U.S. patent number 3,838,950 [Application Number 05/423,130] was granted by the patent office on 1974-10-01 for vacuum pump with lubricant metering groove.
This patent grant is currently assigned to Cenco Incorporated. Invention is credited to Vytautas Andriulis.
United States Patent |
3,838,950 |
Andriulis |
October 1, 1974 |
VACUUM PUMP WITH LUBRICANT METERING GROOVE
Abstract
A vacuum pump having an improved lubricating and sealing system
providing for metered oil flow from an end plate to the center
plate with a return provided along the shaft supporting the pump
rotor. A novel inlet plate is provided to guard against entry of
contaminants into the lubricating and sealing system.
Inventors: |
Andriulis; Vytautas (Chicago,
IL) |
Assignee: |
Cenco Incorporated (Chicago,
IL)
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Family
ID: |
26724789 |
Appl.
No.: |
05/423,130 |
Filed: |
December 10, 1973 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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47239 |
Jun 18, 1970 |
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Current U.S.
Class: |
418/76; 418/91;
418/97; 418/79; 418/96 |
Current CPC
Class: |
F04C
29/02 (20130101); F04C 2220/50 (20130101) |
Current International
Class: |
F04C
29/02 (20060101); F01c 021/04 (); F04c 027/02 ();
F04c 029/02 () |
Field of
Search: |
;418/76,79,82,87,91,92,94,96-99 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Vrablik; John J.
Attorney, Agent or Firm: Walters; Gomer W.
Parent Case Text
This is a continuation, of application Ser. No. 47,239, filed June
18, 1970 and now abandoned.
Claims
I claim:
1. In a vacuum pump having a stator disposed between first and
second end plates, a shaft extending between and supported by the
end plates for angular movement relative to the stator, and a rotor
having vanes positioned for rotation on the shaft in engagement
with the inner circumference of a pumping cavity in the stator, a
lubricant distributing system comprising:
the first end plate having a metering groove with an inlet end and
an outlet end formed therein extending from said inlet end to said
outlet end in the direction of rotation of the rotor and vanes, the
rotor and vanes being arranged to sweep across the open surface of
said metering groove in close proximity thereto, said metering
groove being sufficiently shallow to permit the sweeping of the
rotor and vanes across the open surface thereof to produce a
turbine action that continuously impels a lubricant through said
groove at a desired predetermined rate without being affected by
contaminants that may be in the lubricant;
input means to introduce the lubricant to said inlet end of said
metering groove; and
output means to direct the lubricant at said outlet end of said
metering groove to the appropriate portion of the pump.
2. In a vacuum pump having a stator disposed between first and
second end plates, a shaft extending between and supported by the
end plates for angular movement relative to the stator, and a rotor
having vanes positioned for rotation on the shaft in engagement
with the inner circumference of a pumping cavity in the stator, a
lubricant distributing system comprising:
the first end plate having a continuous flow lubricating path
formed therein and extending in a generally radial direction toward
the shaft;
a metering portion of said lubricating path interconnecting two
enlarged flow portions of said lubricating path and arranged to
have the rotor and vanes impel lubricant therethrough to cause a
predetermined amount of lubricant to be continuously passed through
said lubricating path during operation of the pump irrespective of
pressure conditions and contaminants in the lubricant;
insertion means to introduce the lubricant into said lubricating
path; and
withdrawal means to pass the lubricant from said lubricating path
to the shaft supports and to the pumping cavity in the stator.
3. A lubricant distributing system as claimed in claim 2 wherein
said metering portion is generally transverse to said enlarged flow
portions and impedes lubricant flow through said lubricating path
in the absence of the impelling action of the rotor and vanes.
4. A lubricant distributing system as claimed in claim 2 wherein
said insertion means comprises:
an opening extending through the upper ends of the second end plate
and the stator;
an input passage to introduce lubricant to said opening; and
a vertical recess in the stator adjacent the first end plate and
extending downwardly from said opening to said lubricating
path.
5. A lubricant distributing system as claimed in claim 2 wherein
said withdrawal means comprises:
a chamber in the first end plate about the shaft to receive
lubricant from said lubricating path;
a keyway extending along the shaft from said chamber;
an exhaust area in the second end plate communicating with the
keyway; and
a discharge groove to convey lubricant from said exhaust area into
the pumping cavity.
