U.S. patent application number 11/625163 was filed with the patent office on 2008-07-24 for vacuum pump with wear adjustment.
Invention is credited to David Muhs, Douglas S. Prairie.
Application Number | 20080175722 11/625163 |
Document ID | / |
Family ID | 39641398 |
Filed Date | 2008-07-24 |
United States Patent
Application |
20080175722 |
Kind Code |
A1 |
Muhs; David ; et
al. |
July 24, 2008 |
VACUUM PUMP WITH WEAR ADJUSTMENT
Abstract
A vacuum pump having components that are subject to wear may be
adjusted to compensate for the wear. In some instances, a vacuum
pump may include a housing and an impeller disposed at least
partially within the housing. A gap between the housing and the
impeller may be adjustable to compensate for wear. In some cases,
the housing may include a ring that may be moved to adjust a
tolerance (or gap) between the ring and the impeller. In some
instances, the ring may be rotated to adjust this gap. In other
instances, the ring may be translated to adjust the tolerance.
Inventors: |
Muhs; David; (Minnetonka,
MN) ; Prairie; Douglas S.; (Boise, ID) |
Correspondence
Address: |
CROMPTON, SEAGER & TUFTE, LLC
1221 NICOLLET AVENUE, SUITE 800
MINNEAPOLIS
MN
55403-2420
US
|
Family ID: |
39641398 |
Appl. No.: |
11/625163 |
Filed: |
January 19, 2007 |
Current U.S.
Class: |
417/68 ;
417/53 |
Current CPC
Class: |
F04C 19/00 20130101;
F01C 21/106 20130101; F04C 2230/602 20130101; F04C 2240/30
20130101 |
Class at
Publication: |
417/68 ;
417/53 |
International
Class: |
F04C 19/00 20060101
F04C019/00 |
Claims
1. A liquid ring vacuum pump comprising: a base plate; an eccentric
ring disposed adjacent the base plate such that the eccentric ring
may be rotated relative to the base plate; an impeller disposed
within the eccentric ring; and a cover plate disposed over the
eccentric ring, the cover plate secured to the base plate.
2. The liquid ring vacuum pump of claim 1, wherein the cover plate
spans the eccentric ring and extends beyond an outer diameter of
the eccentric ring.
3. The liquid ring vacuum pump of claim 2, wherein the cover plate
comprises a plurality of bolt apertures, the base plate comprises a
plurality of threaded apertures, and the cover plate is secured to
the base plate via a plurality of bolts extending through the
plurality of bolt apertures into the plurality of threaded
apertures.
4. The liquid ring vacuum pump of claim 3, wherein the plurality of
bolts are disposed exterior to the eccentric ring.
5. The liquid ring vacuum pump of claim 1, wherein at least one of
the eccentric ring and the cover plate are sufficiently flexible to
withstand water freezing within the liquid ring vacuum pump.
6. The liquid ring vacuum pump of claim 1, wherein the eccentric
ring comprises a polymeric material.
7. The liquid ring vacuum pump of claim 1, wherein the cover plate
comprises a polymeric material.
8. The liquid ring vacuum pump of claim 1, wherein the eccentric
ring has a wall thickness that varies from a minimum wall thickness
to a maximum wall thickness.
9. The liquid ring vacuum pump of claim 1, wherein the base plate
is formed as part of a housing.
10. The liquid ring vacuum pump of claim 1, further comprising a
port plate disposed between the base plate and the impeller.
11. A liquid ring vacuum pump comprising: a base plate; an
eccentric ring disposed adjacent to the base plate; and an impeller
disposed within the eccentric ring; wherein the eccentric ring is
rotatable relative to the impeller to define an adjustable
tolerance therebetween.
12. The liquid ring vacuum pump of claim 11, wherein the adjustable
tolerance comprises a minimum distance between the eccentric ring
and the impeller.
13. The liquid ring vacuum pump of claim 11, wherein the eccentric
ring has an outer annular surface defined by a first circle and an
inner annular surface defined by a second circle, the second circle
being offset from the first circle.
14. The liquid ring vacuum pump of claim 13, wherein the base plate
includes an annular groove, and the eccentric ring is disposed at
least partially within the annular groove.
15. The liquid ring vacuum pump of claim 14, wherein the annular
groove is concentric with the first circle and sized to accommodate
the outer annular surface of the eccentric ring.
16. A method of compensating for wear within a liquid ring vacuum
pump comprising a base plate, an eccentric ring disposed proximate
the base plate, an impeller disposed within the eccentric ring and
a cover plate disposed over the eccentric ring, the method
comprising the steps of: loosening the cover plate; rotating the
eccentric ring; and tightening the cover plate.
17. The method of claim 16, wherein the step of rotating the
eccentric ring provides a reduced tolerance between the eccentric
ring and the impeller.
