Sealed and pressure balanced oil lubricating system

A sealed and pressure balanced lubricating system for high pressure rotary equipment includes a housing with a bore divided by a slidable piston into a lubricant chamber and a gas chamber. The gas chamber communicates with an area of the equipment which is exposed to high gas pressure and the lubricant chamber communicates with bearings within the equipment. During operation gas pressure forces the piston against the lubricant to pressure feed the bearings. A relief valve in the piston is opened, after the equipment stops and the pressure therein returns to atmospheric, in the event that pressurized gas has become entrained in the lubricant due to leakage past shaft seals. Such gas forces the piston back towards the gas chamber; the relief valve contacts an actuator and is opened; and the gas escapes to atmosphere through the piston and the gas chamber. The invention prevents problems due to high pressure gas entrained in lubricants of high pressure rotary equipment by quickly exhausting such entrained gases when the system pressure returns to atmospheric.

The present invention relates to a balanced lubricating system for 
lubricating bearings associated with rotary equipment exposed to high 
pressure gases. 
BACKGROUND OF THE INVENTION 
There are many uses for vessels which may be required to withstand high 
internal pressures, say up to and even beyond 20,000 p.s.i., whether in 
the laboratory, industry or the military. One example is a decompression 
chamber for deep-sea divers, which chamber requires a power source to 
operate equipment therein, such as rotary gas pumps for circulating the 
breathing gas mixture through carbon dioxide scrubbers to remove the 
carbon dioxide. Another example is a high-pressure autoclave used to treat 
materials at upwards of 10,000 p.s.i. (680 atmospheres) and which may 
require rotary equipment therein to circulate gases at the high pressures 
within the autoclave. It is not practical or safe to install electrical 
motors within such chambers and hence the drive for the rotary equipment 
for such devices must be external to the pressure chamber. It is, of 
course, necessary to transfer power from a drive motor through the wall of 
the pressure chamber without permitting the escape of any pressurized 
gases from the chamber. 
Commonly assigned Canadian Patent Nos. 1,129,469 of Aug. 10, 1982 and 
1,146,207 of May 10, 1983 illustrate two magnetic drives which 
successfully transfer power to high pressure chambers. Copending Canadian 
Application No. 585,241 of Dec. 7, 1988 illustrates another such device. 
The prior art drives have, in common, a drive shaft which extends through 
the pressure chamber wall from the exterior drive system to the interior 
driven system. The shaft bearings within and without the pressure chamber 
must be lubricated by a suitable lubricant such as oil. During operation 
of the rotary equipment, however, it is impossible to prevent small 
amounts of pressurized gas from entering the oil and, when operations 
cease and the pressure chamber returns to atmospheric pressure, the gas 
which entered the oil under pressure will expand (perhaps by a factor of 
680), causing all sorts of lubricating problems, not the least of which is 
loss of oil and consequent bearing damage. There is, therefore, a need in 
such equipment for a lubricating system which compensates for any leakage 
of high pressure gas into the lubricant so that when pressures within the 
rotating equipment are reduced such gas as may be trapped in the lubricant 
will not cause problems within the lubricant system. 
SUMMARY OF THE INVENTION 
The present invention meets the above requirement by providing a balanced 
lubrication system which is, for all intents and purposes, a closed loop 
system. With the invention the lubricating system is pressurized to 
slightly above the internal operating pressure of the rotating equipment 
so that, preferably, if there is any leakage there will be a leakage of 
lubricant into the gas rather than vice versa. However, should there be 
gas leakage into the lubricant, the lubricant system will release any high 
pressure gas trapped in the lubricant back to the gas portion of the 
system during pressure reduction so that such trapped gas will not have an 
opportunity to expand greatly within the lubricant. 
The invention uses a housing capable of withstanding the operating 
pressures of the rotary equipment, the housing being divided internally by 
a reciprocable piston having a one-way pressure relief valve therein. 
Lubricant is contained within a lubricant chamber on one side of the 
piston and is communicated to the bearings by appropriate conduits. The 
other side of the piston is a gas chamber connected via a passageway to an 
area of the rotary equipment which is exposed to the high operating 
pressures of the equipment. The gas chamber includes a rod or other device 
for opening the relief valve in the piston should the relief valve contact 
the rod and the gas chamber also includes a spring for applying a preload 
on the piston, and hence on the lubricant within the lubricant chamber, 
the preload being in the order of 14 p.s.i. 
When the rotary equipment is at operating pressure the gas chamber will be 
at the same pressure and the piston will be forced towards the lubricant 
in the lubricant chamber to lubricate the bearings of the equipment. When 
the equipment ceases to operate and the pressure therein drops to 
atmospheric the piston will return towards the gas chamber until balanced 
by the preload spring. If there is any high pressure gas entrapped in the 
lubricant due to leakage, that gas will migrate to the lubricant chamber 
as it expands and act on the piston to drive it towards the gas chamber. 
Such movement brings the relief valve into contact with the actuating rod, 
causing the relief valve to open so as to release the pressurized gas to 
the gas chamber and hence to atmosphere. A small amount of lubricant may 
be lost but it can be easily replenished. 
Broadly speaking, therefore, the present invention may be seen as providing 
a balanced lubricating system for lubricating bearings associated with 
rotating equipment exposed to high pressure gases to offset any leakage of 
such gases into the lubricant comprising: high pressure housing means 
closed at each end thereof; conduit means leading from one end of the 
housing means to the bearings to be lubricated; reciprocable piston means 
slidably and sealingly contained within the housing means intermediate the 
ends thereof, the piston means serving to divide the housing means into a 
lubricant chamber and a gas chamber; spring biased relief valve means 
within the piston means, the opening direction of the relief valve means 
relative to the piston means being towards the lubricant chamber; relief 
valve actuation means within the gas chamber; spring biasing means within 
the gas chamber for applying a preload on the piston means in the 
direction of the lubricant chamber; and passage means connecting the gas 
chamber to an area within the equipment which, during operation thereof, 
will be exposed to high pressure gases; whereby (i) as the equipment 
operates pressured gas from the area will be communicated via the passage 
means to the gas chamber to bias the piston means against lubricant in the 
lubricant chamber so as to transmit lubricant therefrom to the bearings 
via the conduit means; and (ii) when the equipment ceases to rotate and 
the area and gas chamber are returned to atmospheric pressure any 
pressurized gas which has leaked into the lubricant will migrate to the 
lubricant chamber and move the piston means towards the gas chamber due to 
the pressure differential thereacross, such movement bringing the relief 
valve means into engagement with the actuation means to open the relief 
valve means and thereby permit the pressurized gas in the lubricant to 
escape to the gas chamber through the piston means and hence escape to 
atmosphere. 
The invention will now be described with reference to the drawings.

