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Патент USA US3077849

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Feb. 19, 1963
Filed Oct. 28, 1960
3.9 133 7
Job/7 Z- éom/e/r
United States Patent 0'
John T.-Gondek, 2206 Roosevelt St. NE,
Minneapolis, Minn.
Filed Oct. 28, 1960, Ser. No. 65,665
1 Claim. (Cl. 103-126)
Patented Feb. 19, 1963
shafts. Each time the tooth of one gear nears dead
center position between the teeth of the companion gear,
the trapped oil is forced under pressure through the
' minute groove in the end walls to the chamfers, from
which it may pass along the journals to lubricate the
journals.‘ This has resulted in an increase in the rating
of the pumps very materially. Pumps of the same size
which were previously rated at 2,000 pounds per square
This invention relates to an improvement in pump con
inch are now rated at 5,000 pounds per square inch, and
structions and deals particularly with a gear type pump
having certain advantages over the conventional type of 10 have been tested successfully at much higher pressures,
due to the slight change in construction.
gear pump.
These .and other objects and novel features of the
Gear pumps are conventionally made ‘with an inter
present invention will be more clearly and fully set forth
mediate section including intersecting arcuate chambers
in the following speci?cation and claim.
to accommodate the gears, and end plates secured to the
In the drawings forming a part of the speci?cation:
ends of the intermediate section to form the chamber 15
FIGURE 1 is a sectional view through a typical form
ends. In some instances, pumps of this type have been
of gear pump embodying the present invention.
formed with one end plate integral with the intermediate
FIGURE 2 is a sectional viewlat right angles to that
section. It is an object of the present invention to pro
of FIGURE 1, the position [of the section being indicated
vide a pump having two generally similar sections each
of which are provided with a cavity forming a part of 20 by the line 2—2 of FIGURE 1.
FIGURE 3 is a transverse sectional view through the
the pump chamber. In other words, the central section
pump illustrated in FIGURES l and 2, the position of
is divided intermediate its ends, and the end sections are
the section being indicated by the line 3—3 of FIG
integral with the two center sections.
URE 2.
A feature of this construction lies in the fact that by
FIGURE 4 is an enlarged view showing a portion of
having two similar pump sections which meet along a
the gear teeth and showing the manner in which ?uid
common line, the tendency for the pump body to deflect
is trapped between the teeth of the gear.
outwardly in a radial direction is very materially reduced.
FIGURE 5 is an enlarged sectional view showing a
When high pressures are being developed by the gear
portion of the gear housing .and the rotors supported
pump, there is a tendency for the pump body to de?ect
in a manner to increase the bore size. As the body is
The pump is indicated in general by the letter A. The
not integrally connected to the end plates, this force is
pump includes a housing which is indicated in general
resisted by the strength of the body and the mechanical
by the numeral 10 and which includes a housing section
connecting means securing the end plates to the body.
11 and a housing section 12. The housing sections 11
By dividing the pump housing intermediate the ends of
the gears, the force is resisted by the integral end walls 35 and 12 are in abutting relation along a plane 13 which,
in preferred form, is intermediate the ends of the gear
as well as the body, thus holding the body from radial
As is indicated in FIGURE 3 of the drawings, the _
A further feature of the present invention lies in the
pump housing sections .11 and 12 arevprovided with
provision of a means of relieving the pressure between
the gears at a point of dead center between the two gears. 40 arcuate cavities 14 and 15 which are in ‘intersecting rela
tion and which are designed to accommodate the gears
In a gear pump, the teeth of the two gears do not ordi
16 and 17 which comprise the pump, As indicated in
narily mesh perfectly so that there is normally a certain
FIGURE 2 of the drawings, the gear 16 is provided with
amount of oil which is trapped between the teeth inter
stub shafts 19 and 20 which are supported in suitable
mediate the axes of the two gears. This point is between
the inlet and the outlet of the pump. The oil which is 45 bearings 21 and 22 in the gear pump sections 11 and 12.
The gear 17 is likewise supported with axial stub shafts
trapped between the two gears at the point of dead center
23 and 24 which are supported in bearings 25 and 26
must escape either between the teeth or past the ends of
in the housing sections 11 and 12. The stub shaft 23
the gears or between the gears and the end walls of the
projects from the housing portion 11 and is preferably
pump housing. This creates a frictional force between
the gears which tends to increase the power required to 50 encircledby an anti-friction bearing 27, as the shaft 23
acts as the drive shaft for the pump.
operate the pump. I have found that by relieving the
As is also indicated in FIGURE 3 of the drawings,
pressure between the gear teeth at the point of dead
the pump section 11 is provided with lateral passages
center between the gears, two important results may be
30 and 31 which form the pump inlet and the pump
achieved. In the ?rst place, the frictional force caused
by the trapped liquid may be eliminated. In the second 55 outlet. These passages 30 and 31 are connected with
place, if the trapped liquid is directed toward the axes
of the gears, this liquid may serve as a lubricant for the
gear shafts. This is particularly advantageous when the
pump is idling at high speeds and has no head pressure
inlet and outlet openings 32 and 33 respectively which
extend in a direction axially through the pump sections.
These passages 33 and 32 also extend through a pump
base section 34 to communicate with inlet and outlet
60 sockets 35 and 36 respectively.
to work against,
A series of angularly spaced bolts 37 extend through
To this end, I have provided slight chamfers in the
the pump housing sections 11 and 12 .and are threaded
gear housing encircling the gear shafts and extending
into the base section 34 to attach the sections together.
into the end walls of the housing. A small groove is
It will be noted that the chambers for containing the
provided on a plane through the axes of the gears con
necting the two chamfers. This groove is in communi
cation with the space between the gear teeth at their
point of dead center permitting the pressure to escape
into the chamfers, thus directing lubricant to these cham
fer areas encircling the gear shafts.