18. The method of claim 16, further comprising a step of removing
the cover plate prior to rotating the eccentric ring.
19. The method of claim 18, further comprising a step of measuring
a tolerance between the impeller and the eccentric ring after
rotating the eccentric ring.
20. The method of claim 16, wherein the eccentric ring comprises
one or more setpoint markings, and rotating the eccentric ring
comprises rotating the eccentric ring sufficiently to align one of
the one or more setpoint markings with an alignment mark on the
base plate.
Description
TECHNICAL FIELD
[0001] The present invention generally relates to pumps, and more
specifically, to vacuum pumps that are subject to wear.
BACKGROUND
[0002] A variety of pumping systems are known. Some pumping systems
are used in industrial or other commercial applications. Such
pumping systems may be used, for example, to evacuate ground water
from a construction site. In some cases, a vacuum pump, such as a
liquid ring vacuum pump, may be used to help prime a larger pump
such as a centrifugal pump.
[0003] It is known that such liquid ring vacuum pumps are often
subject to wear, especially when used in relatively dirty
environments. In such environments, the water system for the liquid
ring vacuum pump can accumulate dirt and other solids over time. As
internal pump components wear, the pumps tend to loose efficiency
and/or effectiveness. In many cases, after such wear occurs, the
entire vacuum pump or at least the worn parts must be replaced,
often at considerable expense. What would be desirable, therefore,
is a vacuum pumping system that is made adjustable to compensate
for such wear.
SUMMARY
[0004] The present invention relates generally to vacuum pumps that
are adjustable to compensate for wear that occurs within the pump.
In some instances, the vacuum pump may be a liquid ring vacuum pump
that includes a housing and an impeller disposed at least partially
within the housing. The impeller may be placed eccentrically with
respect to the housing, with a liquid such as water filling at
least part of a lower portion of the housing. An eccentric space is
typically provided between the housing and the impeller, with the
liquid in the housing filling the space to provide a seal between
the impeller and the housing during operation of the vacuum
pump.
[0005] In such vacuum pumps, which have an impeller that is
eccentrically placed with respect to the housing, a smaller gap or
clearance is typically provided between the top of the housing and
the impeller than at the bottom. During operation, the spinning
impeller causes at least some of the liquid in the housing to move
up and provide a seal along the gap. It has been found that the
size of the gap, particularly at or near the top of the housing and
the impeller, can influence the ultimate efficiency and/or
effectiveness of the vacuum pump. As such, is often desirable to
keep the size of this gap within a tolerance range. To increase the
useful life and/or maintain the efficiency and/of effectiveness of
the vacuum pump, it is contemplated that this gap or clearance
between the impeller and the housing may be made adjustable to help
compensate for wear in the housing and or impeller components.
[0006] In some cases, the vacuum pump housing may include a ring
that extends around the impeller that is movable so that a gap
between the ring and the impeller may be adjusted. In one
illustrative embodiment, the ring may have an eccentric bore, or
the ring may have a concentric bore with an eccentric bore or
recess machined into one end of the ring. In either case, and to
adjust the gap spacing between the ring and the impeller, the ring
may be rotated relative to the impeller. Alternatively, or in
addition, the ring may be simply translated to adjust the gap
between the ring and the impeller.
[0007] The above summary is not intended to describe each disclosed
embodiment or every implementation of the present invention. The
Figures, Detailed Description and Examples which follow more
particularly exemplify these embodiments.
BRIEF DESCRIPTION OF THE FIGURES
[0008] The invention may be more completely understood in
consideration of the following detailed description of various
embodiments of the invention in connection with the accompanying
drawings, in which:
[0009] FIG. 1 is a perspective view of an illustrative liquid ring
vacuum pump in accordance with an embodiment of the present
invention;
[0010] FIG. 2 is an exploded rear perspective view of the liquid
ring vacuum pump shown in FIG. 1;
[0011] FIG. 3 is a schematic view of an eccentric ring that may be
used in accordance with an illustrative embodiment of the present
invention;
[0012] FIG. 4 is a schematic view of the eccentric ring of FIG. 3
used in conjunction with the liquid ring vacuum pump of FIG. 1;
[0013] FIG. 5 is a schematic view of an eccentric ring that may be
used in accordance with an
[0014] FIG. 6 is a cross-sectional view taken along line 6-6 of
FIG. 5;
[0015] FIG. 7 is a schematic view of an illustrative liquid ring
vacuum pump in accordance with an illustrative embodiment of the
present invention;
[0016] FIG. 8 is a schematic view of a concentric ring that may be
used in conjunction with the present invention in an upward
position;
[0017] FIG. 9 is a schematic view of the concentric ring of FIG. 8
moved to a downward position;
[0018] FIGS. 10 and 11 show illustrative adjustment structures in
accordance with an illustrative embodiment of the present
invention;
[0019] FIG. 12 shows a schematic cross-section of a cover that may
be sized and configured to cover the impeller;
[0020] FIG. 13 shows a schematic cross-section of a cover having a
varying wall thickness;
[0021] FIG. 14 is a top view of a cover in accordance with an
illustrative embodiment of the present invention; and
[0022] FIG. 15 is a cross-sectional view taken along line 15-15 of
FIG. 14.
