of my invention.
Fig. 9 is a sectional view taken as indicated by
motor vehicle transmission control although my
5 improvements are adaptable to a wide variety of
applications. As illustrative of one system of
transmission control to which my pump is adapt
able, reference is made to the copending applica
10 tions Serial No. 724,434 ?led May 7, 1934 and
Serial No. 752,948 ?led November 14, 1934.
One object of my invention is to provide an
improved pump which will e?iciently and quickly
provide a relatively high pressure of the oil, such
15 pressure being maintained preferably without re—
line 9-9 of Fig. 8.
Fig. 10 is a view generally similar to Fig. 1 but
showing another modi?cation of my improved
quiring operation of the pump after the required
pressure is maintained.
Further objects of my invention are to provide
stator for the pump shown in Fig. 10.
Fig. 11 is a sectional elevational view of the
Fig. 12 is a sectional plan view through the
a pump having improved characteristics of self
20 regulation in its delivery; improved balance of
the ‘parts; a pump capable of long and continu
pump of Fig. 10, the section being staggered at
the stator as indicated by the line 12-12 of .
Fig. 11.
_ ous service, as is required in motor vehicle con
trol, without undue heat generation, noise, wear
or failure through other causes; and having im
25 proved means preventing the trapping of air in
the pumping system. ‘
operating springs.
l6-l6 of Fig. 15. ,
Fig. 17 is a diagrammatic view of the pump
corporating an improved'arrangement of control
of the swash plate or wabble plate for operating
35 the pistons to produce'and maintain the oil pres.
sure at the pump delivery without objectionable
stator and rotor ports during cut-off of fluid
“hunting” or ?uctuation in the control of the
?uid pressure.
portion of a‘motor vehicle transmission casing
my pump.
Fig. 2 is a sectional plan view along line 2--2 of
Fig. 1.
Fig. 3 is a sectional view taken as indicated by
the staggered line ‘3-3 of Fig. 1.
Fig. 3A is a detail sectional view along 3A—-3A
showing the porting action‘.
Fig. 3B isa view corresponding to Fig. 3A but
showing the parts in a later stage of the porting
Fig. 4 is a view generally similar to ‘Fig. 1 but
'Referring to Figs. 1 to 3 the pump illustrated
in this embodiment of my invention comprises a
suitable supporting structure A which may be a
Further objects andadvantages of my inven
tion will be apparent from the following detailed
description of several embodiments of my invention, reference being had to the accompanying
drawings in which:
Fig. 1 is a sectional elevational view through
Fig. 14 is a sectional elevational view of an—
other modi?cation of my pump.
Fig. 15 is a sectional plan view taken along line 30
|5-l5 of Fig. 14.
Fig. 16 is a detail sectional view along line
Another object of my invention is to provide a
pump of relative simple construction, having its
operating parts compactly arranged for manu
30 facture and assembly at relatively low cost.
In carrying out the foregoing objects, I prefer
ably provide a pump of the swash plate type in
Fig. 13 is a fragmentary view in sectional ele
vation of a portion of my Fig. 1 pump but illus- '
trating a further modi?ed arrangement of piston
formed with the generally cylindrical portion 20
thereof adapted to house the cylindrical pump
rotor 13.
Rotor B comprises a lower enlarged body 2|
and an upper body 22 secured together by fas-i
teners 23. The upper body 22 is suitably driven
by a gear 24 connected by interlocked teeth 25
with the upper end of body 22, the gear being
rotatably journalled by an anti-friction bearing
26 mounted adjacent the-upper end of a stator
C. The upper and lower ends of the stator are
respectively centered and ?xed within the sup
port conduit 21 ‘and the cylindrical boss 28 of
a casting 29 which houses the lower parts of the
pump mechanism, this casting being secured to 55
support A by fasteners 30.