6. A lubricant distributing system as claimed in claim 2
wherein:
said metering portion of said lubricating path is an open groove
extending in the direction of rotation of the rotor and vanes;
and
the rotor and vanes sweep across the surface of said groove to
impel the lubricant therein through said groove at a desired
predetermined rate.
7. A lubricant distributing system as claimed in claim 6 wherein
said groove is shallow relative to said enlarged flow portions to
provide a restricted metering groove.
8. In a multistage vacuum pump of the oil sealed type having a pump
housing containing an oil bath, a stator disposed between a center
plate and an exhaust end plate joined by a bolt at the upper ends
thereof and all located in the oil bath, a shaft extending between
and supported by the plates for angular movement relative to the
stator, and a rotor having outwardly biased vanes positioned for
rotation on the shaft in a pumping cavity in the stator which has
intake and exhaust sections thereof, a lubricant distributing
system comprising:
an opening about the bolt extending through the end plate and the
stator;
an input passage located below the level of oil in the pump housing
to introduce oil to said opening to cause oil flow through the end
plate and the stator;
a vertical recess in the stator adjacent the center plate and
extending downwardly from said opening;
a continuous flow lubricating path in the center plate comprising a
first enlarged flow portion communicating with said recess and
extending downwardly therefrom, a restricted metering groove having
a first end communicating with said first enlarged flow portion and
extending therefrom in the direction of rotation of the rotor so
that the rotor and vanes sweep across the surface of said metering
groove to impel oil therethrough at a predetermined rate, and a
second enlarged flow portion extending from the other end of said
metering groove toward the shaft;
a chamber in the center plate about the shaft to receive the oil
from said lubricating path;
a keyway extending along the shaft from said chamber;
an exhaust area in the end plate communicating with said keyway;
and
a discharge groove to convey oil from said exhaust area into the
exhaust section of the pumping cavity at a region of low
pressure.
9. A lubricant distributing system as claimed in claim 8 wherein
said restricted metering groove is shallow relative to said
enlarged flow portions and impedes lubricant flow through said
lubricating path in the absence of the impelling action of the
rotor and vanes.
Description
This invention relates to improvements in vacuum pumps in general
and, more specifically, is directed to a new and improved system
for providing metered oil flow to the moving parts to improve the
sealing, recovery, lubrication and gas ballast characteristics of
the pump.
Multistage mechanical vacuum pumps of the vane type are well known.
The general elements composing a simple form of a two-stage pump
consist of an intake stage and an exhaust stage. Each stage is
provided with a stator having an interior chamber receiving a rotor
mounted for rotation within the chamber. The rotor diameter is
somewhat less than the diameter of the chamber and it rotates on an
axis which is offset or eccentric relative to the geometric axis of
the chamber of the stator. A typical rotor includes a pair of
oppositely biased vanes which extend axially from one end of the
chamber to the other and are movable in slots in the rotor so as to
be pressed against the interior of the walls of the chamber
throughout rotation and thereby function to sweep the fluid pumped,
such as air molecules, toward the exhaust.
Vane-type mechanical vacuum pumps oftentimes immerse the entire
stage or stages in a bath of oil so that continuous lubrication is
available and to permit the oil to assist in sealing between stages
where differential pressures exist. Ordinarily, when a pump has
been idle, the pumping chambers will fill with oil, which oil is
expelled through the first few revolutions of the rotor. The
exhaust duct or port of the pump is provided with a tortuous path
or other means to prevent exclusion of the oil and, normally it is
discharged so as to be led back to the area around the pumping
chamber.
Known types of vacuum pumps have various means and methods for
providing lubrication to the center plate of the pump which is
located between the two stages. Generally, this lubrication is not
in the form of any positive flow arrangement but through a very
small orifice or the like in the stator, end plate or center plate
which is intended to meter a small amount of oil into the stator
chamber and hopefully migrate to the area of the center plate to
provide for lubrication. This form of lubrication has proved to be
unsatisfactory for many reasons. The location of the orifice is
such that oftentimes contaminants on the surface of the oil or
which are entrained in the oil cause the orifice to become clogged
and thereby starve the stator chambers from a continuous supply of
lubrication. Enlarging the hole to avoid clogging has been proposed
as a solution, however, in such event, the oversupply of such
lubrication causes what is known as "hydraulic knock" which is
undesirable and reduces the over-all efficiency of the pump. Vacuum
pump manufacturers have continued with this technique of
lubrication for lack of a suitable alternative.