[0023] While the invention is amenable to various modifications and
alternative forms, specifics thereof have been shown by way of
example in the drawings and will be described in detail. It should
be understood, however, that the intention is not to limit the
invention to the particular embodiments described. On the contrary,
the intention is to cover all modifications, equivalents, and
alternatives falling within the spirit and scope of the
invention.
DETAILED DESCRIPTION
[0024] The following description should be read with reference to
the drawings, in which like elements in different drawings are
numbered in like fashion. The drawings, which are not necessarily
to scale, depict selected embodiments and are not intended to limit
the scope of the invention. Although examples of construction,
dimensions, and materials are illustrated for the various elements,
those skilled in the art will recognize that many of the examples
provided have suitable alternatives that may be utilized.
[0025] The invention generally relates to pumps. While the
invention is described with respect to a liquid ring vacuum pump,
this is merely for illustrative purposes and is not intended to
limit the invention in any way.
[0026] FIG. 1 is a perspective view of a liquid ring vacuum pump
10. Liquid ring vacuum pump 10 has a housing 12 that includes a
bearing housing 14, a back plate 16, a cover plate 18 and a ring 20
that is disposed between back plate 16 and cover plate 18. In some
cases, cover plate 18 and/or ring 20 may be formed of a material
that is sufficiently flexible and/or elastic to resist damage that
could otherwise occur as a result of water freezing within housing
12. In some instances, cover plate 18 may be formed of a polymeric
material. If desired, ring 20 may be formed of a polymeric
material. In other embodiments, the cover plate 18 and/or ring 20
may be formed from steel, aluminum or any other suitable material,
as desired.
[0027] In some instances, as illustrated, back plate 16 may include
one or more threaded apertures 22 that align with one or more bolt
apertures 24 that are formed within cover plate 18. As shown in
FIG. 2, one or more bolts 50 (or similar fasteners such as screws
or rivets) may be extended through the one or more bolt apertures
24 and into the one or more threaded apertures 22 to secure cover
plate 18 relative to back plate 16 and, in the process, secure ring
20 therebetween.
[0028] Liquid ring vacuum pump 10 may be configured to accommodate
a shaft 26 that extends through housing 12 and drives an impeller
(see FIG. 2, reference numeral 42). Shaft 26 may be driven in any
suitable manner. In some cases, especially if liquid ring vacuum
pump 10 is used to maintain a prime for a larger pump, such as a
larger centrifugal pump, shaft 26 may be driven by the same engine
that is being used to drive the larger pump. In some instances,
shaft 26 may be driven by a separate, smaller, electrical motor or
a fuel-driven engine, if desired.
[0029] Housing 12 may, if desired, include an inlet bore 28 and an
outlet bore 30. As will be discussed with respect to FIG. 2, inlet
bore 28 and outlet bore 30 may be in fluid communication with
internal flow chambers that are, in turn, in fluid communication
with the appropriate portions of a port plate 32. In some
instances, the internal flow chambers present within housing 12 may
be similar to those shown and described in U.S. Pat. No. 6,315,524,
which is herein incorporated by reference in its entirety. Housing
12 may also include mounting apertures, mounting brackets and the
like in order to secure liquid ring vacuum pump 10 as
appropriate.
[0030] FIG. 2 is an exploded rear perspective view of liquid ring
vacuum pump 10, showing some of the structures provided underneath
cover plate 18. A port plate 32 is disposed against back plate 16.
It can be seen that port plate 32 is located eccentrically with
respect to back plate 16.
[0031] The illustrative port plate 32 includes an intake port 34
that may be in fluid communication with an intake chamber (not
illustrated) that may, in turn, be in fluid communication with
intake bore 28. The illustrative port plate 32 also includes a
discharge port 36 that may be in fluid communication with a
discharge chamber (not shown) that may, in turn, be in fluid
communication with discharge bore 30. A water intake port 38 is
also disposed within port plate 32. In some cases, water intake
port 38 may be in fluid communication with a water chamber formed
within housing 12, and may also be in fluid communication with a
water intake bore (not shown). Details regarding the intake
chamber, the discharge chamber and the water chamber are further
discussed in the aforementioned U.S. Pat. No. 6,315,524.
[0032] An impeller 40 is disposed in front (as illustrated in FIG.