The bodies 2| and 22 have the axial bores 3|, 32 I The plate D will thus assume an angle depend-'
rotatably engaging the I stator C. Body 2| has ing on .the pumping requirements and normally
an annular series of cylinders 33 extending there
the pump, after producing the desired pressure,
through parallel to the body axis, these' cylinders will become inoperative insofar as reciprocation
each slidably receiving a piston plunger 34. Each of the pistons is concerned until such time as the
piston has an upwardly opening bore 35 accom
pressure falls for any reason. With the pump
'modating a spring 36 acting between the upper operating at maximum delivery capacity, pistons
body 22 and the piston for yieldingly urging the 35 closely approach the upper body 22, thereby
piston downwardly to maintain the lower round
insuring against entry-of air into the system.
10 ed. end 31 thereof in contact with the upper ele
The delivery pressure may be readily varied by
ment or ring 36 of a swash plate D. The lower adjusting the tension of springs 51, 58 at the 10
element 39 rotatably supports the upper ring by abutment 55.
the anti-friction bearing 390 and is rigidly
The passages 45, 5| are preferably milled saw
mounted on spaced arms40 secured to a shaft 4|
kerfs for low cost manufacture, these pairs‘of
16 journalled at its opposite ends at 42, 43 in cast‘
passages being preferably vertically communicat
ing 29 for pivotal movement by an arm or lever ing whereby. passages 45. function alternately 15
44 ?xed to shaft 4i and thus movable with arms both as delivery and inlet passages for cyl
40 as will presently be apparent.
Radiating inwardly from the upper ends of each
20 cylinder 33 is a slot-like conduit 45 providing an
inlet for the ?uid to each cylinder. Stator C has
an axial bore 46 for supplying the ?uid upwardly
from a reservoir in support A, the ?uid level be
ing well above Opening 47 to deliver the‘ oil
25 through transverse stator passage 48 communi
cating with bore 46. The latter bore terminates
at 49 just above the radially extending out
- wardly ?aring delivery passage 50.
The upper body 22 has its under face formed
with circumferentially spaced radially extending
milled slots 5| forming pressure delivery pas
sages between the respective cylinders 33 and
the stator.
The stator has an upwardly ex-'
tending delivery bore 52 which terminates just
35 below a second radially extending outwardly
?aring passage 53 which extends 180° from pas
sage 50. The upper end of bore 52 delivers ?uid
to conduit 54 in the support 21 and is suitably
conducted to the points of use of the fluid under
40 pressure produced by the pump.
The arm 44 carries an adjustable abutment
screw 55 pivotally seating spring abutment 56, a
spring assembly 51, 58 acting between casing abut
ment 59 andabutment 56 tending to yieldingly
45 tilt the plate D as shown in Fig. 1.
The spring
assembly determines the oil pressure maintained
by the pump as will be presently apparent. '
In operation of the pump in Figs. 1 to 3 as
thus far described, the bodies 2|, 22 are rotated
as a unit by drive gear 24, pistons 34 -being
reciprocated by swash plate D and springs 36.
As the pistons pass passage 50 they are moving
downwardly and thereby drawing oil from the
reservoir to bore 46 for delivery through pas
sage 50 and passages 45 then in communication
therewith; the remaining pistons moving up-v
wardly and delivering oil under pressure from
their cylinders 33 through the associated passages
- 5| and thence to the passage 53 and conduit 52.
The intake and delivery through conduits 46
and 52 is thus continuous and the pressure
rapidly builds up to the desired value determined
by the strength of spring assembly 51, 58 and
theratio of the leverage of ‘arms 44 and 40 about,
65 pivot 4|.
When the delivery pressure tends to exceed. the
'desired value, which may run in the neighbor
hood of 500 pounds per square inch for trans
mission control systems, the delivery pressure act
ing through the upwardly reciprocating pistons
34 causes plate D to level off about pivot 4| fur
ther compressing springs 51, 58 and thereby re
ducing or eliminating reciprocating movements '
of the pistons depending on the rate of use of
75 the oil‘ pressure or rate of .fall in such pressure.
inders 33.