The present invention relates to a new and improved lubricating
system for a vacuum pump to provide constant metered flow to the
moving parts of the vacuum pump and thereby overcome the
difficulties heretofore experienced. Since a continuous and
complete supply of the oil is available with the present invention,
constant sealing between stages and areas of differential pressures
is assured. Improved gas ballast is experienced. Because of the
improved lubrication and sealing qualities, a quicker recovery is
possible after the vacuum has been broken. Improved performance is
experienced in work in which contaminants can be pumped and
expelled, such as would be encountered in freeze drying work and
the like.
The present invention provides an extremely simple and economical,
but highly effective, lubricating arrangement in the exhaust stage
of the pump which is formed mostly by removing existing material in
the stator and center plate. An improved oil inlet plate is
provided at the intake to preclude entry of floating contaminants
into the pump. Oil flows in and around an existing bolt which
functions to join the end plate, stator and center plate. On
reaching the area of the center plate, the oil flows through a
vertical groove in the stator to a vertical groove in the center
plate and then down in a generally radial direction toward the axis
of rotation of the rotor. Oil is distributed to the rotor vane and
the center bearing with any excess oil led along the rotor shaft,
where it lubricates the vanes, to the bearing area in the end plate
for discharge into the oil bath surrounding the stages. As will be
seen, since the oil flow is metered, excess oil is not a
problem.
Through the unique metering system, a continuous supply of sealing
oil is provided to the center plate wall to lubricate the moving
parts and provide good sealing between areas of differential
pressure. An oil inlet plate of novel design is provided to prevent
the introduction of contaminants into the lubricating system. A
machined groove in the center plate forms a fixed orifice of
predetermined size so as to limit the flow of oil to the center
bearing area and into the pumping stage. The location of the
orifice is such that the action of the sides of the vanes of the
rotor passing over the orifice will maintain the orifice free of
contaminants in the event they should enter the system, thereby
assuring a continuous metered flow of lubricant to the moving
parts.
From the foregoing general description, it can be seen that through
the present invention, a mechanical vacuum pump is provided having
improved vacuum, better lubrication, better sealing between the
points of differential pressure, achievement of better gas ballast
control and also providing means to prevent the entrance of
contaminants into the lubricating system.
It is an object of this invention to provide a new and improved
mechanical vacuum pump having the above-stated attributes and which
overcomes the problems outlined.
It is a further object of this invention to provide a new and
improved vane-type vacuum pump in which metered constant flow of
lubricant is provided through the provision of a novel lubrication
system.
It is a further object of this invention to provide a mechanical
vacuum pump of the vane type in which a novel oil inlet plate is
provided to reduce the possibility of the entrance of contaminants
into the novel lubrication system.
It is a still further object of this invention to provide a new and
improved lubricating system having a fixed orifice for controlling
lubricant flow, the orifice being strategically located so as to be
continuously swept clean of any contaminants through the sweeping
or wiping action of the vane.
Objects in addition to those specifically set forth will become
apparent to the man skilled in the art upon consideration of the
drawings and following description in which like reference
characters will be used wherever feasible to designate the same or
equivalent structures.
IN THE DRAWINGS
FIG. 1 is a longitudinal cross-sectional view of a vacuum pump;
FIG. 2 is a cross-sectional view taken generally along line 2--2 of
FIG. 1 and illustrating the lubrication path in the center plate in
dotted lines;
FIG. 3 is an enlarged elevational view of the center plate showing
the lubrication path in full elevation;
FIG. 4 is a perspective view of the center plate with the stator
and rotor shown in phantom lines to illustrate the sweeping action
of the rotor vanes;
FIG. 5 is a fragmentary elevational view of the end plate of the
pump showing the lubricant groove;
FIG. 6 is a plan view of the oil inlet plate of the present
invention;
FIG. 7 is a rear elevational view of the plate shown in FIG. 6;
FIG. 8 is a perspective view of the oil inlet plate of FIGS. 6 and
7; and
FIG. 9 is an enlarged cross-sectional view of the novel lubricating
system of the present invention with arrows to show the general
flow path of lubricant.