2) of port plate 32 and may be secured to shaft 26. The
illustrative impeller 40 includes a plurality of curved vanes 42,
but this is not required. For example, the impeller 40 may include
a plurality of straight or other shaped vanes, if desired. In some
cases, using curved vanes 42 may help increase the performance of
vacuum pump 10 over a vacuum pump that uses straight vanes.
[0033] In some instances, the size and shape of each of these ports
may be defined to provide optimal performance, if desired. As noted
above, the cavity defined by the housing 12 may be filled at least
partially with a liquid such as water. In some cases, the housing
12 is filled about half-way, but it is contemplated that other
amounts of liquid may be used. As impeller 40 rotates past intake
port 34 eccentrically to the ring 20 and casing, the liquid between
the vanes 42 of the impeller 40 may be at least partially expelled
leaving a void between the vanes 42 thereby creating a vacuum. This
vacuum pulls air through the intake port 34, which is conveyed into
the impeller casting and becomes trapped between the impeller vanes
42. As the cycle progresses toward the discharge port 36
eccentrically to the ring 20 and casing, at least some of the
liquid is forced into the space between the vanes 42, pushing the
trapped air out of the discharge port 36. A small amount of liquid
typically discharges with the gas. Therefore, a small amount of
make-up liquid may be provided via water intake port 38. This
make-up liquid helps maintain the liquid ring, and also absorbs the
heat energy of the compression.
[0034] In the illustrative design shown, the discharge port 36 is
smaller than the intake port 34. Both the intake port 34 and the
discharge port 36 are crescent shaped with one blunt end. The blunt
end of the intake port 34 is arranged so that a rotating vane 42 of
an impeller 40 passes over the blunt end after passing over the
rest of the intake port 34. This tends to increase the vacuum that
draws gas into the space between the vanes 42 of the impeller 40.
In contrast, the blunt end of the discharge port 36 is arranged so
that a rotating vane 42 of the impeller 40 passes over the blunt
end before passing over the rest of the discharge port 36. The
narrowing of the discharge port 36 tends to increase the pressure
between the vanes, thereby forcing the gas from the space between
the vanes 42 of the impeller 40.
[0035] In some cases, if desired, the exhaust of liquid ring vacuum
pump 10 may be provided through discharge bore 30. The vacuum pump
discharge may include both air and water. To recapture the water,
the vacuum pump discharge may be provided across a relatively cool
surface, which tends to cool and condense the water onto the cool
surface. The cooled water can then be collected and provided back
to vacuum pump 10. This closed loop system may allow liquid ring
vacuum pump 10 to operate continuously for longer periods of time
without having to add significant quantities of water.
[0036] In some cases, if desired, the vacuum pump discharge may be
provided to a muffler that can include one or more baffles in order
to reduce the noise before the vacuum pump discharge is released to
the atmosphere. In some instances, it is contemplated that the
exhaust of vacuum pump 10 may pass through a heat exchanger
assembly that can be used to cool the exhaust and thereby condense
water therein.
[0037] The illustrative embodiment shown in FIG. 2 shows both the
intake bore 28 and discharge bore 30 located on the same side of
the impeller 40. It is contemplated, however, that the intake bore
28 and the discharge bore 30 may be positioned on opposite sides of
the impeller 40. When so provided, an intake port plate having an
intake port 34 may be positioned on the side of and adjacent to the
intake bore, and a discharge port plate having a discharge port 36
may be positioned on the side of and adjacent to the discharge
bore. Another casting, having the discharge port, may then replace
the cover plate 18.
[0038] In some cases, seals such as O-rings may be used to provide
a seal between base plate 16, cover plate 18 and ring 20. As
illustrated, a first O-ring 42 may be disposed between cover plate
18 and ring 20 while a second O-ring 44 may be disposed between
ring 20 and back plate 16. First O-ring 42 and second O-ring 4 may,
if desired, be formed of any resilient material such as rubber.
[0039] While not required, in some cases, first O-ring 42 may fit
at least partially into a groove 46 that is formed in ring 20. In
some instances, back plate 16 may include a groove 48 that
accommodates second O-ring 44 as well as part of the ring 20
itself. In some cases, groove 48 may include, in cross-section, a
rectangular portion sized to accommodate the edge of ring 20 as
well as a dished or curved center (in cross-section) portion sized
and shaped to accommodate second O-ring 44.
[0040] In some cases, first O-ring 42 and/or second O-ring 44 may
be sized and configured to permit some movement of ring 20 relative
to back plate 16 (and hence relative to impeller 40). In some
cases, ring 20 may be eccentric, and may be rotated to compensate
for wear of ring 20 and/or impeller 40. In some instances, ring 20
may be concentric, and may be translated to compensate for wear of
ring 20 and/or impeller 40.