As a further feature of my invention, I have
provided means for balancing the __side thrust 20
between stator C and body 22 occasioned by the
radial high pressure passage 53. Thus, above
passage 53 and extending 180° therefrom is a
further similar passage 6'0 ‘between conduit 52
and the inner walls of body 22, it being apparent 25
that in this manner the side thrusts are balanced
out. In the absence of my pressure balancing
port“, the stator C and body 22 are relatively
displaced by the ?uid pressure giving rise to
leakage between these parts. This relative dis 30
placement exposes more area of these parts to
the high pressure fluid which in turn produces
more separation and more leakage.
4 Above the pressure thrust balancing passage
60, the stator is formed with a series of axially 35
spaced narrow circular grooves 6| forming a
labyrinth seal against the escape of oil outwardly
between body 22 and the stator.
If desired, a cylindrical shield 39| may be sup
ported between casing parts 20 and 25 to sur 40
round bodies 2| and 22 to prevent undue foam
ing and splashing of any. oil thrown from the
pump bodies.
' 1
By reason of the arrangement of ?uid circula
tion through stator 0 whereby the oil enters at 45
the lower end and is delivered at the upper end,
I have provided, a “uni?ow” action of the oil,
preventing air hammer, air trapping, and air
pounding. It is, of course, highly desirable to
provide noiseless pump operation and my pump
has improved characteristics, of quietness of 50
operation. Furthermore, since the pistons are
not reciprocating the majority of the time, the
life of‘ the pump is materially increased over
prior known types of pumps adaptable to the 55
uses suggested hereinabove.
In order to limit upward movement of pistons
34 under the action of springs 51, 53 and plate
_D and to also adjustably vary themaximum
stroke of the pistons with accompanying varia- ,
tion in the pump discharge, I have provided the
element 39 with a second lever arm 392 which
extends oppositely from arm 44 ‘but integral '
therewith. Arm 392 carries an adjustable set
screw 393 which strikes a bracket stop 394 de
pending from support A. The set screw pro
vides the means for adjusting the stroke of the
pump as aforesaid. -
With the rotation of- body members 2|, 22 as
indicated by the arrow in Fig. 3 the pistons 34 70
progressively move upward, pumping oil, for
those cylinders which have their discharge slots
5| communicating with the stator pressure cham
ber 53. When each of the slots 5| reaches the
enduof chamber 53, the pressure discharge‘ 75
spring 3|;b surrounding the body 2|h for urging
through such slot ceases at a point in the rota
tion of body 2| where the piston is approxi
mately at its uppermost limit of movement. The
piston associated'with such slot is then momen
tarily sealed from communication with stator
chambers 53 and 55 by the stator walls between
all of the pistons against the swash plate Db.’
To this end the pistons 3'4b are joined, for rela
tive movement nevertheless, by a ring 63 passing
holes in through the lower ends of the pistons.
Seating on this ring and loosely receiving the
pistons therethrough is a plate 64 on which spring
these chambers. Continued rotation progres
sively brings passages 45 into communication
3Gb acts.
with stator intake passage 5|], the pistons mov
ing inwardly. Slots 5| are closed ‘on from com
munication with chamber 53 during the time slots
45, which are associated with such closed off slots
5|, are open to the intake chamber 5|]. Approxi
mately half of the cylinders are continuously op
erating for intake while approximately half are
ends of cylinders 33*‘. The cylinders may thus
be formed completely through body 33b which
The upper end of the spring abuts
the outer portion of a frusto conical ring 65
which seats on a similar face of body 33”, through 10
an intermediate gasket 56, for closing the upper
is a unitary structure driven as before by a
gear 24*’. .
continuously operating for pressure discharge of
the ?uid, assuming of course that the plate D
is not levelled off.
?tted to the cylindrical part of body 2|b above
I have further provided means for preventing
what is known as a “wire drawing” e?ect in ?uid
pumps. This effect is in the nature of a knock
or hydraulic hammer resulting from too abrupt
ly cutting off the pump ?uid pressure delivery.
To a lesser extent these objectionable noises often
occur at other points in the cycle of pump opera
passages 53“ and 53'’, a threaded nut 61 holding
the ring 65 in position.