Referring now to FIG. 1, reference character 10 indicates a
multistage vacuum pump having the general characteristics outlined
above. The pump includes an outer housing 11 composed of right-hand
and left-hand casings 12 and 13, respectively, which are joined to
a common center plate 14 by means of cap screws 15 and 16 or the
equivalent. The housing halves 12 and 13 form with the center plate
a tank or chamber to receive the lubricating and sealing oil, the
level of which is indicated by the arrow 17. Openings (not shown)
in the center plate permit the oil to flow freely between the
housings 12 and 13.
Disposed within the housing 11 is a first or intake pumping stage
indicated generally at 20 and an exhaust stage indicated generally
at 21. The intake stage includes a customary stator 22 which houses
a rotor 23 having spring loaded vanes 24 and 25. The rotor is keyed
to a shaft 26 which is supported by a bearing 27 carried in the
center plate 14.
The exhaust stage 21 includes a stator 32 having a cavity 31
receiving a rotor 33 which is also keyed for rotation with the
shaft 26. A spring guide pin 34 extends through the shaft and
supports a spring member 35 which urges the vanes 37 and 38
outwardly against the inner circumference of the cavity 31 of the
stator 32. An end plate 40 is joined with the stator 32 to the
center plate by means of bolts 41. Similarly, an end plate 42 is
provided in the intake stage 20, also being joined to the center
plate by means of bolts 43.
The shaft 26 extends through the end plate 40 and is supported
thereby with a pair of thrust washers 45 and 46 acting between
grooves in the shaft and the thrust bearing surfaces on the end
plate 40 to take any axial or end loads on the shaft 26. A sealing
assembly indicated generally at 47 seals the shaft 26 as it exits
the housing. The seal 47 is of a known type commonly referred to as
a face seal in which radially extending surfaces sealed to the
housing and shaft, respectively, move relative to each other while
in contact with each other. The shaft 26 is illustrated as being
broken away at its right-hand end, however, in practice is extended
and supports a pulley which is adapted for driving by a belt.
A gas ballast valve assembly 48 of known type is shown in FIG. 2
and is adjustable to permit the introduction of gas such as air
into the exhaust stage of the pump. The gas ballast valve assembly
48 includes a valve body 50 supported by the stator 32 and having
gas intake ports 51. A control knob 52 permits adjustment of the
movable valve member 53 to control the flow from the opening 51
through a central bore 54. A spring-biased or one-way ball valve 55
is provided at the lower end of the cylindrical valve body 50 and
is preloaded to the desired degree. In operation, when the knob 52
is opened, outside air may be admitted to the exhaust chamber just
prior to pressure buildup and discharge of the fluid pumped in
order to assist in flushing the chamber. This will be described in
greater detail with reference to the description of the operation
of the pump.
Referring now to FIG. 9, it can be seen that the body of the bolt
41 at the top of the exhaust stage 21 is of lesser diameter than
the diameter of the opening 60 in the end plate 40 and the opening
61 in the stator 32. This provides clearance around the
circumference of the bolt 41 with the opening to form a path or
conduit through which lubricating oil may flow to the center plate.
The bolt 41 is a conventional hexagonal head 62 which clamps an oil
intake plate of novel design, indicated generally at 63, over the
outer end of the opening. With reference to FIGS. 6, 7 and 8, the
intake plate may be inexpensively formed through use of sheet metal
stamped to the desired shape and folded in the manner illustrated.
A cutaway section 64 is formed on one side of the plate for
communication with an enlarged opening 65 approximating the
diameter of the opening 60 in the end plate 40. A second opening 66
is formed in the outer portion of the plate and provides sufficient
clearance to admit the body of the bolt 41. The opening 65 is
bounded through approximately 270.degree. in order to transmit and
distribute the clamping pressure of the bolt head 62 over a wide
area on the end plate 40. In practice, the cutaway section 64 is
disposed below the level of the oil, thereby assuring that the oil
will be taken in through the path shown in FIG. 9 below the surface
of the oil. In this manner, contaminants floating on the surface of
the oil are less likely to enter the system.
The inner end of the stator 32 is machined to provide a recess 70
which communicates with the opening 61. The lower end of the
opening 70 communicates with a vertical lubricating path indicated
generally at 71 in FIG. 3 which is formed in the center plate 14.