[0041] In some instances, as illustrated, ring 20 may include one
or more setpoint markings 52 that may be used in ascertaining a
rotational position of ring 20 with respect to back plate 16. Back
plate 16 may include an alignment mark 54. In some cases, ring 20
may include a plurality of setpoint markings 52 that are equally or
otherwise spaced. If desired, back plate 16 may include two or more
alignment marks.
[0042] It will be recognized from FIG. 2 that the gap or clearance
between impeller 40 and ring 20 is at a maximum at the bottom of
ring 20 and is at a minimum at the top of ring 20 (in the
illustrated orientation). As noted above, this change in clearance
between ring 20 and impeller 40 assists in forming a liquid ring
that permits operation of vacuum pump 10. It will be recognized
that the minimum gap, or clearance, between ring 20 and impeller
40, particularly at the top thereof, can have a significant impact
on the performance and/or efficiency of vacuum pump 10.
[0043] FIG. 3 is a schematic illustration of an eccentric ring 56
that may be used within vacuum pump 10. It will be recognized that
in FIG. 3, the eccentricity of eccentric ring 56 has been
exaggerated for illustrative purposes, and may represent one
illustrative embodiment of ring 20 of FIG. 2. In some instances,
eccentric ring 56 may have an outer annular surface 58 and an inner
annular surface 60. Outer annular surface 58 may be considered as
defined by a first circle having a first center 62 and inner
annular surface 60 may be considered as defined by a second circle
having a second center 64. It can be seen that second center 64 is
offset from first center 62. In some illustrative embodiments,
second center 64 may be offset by a distance of about 0.010 inch to
about 0.200 inch from first center 62.
[0044] FIG. 4 is a schematic illustration of eccentric ring 56 of
FIG. 3 disposed within an annular groove 48 in back plate 16. It
can be seen that annular groove 48 has an outer perimeter 66 that
is concentric with outer annular surface 58 and that is sized to
accommodate outer annular surface 58 of the eccentric ring 56.
Annular groove 48 may have an inner perimeter 68 that is concentric
with outer perimeter 66 and that is sized to accommodate a maximum
wall thickness of eccentric ring 56.
[0045] It can be seen that a tolerance between eccentric ring 56
and impeller 40 (when eccentric ring 56 is used as ring 20 of FIG.
2) may be adjusted by rotating eccentric ring 56 relative to back
plate 16 (FIG. 2). In some cases, eccentric ring 56 may be rotated
by loosening one or more of the plurality of bolts 50 so that
eccentric ring 56 is free to rotate, then rotating eccentric ring
56, followed by re-tightening the loosened bolts 50. It is
contemplated that, for example, eccentric ring 56 may be rotated
until it binds against impeller 40, and then reversed slightly. In
some cases, eccentric ring 56 may include one or more setpoint
markings that may be aligned against an alignment mark on back
plate 16. These setpoint markings may be used not only for guiding
adjustments, but also for initial assembly, if desired.
[0046] In some cases, it may be desirable to completely remove
cover plate 18 (FIG. 2) so that the gap or tolerance between
eccentric ring 56 and impeller 40 may be visually or mechanically
inspected. In some instances, a feeler gauge may be used to
ascertain the gap or tolerance between eccentric ring 56 and
impeller 40. In some cases, an acceptable tolerance between
eccentric ring 50 and impeller 40 may be in the range of about
0.040 inch to about 0.090 inch, but other tolerances may be used,
as desired.
[0047] Another advantage to completely removing cover plate 18 is
that this permits a visual inspection of impeller 40, so that any
broken or bent vanes 42 may be recognized. If such damage is found,
it may be necessary to replace impeller 40. When replacing cover
plate 18, it may be desirable to reverse cover plate 18, especially
if one side of cover plate 18 (the side previously facing impeller
40) is partially worn. This may extend the useful life of the cover
plate 18.
[0048] FIGS. 3 and 4 illustrate an embodiment in which eccentric
ring 56 is formed with inner annular surface 60 is defined by a
circle that is offset from a circle defining outer annular surface
58. In some cases, however, it may be desirable to instead use an
eccentric ring having an eccentric outer surface, sometimes only at
one end of the ring. FIGS. 5, 6 and 7 demonstrate such an eccentric
ring.
[0049] FIG. 5 is a perspective view of an eccentric ring 57, and
FIG. 6 is a cross-sectional view taken along line 6-6 of FIG. 5.
Eccentric ring 57 has an outer annular surface 59 with a concentric
inner annular surface 61. Outer annular surface 59 may, if desired,
include an annular notch or groove 63 that may be molded, milled,
ground, or otherwise formed within outer annular surface 59 along
the side of eccentric ring 57 that is disposed closest to a back
plate such as back plate 16 (FIG. 2). A smaller groove 65 may be
molded, milled, ground, or otherwise formed within an opposing edge
of eccentric ring 57. Groove 65 may be configured to accommodate an
O-ring such as first O-ring 42 (FIG. 2). In some cases, groove 65
may have dimensions slightly less than those of first O-ring 42, so
that first O-ring 42 may extend out of groove 65 sufficiently to
contact and seal against a cover plate such as cover plate 18 (FIG.