The stator Cb has its lower end'formed with 20
a plate 53 formed with a supporting shaft 4|b
on one side of the stator and a boss 69 on the.
other side. Plate Db pivots on shaft 4|b and has
a lever extension 44b provided with forked ends
tion such as at intake cut-off for each cylinder.
10 receiving therebetween a cup 1| having a 25
lever flange 12 against which the lever ends 10
act. The boss threadedly receives the upstand
To overcome these objectionable noises, I have
provided a porting structure having a very grad
ual actioh and a typical arrangement will be
described in reference to the pressure delivery
It will be noted'from Figs. 1 and 3 that the
generally vertically extending walls of chambers
50 and 53 are curved.
The ring 65 has an upper cylindrical portion
ing pin 13 which passes through the upper end
closure 14 of cup 1| and threadedly receives stop
washer 15 and nut 16 adapted to adjustably limit 30
upper movement of cup 1|.
This cup is urged
upwardly by a spring 51b centered by boss 69 and
surrounding pin 13. By adjusting the'nut 16 it
will be apparent that the maximum. upward
movement of pistons 34b is adjustably controlled 35
This produces a desired
curved edge at the ends of these chambers where
the stator controls porting events with passages
45 and 5|. For convenience the said curving is
as well as the pump stroke in a manner similar
carried across the chambers 50 and 53 although
‘The operation of the Fig. 5 embodiment is sub
stantially similar to the Fig. 1 arrangement. 40
When the plate Db levels off under the pressure
developed by pistons 34”, the lever ends 10 de
press cup 1| against spring 51“, it being noted
that in this instance the fulcrum 4|b of the plate
Db is on the opposite side of stator Cb from the 45
spring 51b. The oil is suppliedv to conduit 46*’
through inlet passage 48*’ as before.
Referring now to the‘Fig. 6 embodiment of
my invention, the stator Cc surrounds the rotat
disposed body 2|° driven by gear 50
_ able centrally
24°. ‘This body is formed with downwardly open
the controlling edges alone provide the desired
functions being now considered. Furthermore
other edges than curved may be employed within
keeping of the broader teachings of this phase of
_ my invention just so
action is obtained.
long as a gradual porting
In Fig. 3A I have illustrated a passage 5| ap
proaching cut-off from pressure chamber 53, the
piston associated with such passage 5| nearing
the top of its stroke. In Fig. 3B, the same pas~
sage has rotated or moved from the Fig. 3A po
sition and is just completing the pressure cut-o?.
to the adjustment of the set screw 393 in the
Fig. 1 embodiment.
This cut-off action is very gradual as the trail
ing cylinders 33° receiving portions 34° urged
ing edge of passage 5| progressively eclipses the
curved edge of chamber 5|. A similar condition
is preferably provided at the other porting events
of the pumping cycle as will be readily under
by springs 36° against the plate D° > pivotally
supported at 4|° between the vertical axis 11 of
the plate lever portion 44°. The 55
In the Fig. 4 embodiment of my invention,
most of the parts are identical to those in Fig. 1
as indicated by the same reference'numerals.
However, in Fig. 4 the pistons 34“ are solid and
60 springs 36° associated therewith are located above
the pistons, the body 22a being enlarged to pro
vide the spring receiving pockets 62.
Referring to the embodiment of my invention
illustrated in Fig. 5, the stator Cb‘has its intake
65 bore 46” offset from the stator axis containing
delivery bore 52*’. the inner ends of these bores
overlapping axially and respectively communicat
ing with radial outwardly ?aring intake and de
livery passages 50b and 53b respectively. The
70 latter passages respectively communicate through
a series of circumferentially spaced conduits 45b
and 5|b with the similarly arranged cylinders
33“ having pistons 34b associated therewith.
.In Fig. 5 I have provided a single common
plate in this instance has a hardened wear re
sisting insert 18 slidably engaging the pistons 34°.