The lubricating path 71 may be formed in any manner such as by
milling a vertical groove 72, communicating at its lower end with a
horizontal metering groove 73 which is of lesser dimension than the
groove 72. A groove of increased width 74 extends diagonally from
the opposite end of the groove 73 and provides a flow path into the
area of the bearing 27 and the shaft 26. Grooves 72 and 74 may be
formed with a lesser degree of precision than the metering groove
73. The dimension of the metering groove is determined for each
size of pump and in manufacturing is carefully controlled, as this
metering groove 73 functions as a flow restrictor to meter the flow
of lubricant into the area of the bearing 27. An adequate, but not
excessive, amount of oil is continuously available.
As is evident in the cross-sectional view of FIG. 2, a keyway 75 in
the rotor 33 provides a path to direct the oil from the area of the
center bearing back to the end plate 40 to provide lubrication for
the thrust bearings and supporting bearings on the shaft 26.
Referring now to FIG. 5, the end plate 40 is shown in broken-away
elevation. The shaft 26 is shown in cross section and surrounding
the shaft is a cavity 80 which forms an exhaust area for the
lubricating oil which has been metered from the center plate across
and along the rotor shaft. A groove which is of inverted V shape is
shown at 81 and communicates with the cavity 80. The shape of the
groove provides a path for the lubricating oil to be discharged
into a low pressure area of the exhaust section of the pump cavity,
thus assuring that the oil will be vented into an area where the
gases are not yet fully compressed. Any oil reaching the cavity is
expelled by conventional means. In this manner, the flow of oil in
the circuit path shown by the arrows in FIG. 9 is continuously
assured, thereby providing for maximum improved lubrication and
anti-seize protection, as well as substantially improving the pump
characteristics.
In operation, the first pumping gauge 20 is connected through a
conduit (not shown) to the device to be evacuated. Rotational
motion is applied to the shaft 26 by a pulley and belt or other
conventional drive (not shown). On the first few revolutions of the
shaft 26, oil is expelled from the pumping chambers (see FIG. 2)
while a film of lubricant remains between the working parts,
especially at the sealing seat indicated generally by the arrow and
reference numeral 100 in FIG. 2. The sealing seat 100 is in
continuous contact with the rotor 33 so as to divide the stator
chamber and thereby assure the expelling of the fluid pumped.
In the known form of prior art pump, an orifice is provided in the
end plate 40 adjacent the top of the rotor to allow oil to drip
into the exhaust stage pumping chamber, with reliance on the
movement of the pump to distribute the lubricant. Distribution of
lubricant by this technique is less than satisfactory. If the pump
is rotated for prolonged periods, the surfaces can and do become
dry, causing the shaft, rotor and vanes to seize, requiring the
pump to be disassembled and reworked before it is again
operational. The problem of seizing is virtually assured in those
instances in which the tiny orifice through the end plate becomes
plugged with contaminants, thereby starving the internal working
parts of the pump of any lubrication. It is also more expedited and
pronounced in applications in which contaminants are pumped, such
as in freeze drying, vacuum deposition of metals and the like.
In the present design, after the pump has reached an operational
condition, a continuous supply of lubricant enters along the oil
inlet plate 63 in the manner shown in FIGS. 1 and 9 by the arrows.
Inasmuch as the oil rotary opening is well below the operating
level 17 of the oil, the likelihood of floating surface
contaminants entering the pumping chamber is materially reduced.
Moreover, floating contaminants will not be introduced when the
chamber is vented to atmosphere, as would occur during periods of
nonuse, change-over or the like. Should contaminants enter the
system, the wiping action of the inner sides of the vanes passing
the fixed orifice or metering groove 73 keeps the groove from
becoming obstructed (see FIG. 4). In addition, the wiping action of
the sides of the rotor 33 and vanes 37 and 38 acts as a turbine
pump to impel the oil along the groove 73 which has been
illustrated as being straight. It is clear that the rotating rotor
33 and vanes 37 and 38 form a constantly moving side of metering
groove 73, which contacts and is adhered to by the oil flowing
through the groove 73 and impart momentum to the oil to impel it
along the metering groove 73. Obviously, the groove 73 may be
arcuate if desired.
Oil can and does flow freely along the circumference of the bolt 41
into the recess 70 where it flows into the vertical groove 72.
Because of the reduced cross-sectional area of the groove 73
connecting the grooves 72 and 74, the flow of oil is restricted.