2).
[0050] In some cases, notch or groove 63 may be formed such that it
has a depth (measured, for example, from outer annular surface 59)
that varies depending on the radial position around eccentric ring
57. In some instances, the depth of notch or groove 63 may vary
from a maximum depth at (in the illustrated orientation) a top of
eccentric ring 57 to a minimum depth at the bottom of eccentric
ring 57. In some cases, notch or groove 63 may be formed having a
center of curvature that is offset about 0.050 inch from the
central axis of the outer annular surface 59 and the inner annular
surface 61, which may result in the remaining end portion of the
eccentric ring 57 adjacent the notch or groove 63 having an
effective thickness at the bottom of the ring 57 that is about
0.100 inch greater than the thickness of the top of eccentric ring
57.
[0051] FIG. 7 shows eccentric ring 57 disposed within vacuum pump
10. Impeller 40 is mounted to shaft 26, as previously described.
Eccentric ring 57 is disposed between a back plate 16a and cover
plate 18. Back plate 16a is similar to back plate 16 previously
described, but includes a groove 67 that may be molded, milled,
ground or otherwise formed within back plate 16a to accommodate an
O-ring such as second O-ring 44 (FIG. 2). In some cases, groove 67
may have dimensions slightly less than those of second O-ring 44,
so that second O-ring 44 may extend out of groove 67 sufficiently
to contact and seal against eccentric ring 57.
[0052] In some cases, back plate 16a may be formed to have a step
69 that provides an annular surface against which the end of the
ring 57 that includes annular notch or groove 63 may rotate.
Because the notch or groove 63 is eccentric relative to the outer
annular surface 59 and the inner annular surface 61 of the ring,
when eccentric ring 57 rotates with respect to back plate 16a (and
hence with respect to impeller 40) along step 69, the gap or
tolerance between inner annular surface 61 of the ring and impeller
40 may be adjusted.
[0053] As discussed above with respect to eccentric ring 56 (FIGS.
3 and 4), in some cases, eccentric ring 57 may be rotated by
loosening one or more of the plurality of bolts 50 so that
eccentric ring 57 is free to rotate, then rotating eccentric ring
57, followed by re-tightening the loosened bolts 50. Likewise, it
is contemplated that, for example, eccentric ring 57 may be rotated
until it binds against impeller 40, and then reversed slightly. In
some cases, eccentric ring 57 may include one or more setpoint
markings that may be aligned against an alignment mark on back
plate 16a. These setpoint markings may be used not only for guiding
adjustments, but also for initial assembly, if desired.
[0054] In some cases, it may be desirable to completely remove
cover plate 18 (FIG. 2) so that the gap or tolerance between
eccentric ring 57 and impeller 40 may be visually or mechanically
inspected. In some instances, a feeler gauge may be used to
ascertain the gap or tolerance between eccentric ring 57 and
impeller 40. In some cases, an acceptable tolerance between
eccentric ring 57 and impeller 40 may be in the range of about
0.0040 inch to about 0.090 inch, but other tolerances may be used,
as desired.
[0055] In some cases, a gap or tolerance between impeller 40 and
ring 20 (FIG. 2) may be adjusted by translating ring 20, rather
than by rotating ring 20. FIGS. 8 and 9, in combination, illustrate
how translating ring 20 may adjust the gap or tolerance between
impeller 40 and ring 20.
[0056] In particular, FIG. 8 illustrates a concentric ring 70
disposed adjacent back plate 16 and impeller 40. Concentric ring 70
may be considered as having a uniform or at least substantially
uniform wall thickness all the way or at least substantially all
the way around concentric ring 70. In some cases, as illustrated,
concentric ring 70 has, in cross-section, an outer surface 72 that
is defined by a first circle and an inner surface 74 that is
defined by a second circle. The first circle and the second circle,
while not the same size, may have a common center.
[0057] It will be recognized that the position of impeller 40 is
typically fixed by virtue of impeller 40 being secured to shaft 26.
Thus, any change in the relative position of impeller 40 with
respect to concentric ring 70 may be achieved by moving, or
translating, concentric ring 70.
[0058] In FIG. 8, it can be seen that concentric ring 70 has been
moved upwards (in the illustrated orientation) as far or nearly as
far as possible, as concentric ring 70 is in close proximity, if
not in actual contact, with threaded apertures 22 located at or
near the top of back plate 16. This position may, for example, be
used when impeller 40 and concentric ring 70 are new or at least
have not substantially been worn. A small tolerance or gap can be
seen between the top of impeller 40 and the top of concentric ring
70.