The stator is formed with the diametrically op
posite fluid inlet and dischargev passages 50° and
53° respectively, these passages being alternately 60
open to cylinders 33°, as body 2 |0 rotates, through
the radial passages 45°. The ?uid intake to pas
sage 5|)c from the fluid reservoir is provided by a
vertical conduit 46° provided in the stator while
the pressure discharge in this instance .is di 65
rected downwardly through conduit 52°.
The discharge passage 53° has an extension 19 '
at which the stator has upper and lower .bores
83, 8 |' communicating therewith. Bore 80 accom
modates a pressure relief valve 82 seated by 70
spring 83, a relief discharge port 84 being pro
vided for bore 80 above valve 82.
Bore 8| slidably receives a control plunger 85
having its upper end exposed to the ?uid pressure
_of passage 53° and having its lower end engaging
lever 44°. By reason of the offset between axis for operation on a- vertical axis of rotation instead
11 and pivot shaft HQ it will be apparent that » of horizontal.
a majority ‘of the pistons 34° will act to urge plate
" Referring to Figs. 10 to 12, I have illustrated
D‘2 to its inclined position as illustrated in Fig. 6.‘
a further embodiment of my invention closely
The pressure 'rise, above a predetermined amount similar to the Fig. 1 embodiment (as indicated
depending on the diameter of plunger 85, strength by the use 'ofumany similar reference characters)
of springs 36°, length of lever 440 and other fac
but differing therefrom primarily in the manner
tors, will act through the plunger to level off of balancing the stator and pump body against
the swash plate as before described.
In this embodiment of my invention, the swash
plate is arranged so that in leveling off toward
its horizontal position the pistons 340 move up
wardly (rather than downwardly as in Figs. 1,
4 and 5). This has the advantage of positioning
15 the pistons, when levelled off, at or very close
to the cylinder closing walls 86 where the pistons
normally lie at the tops of their working strokes. _.
Thus the volume of oil trapped‘ above the pistons
is a minimum resulting in reduced air trapping
20 and noise. Any leakage including ?uid pressure
loss due to porting as the pump body rotates at
the level off condition, results in the plate Dc
adjusting itself for a small movement of pistons
34c and this sometimes produces objectionable
25 noises unless the clearance space above the pis
tons is maintained relatively small. - The circular
form of passages 450 provides gradual eclipsing
with the edges of passages 50° and 53c to obtain
the advantages set forth in connection with
30 Figs. 3A and 3B.
Referring to the embodiment illustrated in
Figs. 8 and 9 I have illustrated my pump rotat
relative displacements resulting from the pres
sure of the ?uid.
The oil is drawn into the stator Ce through
inlets 486 to bore 468, thence to the inlet cham
ber 50‘? for admission to cylinders 33 through pas
sage slots 45. The cylinders deliver the oil under
pressure to the chamber 538 whence the oil passes
through delivery bore 528 to its points of use.
One feature of‘ my present arrangement re
sides in the provision of a compact structure
occupying less space than usual together with
less pump Weight and cost by overlapping the
chambers 50° and 53e in the direction of the
axis of stator C9 as is clearly shown in Figs. 10
and 11.
As another feature of this embodiment of my
invention, the pressure balance for the stator
and rotating bodies 2| and 22 is divided attwo
points so that the opposing or counteracting
pressure acts below the chamber 538 as well as
thereabove as in Fig. 1 at chamber 60. Thus,
pressure balancing stator chambers 66° and 601
respectively communicate by stator passages 90,
9| with bore 529 and chamber 53*’. In this man
ably about a horizontal axis instead of a vertical ner the stator is relieved of any tilting‘ tendency
axis. The transmission drive shaft 81 passes ' since the balancing forces do not produce a
35 freely through the rotatable body 2N driven as couple as in Fig. 1. At the same time separat
before through coupling 251, this body having
horizontally disposed cylinders 33d accommodat
ing pistons 34d, the intake and delivery passages
ll5d communicating alternately with the intake
and delivery passages 5i!‘1 and 53d of stator C“.