The dimensions of the flow restrictor groove 73 are carefully
designed and controlled during manufacture to obtain the precise
metering rate for adequate, but not excessive, lubrication for each
size of pump design. Design dimensions are readily obtained through
application of trial-and-error techniques for each pump size.
The rate of flow of oil into the groove 74 is controlled by the
fixed orifice 73 (see FIG. 3). The oil exits the groove 74 into a
circumferential chamber 101 formed by the recess receiving the
bearing 27. When filled with lubricant, the chamber 101 forms a
liquid seal between the intake stage and exhaust stage as well as
providing a ready supply of lubricant to continuously lubricate the
bearing 27. The oil exits the chamber 101 and flows along the
keyway 75 and shaft into the area of the thrust washer being
ultimately discharged through the specially shaped groove 81 into a
region of low pressure in the area of the exhaust section of the
pump so as to prevent contamination or entrainment of air in the
medium pumped in the oil. It is then exhausted to the tank for
recirculation.
The present pump, insofar as gas ballast is concerned, operates in
a manner somewhat similar to the conventional vane-type pump in
that there is a connection directly to atmosphere from the exhaust
chamber. With particular reference to FIG. 2, when the moving vane
sweeps around the bottom of the chamber as in the case of the vane
38, the pressure in the chamber is normally subatmospheric. When
the metering or needle valve 53 is opened, air may enter the port
51 and, under the influence of atmospheric pressure, presses the
ball 55 away from the seat to permit the entry of air into the
exhaust chamber. In prior art pumps, the quantity of air introduced
had to be kept fairly small because of the strong likelihood that
excessive air would find its way into the intake stage of the
pump.
In the present invention, large amounts of air may be introduced
without such a problem occurring since adequate oil is available at
the sealing seat 100 and in the center bearing 27 and along the
moving surfaces acting as a liquid barrier to prevent the gas
ballast and fluid pumped from entering other parts of the pump. The
vane 38 in FIG. 2, which is moving in a counterclockwise direction,
compresses the gas introduced from atmosphere as well as the fluid
pumped exhausting all fluids through the exhaust opening as the
vane 38 approaches the seat 100. As the pressure builds up ahead of
the vane, the spring biases the ball 55 into engagement with the
seat, precluding further introduction of atmosphere into the
exhaust chamber.
A continuous and adequate supply of lubrication is provided to
reduce internal leakage between stages. The oil functions as a
liquid seal between the stages as well as between the exhaust and
intake portions of the pump. The correct amount of oil is metered
to the exhaust chamber, minimizing hydraulic knock. Moreover, the
turbine action of the vane assures uniformity in the flow rate of
the oil.
In summary, the pump of the present invention provides faster
evacuation at lower pressures which is sometimes referred to as
"merit factor." This is the percentage of pumping speed retained by
the pump at low pressures. The supply of oil being the optimum or
right amount at all times provides for metered internal lubrication
and, therefore, less gas (air) enters the pump when it is exposed
to atmosphere.
As pointed out above, the provision for increased or full gas
ballast is provided. In present applications of vacuum pumps, such
as freeze drying, thin film coating and color television tube
evacuation, the removal of gas dissolved in the pump oil is
absolutely required. The full gas ballast assists in preventing
condensible gases from becoming entrained in the oil and permits
removal of dissolved gases by bleeding large amounts of air into
the exhaust stage of the pump to provide for rapid oil purging.
Known forms of pumps permit only a limited supply of air to be
introduced because of the problem of the air entering the preceding
stage of the pump and areas where it cannot be readily
exhausted.
In addition, the ultimate pressure with or without gas ballast is
decreased because of the improved lubrication and sealing. A pump
incorporating the present invention will reach a pressure of at
least 10 to 100 millitorr below that of known types of pumps
commercially available. In many instances, pressures of up to 1 or
2 millitorr may be achieved with the present pump with the gas
ballast valve wide open. In addition to the foregoing, the present
pump will recover faster after opening to atmospheric pressure
since the lubrication is uniform in all the working parts of the
pump to preclude the entry of air. This reduces the recovery time
considerably, which is quite desirable in cyclical processes. The
present pump is expected to provide longer life because of the
adequacy of lubrication at all times.
Upon a consideration of the foregoing, it will become obvious to
those skilled in the art that various modifications may be made
without departing from the invention embodied herein. Therefore,
only such limitations should be imposed as indicated by the spirit
and scope of the appended claims.
* * * * *