[0059] As impeller 40 and/or inner surface 74 of concentric ring 70
begin to wear, concentric ring 70 may be moved downwards to
compensate for this wear. As discussed above with respect to FIG.
2, concentric ring 70 may be held in position by virtue of being
sandwiched between cover plate 18 and back plate 16 by bolts 50.
Thus, concentric ring 70 may be adjusted by loosening bolts 50
(FIG. 2), translating concentric ring 70, and then re-tightening
bolts 50.
[0060] In some instances, concentric ring 70 may be adjusted by
moving concentric ring 70 downward until it contacts impeller 40,
and then moving the concentric ring 70 slightly upwards. In some
cases, it may be useful to completely remove cover plate 18 so that
the tolerance between the impeller 40 and the concentric ring 70
can be measured and/or visually inspect and/or clean the components
underneath cover plate 18. As indicated above, in some instances,
it may be useful to reverse cover plate 18 prior to
reattachment.
[0061] To give a sense of the adjustment that can be made in the
relative position of concentric ring 70, FIG. 9 shows concentric
ring 70 moved downward (in the illustrated orientation) as far as
it can go. i.e., outer surface 72 is in proximity to or even in
contact with at least some of the threaded apertures 22 located at
or near the bottom of back plate 18. At the same time, impeller 40
is represented in a pristine, or unworn, condition. It can be seen
that some of the vanes 42 on impeller 40 extend into concentric
ring 70. While this exact configuration is not workable, it
provides an idea of illustrative adjustment ranges that are
possible.
[0062] In some instances, it may be useful for vacuum pump 10 to
include adjustment structure or structures are adapted to help make
small translational adjustments in the position of concentric ring
70. FIGS. 10 and 11 show illustrative adjustment structures. FIG.
10 illustrates concentric ring 70 disposed adjacent back plate 16,
with impeller 40 disposed within concentric ring 70.
[0063] In this Figure, it can be seen that vacuum pump 10 includes
several eccentric cams 76 that are disposed near an upper (in the
illustrated orientation) portion of concentric ring 70 as well as
several eccentric cams 78 that are disposed near a lower portion of
concentric ring 70. Eccentric cams 76 may be thought of as being
positioned to exert a downward force on outer surface 72 of
concentric ring 70, while eccentric cams 78 may be thought of as
being positioned to provide a counterforce to that provided by
eccentric cams 76.
[0064] In some cases, if desired, vacuum pump 10 may include one,
two, three, or more eccentric cams 76 positioned along an upper
portion of concentric ring 70 and one, two, three, or more
eccentric cams 78 positioned along a lower portion of concentric
ring 70.
[0065] Each eccentric cam 76 and each eccentric cam 78 may, if
desired, pivot about an attachment point 80. In some cases, each
attachment point 80 may be a screw, bolt or other fastener that may
be loosened or tightened. In some cases, as illustrated, attachment
points 80 are distinct from threaded apertures 22 that are used for
securing cover plate 18. In some instances, attachment points 80
may simply be apertures that align with one or more of threaded
apertures 22 and that permit bolts 50 to pass through attachment
points 80, if desired.
[0066] In order to adjust the relative positions of each eccentric
cam 76 and each eccentric cam 78, the attachment points 80 may be
loosened. In some cases, a wrench or similar tool may be used to
rotate one or more of the eccentric cams 76 and/or the eccentric
cams 78. If desired, each eccentric cam 76 and each eccentric cam
78 may include a square or other shaped end 82 that facilitates
adjustment with a wrench or similar tool.
[0067] In some cases, cover plate 18 (not seen in this Figure) may
be loosened or even removed prior to adjusting the position of
concentric ring 70 by rotating one or more of the eccentric cams 76
and one or more of the eccentric cams 78. If cover plate 18 is
removed, a feeler gauge or similar instrument may be used to
determine and set the gap or tolerance between inner annular
surface 74 of concentric ring 70 and impeller 40. FIG. 11 provides
an illustrative vacuum pump 10 that includes several adjustment
structures 84 that are disposed along an upper (in the illustrated
orientation) portion of concentric ring 70 and several adjustment
structures 86 that are disposed along a lower portion of concentric
ring 70. Adjustment structures 84 may be thought of as being
positioned to exert a downward force on outer annular surface 72 of
concentric ring 70 while adjustment structures 86 may be thought of
as being positioned to provide a counterforce to that provided by
adjustment structures 84.
[0068] In some cases, if desired, vacuum pump 10 may include one,
two, three, or more adjustment structures 84 positioned along an
upper portion of concentric ring 70 and one, two, three, or more
adjustment structures 86 positioned along a lower portion of
concentric ring 70.