The body ‘Md may be driven with shaft 81 but
is preferably driven separately at a higher speed
from shaft 81 or other power source so that when
ing tendency between the stator and rotating
pump bodies with resulting leakage and binding
is prevented.
From Fig. 12 it will be noted that the pistons
reach top dead center just prior to cut-off of ,
?uid pressure delivery from»successive passages
5|. This condition is illustrated for the upper
most cylinder in Fig. 12. In this manner I pre
the motor vehicle idles or drives slowly, the pump
45 will be rotated su?iciently fast to build up and
vent carrying over a pressure in the passages
maintain the desired oil‘pressure. Oneof the
complete evacuation without producing hydraulic
ends of the pistons are loosely tied by a ring 63d
(as in Fig. 5), the pistons acting against ring
33‘1 of plate D4. The latter plate comprises bear
ing 390‘! and lower ring 38‘1 having a lever ex
tension 44“. The plate ass'emblypd is pivotally
supported by ears 394 projecting from plate 39d,
these ears being pivotally supported at 4|d from
the casing structure.
Only every third piston 34d has a spring 364
urging the piston outwardly. However, the pis
tons are tied together by ringj3dras aforesaid
5| to the intake passage 50e and allowing for
hammer noises and shocks. A slight amount
of vacumn is created in each passage 5| and
associated cylinder between pressure cut-01f and
intake thereby producing a rapid in?ow of ?uid
at the start ofthe intake cycle for each passage
In the same manner the arrangement is
such that for intake cut¢o? each piston reaches
bottom dead center just before cut-o?' takes
place, providing for more efficient intake an
general pumping e?iciency.
Referring to' Fig. 13, I have illustrated only
so that movement of all pisto/n’s in following the - a portion of the pump structure intended to be
inclination of the swash plate is assured. Plate identical to that of Fig. 1 excepting that the
D‘ is pivoted at the horizontal axis of the pump pistons 341 have an individual spring 361 sur
and the normal tendency for the plate to tilt as rounding each piston instead of being located
in Fig. 8 is produced by a spring 5‘!‘1 opposed by within each piston as in Fig. 1. Each spring
a plate controlling plunger 85[1 exposed at its in
acts between an abutment 92 carried by a piston
ner end to the discharge passage 53d.‘ The plung
and a relatively ?xed abutment provided by cy
65 er functions similarly to plunger 85 of Fig. 6 lindrical recess 93 in the rotatable body 2|‘.
in leveling oif plate Dd in response to abnormal Obviously any of my other embodiments may
‘rise in the ?uid delivery pressure. In Fig. 8 I have the pistons thereof provided with exterior
it will be noted that the ?uid enters chamber individual springs if desired.
504 through intake 88 and leaves chamber 53d
In Figs. 14 to 17 I have illustrated a. pump
70 through outlet 89, the ?uid travelling transversely structure embodying many of the novel features
to the horizontal pump axis along a substantially particularly of the Fig. 6 embodiment, asiwell as 74
vertical plane, the delivery of the cylinders prer ' other embodiments.
erably being at the highest points inwardly of the
The stator Ct draws oil through bore 461 which
cylinders, as before, to prevent airtrapping. ‘Ob
opens to intake chamber 53'f passes oil under
75 viously, if desired, the pump may be positioned
pressure through bore 52' and thence through
of the ?xed casing 211. The pistons
site ends thereof, said stator inlet end project- »
ing into a reservoir containing ?uid to be
34’, swash plate D1 pivotally mounted at M!