A feature of this construction lies in the fact that the
pump gears form a lubricating pump for the pump
65 gears 16 and 17 exend to either side of the center line
connecting the two pump sections so as to minimize the
tendency for the extremely high pressure to de?ect the
body in a radial direction, or in a manner to increase
the bore diameter. Radial de?ection is prevented by the _
integral connection of the body with the ends of the
As indicated in FIGURE 4 of the drawings, there is '
3 077.839
normally'a tendency for liquid' to be trapped in the space
inch, and the groove or passage connecting these cham
'40 between 'the'too'th'4l of '6ne"'gear such as 16 and
the base between the teeth’as indicated at 42 in the other
gear 17. As the gears rotate, this ?uid under pressure
must es'cape'either'between'the teeth'or about the ends
'fe'rs'rnay be of about’ equal 'width. 'At the hignpres‘su'res
involved, this size is sufficient to properly lubricate the
of the gears. ‘The compression ‘of this fluid causes a
tendency‘to stop rotation of the gears, and requires
greater ‘pressure in "or‘der‘to ‘keep them in operation.
As is ‘indicated in the drawings, ‘each ‘of the pump
the principles ‘of construction and operation of my im
In accordance with the‘ patent statutes, I have described
provement in pump constructions; and 'while I have en
deavored to set forth the best embodiment thereof, I
desire to have it understood that changes may be made
housing sections‘ll and 12 are provided with cham‘fei‘s 10 within the scope of the following claim without departing
between ‘the ends of pump housing and the ends ‘of the
from the spirit of my invention.
gears 167
A chamfer'43 encircles the stub shaft‘19 in
I claim:
‘the housing section'l‘l at'the end of the gear 17, and a
A gear pump including,
a pair of interme‘shing'gears,
similar chamfer 44 is provided in the housing ‘section
12 at the opposite end of ‘the gear 16. In a similar
parallel shafts supporting said gears,
manner, cha‘r‘nfers 45'and'46‘a1‘e provided in the'housing
séetions'll and'12 at ‘opposite ends of the gear 17. These
chamfers extend about the journals 21'and ‘22 at their
juncture with the 'gear‘receiving recesses'14 and about
the‘ journals 25 and 26 at‘th'eir juncture with the puinp
stantially the‘sanie cross‘se‘ction throughout their
axial lengths,
each "section including ' a 'pair of similar relatively
chambers 15. ‘The ch'a'rnfers are very's‘mall and termi
shallow intersecting cylindrical cavities in'a surface
thereof, the‘cavities'mat‘ing to provide a gear cham
nate well short of the bases‘of the gear'teeth‘s'o‘that
‘there ‘is ‘no communication between the small chambers
said sections including axial bores extending there
de?ned by the chamfers and'the exterior of’the gear
teeth‘ except at‘the ‘point of ‘dead 'center'between the
‘gears. 'As‘ indicated ‘in FIGURES of the drawings, and
as indicated in dotted'o'utline in‘ FIGURE‘3 of the'draw
through in concentric ‘relation to‘said cavities to
' accommodate saidshafts,
the juncture betweensaid boies and said cavities being
chamfered, andv in ‘which each section includes a
groove connecting‘said'chamfers ‘at the point of
tangency of said gears, .and
ings, a narrow slot or passage 47 is provided connecting
‘the c‘hzi‘mfers’43 'and 45 ‘at 'one end of the gears'16 and
‘17 and conn'ecting’the c‘ha‘mfeis '44 and 46 at the oppo
site end of these-‘gears. This passage ‘47 is ‘substantially
a pump‘ housing‘compr'is'ing a'pair of sections of‘sub
narrower'th'an the‘wid'th ‘of'the ‘gear teeth'and ‘is be
tween-bur not connected with the inlet and outlet 'pas
sages 30 and 31. The purpose of this groove 47 ‘at each
vend of the gears‘ is toQpe'rinit' the‘ escape of ?u'idtrap'ped 35
‘between the teeth as‘the‘teeth‘pass through dead center
position‘be't‘ween thet'ax'es of‘the 'gears. Thus "in‘place
‘of 'building'u‘p’a'highpressure in‘the chamber‘ 40 be
“tween the teeth of one gear and the base of the teeth
‘of the opposite‘ gear, rh‘irpres‘sure ‘is permitted to ‘escape 40
through the .groove 47 for use in lubricating the’bear‘ings
of thegears.
As‘an actual example,‘ in a‘high'pressurefpunip‘having
’a"p'urnp bore of‘perhaps ?vefsixte'ehths of “an inch, the
‘c'hamf‘er may "be “abouf?ve 'to ten ‘thousandths "of "an 45
bolts‘arrang‘ed in angularly spaced relation about said
cavities securing said sections together.
References'Cited in the tile of this patent
Lindsay ______ .._' _____ __ Oct. 31, ‘1922
Cook ________________ __ Feb. 1,1949
Ilyin _________________ __ June 6, “1953
Thomas ____ ..._‘ _______ .._.‘June‘23, 1953
Korkowski et al _______ __ Dec. 17, 1957
‘Germany ____________ __ May 27, ‘1922
Italy ________________ __ Jan. 14, 1947
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