[0069] Each of the adjustment structures 84 and each of the
adjustment structures 86 include a base portion 88 that is welded,
bolted, or otherwise attached to base plate 16. Each base portion
88 may include a threaded aperture that accommodates a threaded rod
90 having a handle portion 92. Handle portion 92 may be configured
to permit hand operation. In some cases, handle portion 92 may be
configured to accommodate a tool such as a wrench or a screwdriver.
The threaded rods 90 may be turned in either direction, thereby
either advancing or retracting the threaded rod 90.
[0070] Turning one of the threaded rods 90 in a first direction,
such as clockwise, will cause the threaded rod 90 to advance
towards concentric ring 70 and thus the threaded rod 90 may apply a
force to concentric ring 70 sufficient to move concentric ring 70.
Turning one of the threaded rods in a second direction, such as
counter-clockwise, will cause the threaded rod 90 to retreat from
the concentric ring 70.
[0071] Thus, to move concentric ring 70 in a downward direction, it
may be useful to turn each of the threaded rods disposed within
adjustment structures 84 in a clockwise direction while also
turning each of the threaded rods 80 disposed within adjustment
structures 86 in a counter-clockwise direction. It will be
understood that it may be useful to either loosen or remove cover
plate 18 prior to adjusting the position of concentric ring 70.
[0072] In each of the Figures discussed thus far, vacuum pump 10
has included a flat or relatively flat cover plate 18. It is
contemplated, however, that vacuum pump 10 could instead employ a
dish or bowl-shaped cover. FIG. 12 shows a schematic cross-section
of a cover 94 that may be sized and configured to provide the
function of the cover plate 18 and the ring 20 (FIG. 2). In some
cases, cover 94 may include a flange portion 96 that permits cover
94 to be bolted to base plate 18, as discussed previously with
respect to cover plate 18. Cover 94 may be seen as including a
lower surface 95 disposed within flange portion 96. In some
instances, the cover 94 itself may be translated to provide a
particular gap or tolerance between impeller 40 and an inner
surface 98 of cover 94.
[0073] It is contemplated that a cover could also be rotated in
order to adjust a gap or tolerance. FIG. 13 shows an illustrative
cover 100 that may have a varying wall thickness (much like
eccentric ring 56). A tolerance between impeller 40 and an inner
surface 102 of cover 100 may be adjusted simply by rotating cover
100. A flange 104 may permit cover 100 to be bolted to base plate
16. Cover 100 may be seen as including a lower surface 101 disposed
within flange portion 96. In some cases, flange 104 may include
elongated bolt apertures that match the curve of cover 100 and that
permit cover 100 to be rotated to achieve a desired tolerance.
[0074] It will be recognized that minor manufacturing tolerances
may exist in one or more of the components within liquid ring
vacuum pump 10. In some cases, a tolerance or gap between cover
plate 18 (or cover 94 or 100) and a side of impeller 40 (FIG. 2)
may impact the performance and efficiency of liquid ring vacuum
pump 10. FIGS. 14 and 15 show an illustrative cover 106 that may be
used to compensate for manufacturing tolerances and/or for
wear.
[0075] Cover 106 includes a cover portion 108 and a flange 110 that
may be used for securing cover 106 to back plate 16 (or 16a) as
discussed above. If desired, flange 110 may include any appropriate
mounting apertures, adjustment structures, and the like. In FIG.
15, it can be seen that cover portion 108 has a lower surface 112
and an upper surface 114. Lower surface 112 is not parallel with
upper surface 114. When secured to back plate 16 (or 16a) with an
intervening ring, upper surface 114 may be parallel or at least
substantially parallel with back plate 16 (or 16a).
[0076] In some instances, lower surface 112 may not be parallel
with back plate 16 (or 16a), and thus lower surface 112 may not be
parallel with a side of impeller 40 (FIG. 2). Therefore, it can be
seen that a tolerance or gap between lower surface 112 and a side
of impeller 40 may be adjusted by either rotating or translating
cover 106 relative to impeller 40. In some cases, cover 106 may be
rotated or translated to adjust a gap or tolerance between cover
106 and impeller 40 at a position adjacent to where the gap or
tolerance between ring 20 (or eccentric ring 56, concentric ring 70
or eccentric ring 57, for example) is at a minimum. In a like
manner, it is contemplated that the lower surfaces 95 and/or 101 of
the covers shown in FIGS. 13 and 14 may also be angled (e.g.
non-parallel) relative to the side of the impeller so that the gap
or tolerance between the cover and the impeller may likewise be
adjusted.
[0077] The invention should not be considered limited to the
particular examples described above, but rather should be
understood to cover all aspects of the invention as set out in the
attached claims. Various modifications, equivalent processes, as
well as numerous structures to which the invention can be
applicable will be readily apparent to those of skill in the art
upon review of the instant specification.
* * * * *