with lever M’ "i=1 oil pressure operated leveling
pumped, a rotor surrounding said stator coax
off plunger 851 s.» -'--r.-~: as described in connection
with parts corresponding thereto in Fig. 6. How
ever, in Fig. 14 the plunger bore 8|! communi
bore 54‘, a pressure relief valve
~ cates with the
821 being provided thereabove. In order to pre
vent too sudden movements of control plunger
85‘ and plate D‘, the bore 8|‘ contains a ?xed
ba?le 94 having a restricting ori?ce 95. The
baffle acts as a dash pot to check undesirable
?uctuations and sudden movements of the swash
ially therewith, said rotor having a plurality of
cylinders spaced around said axis, pistons in said
cylinders respectively, a pivotally supported
wabble plate surrounding ,sa'd stator in engage
ment with one end of said pistons, said rotor
having a plurality of ?uid conducting passages
respectively opening to said cylinders, said stator 10
having inlet and delivery ports respectively come
municating with said stator inlet and delivery
conduits, said stator inlet and delivery ports be
ing respectively positioned to successively regis
I have also provided a further improved port
ing arrangement and construction for obtaining
improved pumping efficiency and quietness of
ter with a plurality of said rotor passages during 15
rotation of said rotor, said statorhavingaa?uid
conducting passage communicating at oneend
thereof with said ?uid, delivery conduit and hav
ing its other end‘ disposed to subject said rotor
Each of the chambers ill)t and 53I has at least
one controlling edge thereof, such as the intake
20 cut-off and the pressure cut-off edges respec
to the pressure of ?uid in said passage, means
yieldably urging swinging movement of said
wabble plate about its pivotal support toward a
tively, constructed for improved operation with ‘ position inclined with respect to a plane perpen
the cylinder passages 45‘. In Figs. 16 and 17 I
have illustrated this arrangement in connection
with the typical passage 53!. This passage is
25 generally rectangular in section except in the
region adjacent the discharge controlling edge
where'the'inner wall of the passage has a curved
groove 96 which terminates outwardly in a
rather sharp pointed generally elliptical edge as
30 shown in Fig. 1'7. As the circular port of pas
sage 451 sweeps‘ across the edge 96 as the body
dicular to said axis, and means responsive to the
pressure of the ?uid delivered by said pistons 25
for moving said wabble plate in opposition to said
yielding means.
2. In a ?uid pump, a stationary structure hav
ing ?uid inlet and delivery passages, a rotary
structure formed with a plurality of cylinders
extending in the direction of the axis of rota
2|t rotates, as indicated by the dotted line in
Fig. 17, the discharge of ?uid from passage 451
to chamber 53‘ is very gradually cut off.
‘ .
noted that when my
piston is at its highest point, the rotor port Mit
has just passed the stator port edge 96', the dis
tion and spaced circumferentially thereof, a pis
ton reciprocating in each of said cylinders, means
for conducting ?uid from said inlet passage to
said cylinders in response to movement of said
pistons in one direction of reciprocatory move
ment thereof and for delivering ?uid under
pressure from said cylinders to said delivery pas
sage in response to movement of said pistons in
sible while pressure is being built up by the pis
ton and while passage 45f is open to chamber
their other direction of reciprocatory movement, 40
a wabble plate structure controlling movement
of said pistons, wabble plate adjusting means
531. This provides relatively great pump e?i
comprising a lever arm, common means for piv
ciency and prevents carrying over a pressure of
an increasing character, in any cylinder, to the
otally mounting said wabble plate structure and
charge passage 45‘ being carried as far as pos
said lever, yielding means acting on said lever 45
intake chamber 50‘.
45 '. The inner ends of passages 45t which form‘
arm for imparting swinging movement to said
50' ports 451 at the region of ?nal ?uid discharge
erably associated with said ?rst mentioned lever
arm for limiting upward movement of said pis
wabble platestructure, means carried by said
circular ports preferably have a diameter smaller , lever arm and acting on said yielding means for
96 at the port ' adjustably conditioning the latter for predeter- '
than the height of the groove
controlling outer edge so that leakage will- not mining the ?uid pressure maintained by said
occur to any undesirable extent between adjacent pump, means including a second lever arm op
to chamber 5i!t and at the same time to obtain
as large a number of ports and cylinders as pos
sible in the rotor.
What I claim is:
1. In a ?uid pump, a substantially vertically
disposed stator having axial ?uid inlet and de
livery conduits respectively formed in the oppo
tons under ‘the action of said yielding means, and
adjustable means acting on said second lever arm
for varying the upward movement of said
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