DESCRIPTION OF THE PREFERRED EMBODIMENT 
FIG. 1 illustrates, somewhat schematically, a practical application for the 
present invention. FIG. 1 shows a blower housing 10 containing rotary 
equipment, such as a blower or impeller which can create high pressure 
moving air therein, which air is communicated via conduit 12 to an 
autoclave or a hyperbaric chamber (not shown). A motor 14 mounted to a 
table 16 along with blower housing 10 drives a magnetic drive 18 in a 
manner as described in the aforementioned pending application or in 
Canadian Patent No. 1,129,469. The magnetic drive includes a shaft 20 
(FIG. 2) which passes into the blower housing 10 and is supported 
rotationally by bearings 22, 24 in the drive and the blower housing 
respectively. 
Lubricant for the bearings 22, 24 is supplied via conduits 26, 28 from a 
balanced lubricant supply unit 30 which is at the heart of this invention 
and is only shown schematically in FIG. 1. The important features thereof 
are the high pressure housing 32, the reciprocable piston 34 dividing the 
housing into a lubricant chamber 36 and a gas chamber 38, the relief valve 
40 in the piston 34, the actuating rod 42 in the gas chamber, and the 
preload spring 44 also in the gas chamber. The gas chamber 38 communicates 
with an area within the blower chamber which is exposed to the high 
operating pressures therein by a passage or conduit 46. 
With reference to FIG. 2 the magnetic drive means 18 typically includes a 
laminated hyperbaric barrier 48 surrounding the shaft 20. Lubricant can 
pass along the shaft between the bearings 22, 24 along the narrow 
circumferential gap (not shown) between the shaft and the barrier 48. At 
the tail end 50 thereof the drive 18 includes a port 52 to which conduit 
26 can be connected so that lubricant L therein has access to the lower 
end of shaft 20 and hence to the bearings 22. Further details of the 
magnetic drive 18 are not required for a full understanding of the present 
invention. 
The blower housing 10 contains the rotary equipment, such as an impeller or 
blower 54, connected to the shaft 20 by suitable means such as bolt 56. 
During rotation of the impeller 54 the area 58 will be at the operating 
pressure of the blower and such pressure will be communicated to the area 
60 by way of openings 62a in the mounting flange 62. A dynamic lip seal 64 
is provided for engagement with the shaft 20 during rotation thereof, 
which seal serves to prevent lubricant from escaping from the lubricant 
space 66, which space contains the bearings 24 and is connected via port 
68 with the lubricant conduit 28. Port 70 through the blower housing 10 
connects the high pressure area 60 with the gas passage 46. As with the 
magnetic drive 18 further details of the bloer housing 10 are not required 
for an understanding of the present invention. 
Turning now to FIGS. 3, 4 and 5 further details of the balancing unit 30 
will now be described. Unit 30 includes an elongated, generally 
cylindrical high pressure housing 32 which includes a cylindrical axially 
extending bore 72 therein, open at one end only. At the other end the bore 
72 terminates at a hemispherical end wall 74 contained within housing end 
wall 76. Lubricant outlet ports 78, 80 extend through the housing 32 for 
connection to conduits 26, 28 respectively (see FIG. 2) and communicate 
those conduits to the bore 72. 
Piston 34 is slidably and sealably reciprocable within the bore 72, 
dividing the bore into a lubricant chamber 36 on one side thereof and a 
gas chamber 38 on the other side thereof. Ports 78, 80 communicate with 
the lubricant chamber portion of bore 72. 
The piston 34 is generally cylindrical and is provided with 
circumferentially extending split wear rings 82 within mating recesses 
machined in the outer surface of the piston. A blind bore 84 extends into 
the piston 34 from the gas chamber side thereof and boss portion 86 of the 
piston extends into the bore 84 from the blind end thereof. A blind bore 
88 extends into the piston 34 from the lubricant chamber end and an 
annular boss 90 defines an annular valve seat 92 thereon. An axial bore 94 
extends through the central portion of the piston to communicate bore 84 
with bore 88. If desired, the gas chamber end of bore 94 may be internally 
threaded as at 96 for purposes to be described hereinafter. 
At the lubricant chamber end an annular radial seal 98 is provided in an 
annular recess of the piston 34 to seal the piston relative to the bore 
72. Seal 98 is a commercially available seal comprising a TEFLON (trade 
mark) cover over a stainless steel spring. 
A cylindrical relief valve retainer 100 is located within blind bore 88, 
retainer 100 including a cylindrical flange portion 102 which engages the 
end face of the piston and is secured thereto by machine screws (not 
shown), the heads of which are recessed or countersunk in the flange 
portion 102. Preferably four such screws are used, the screws alternating 
with axially extending bores 104. Between the inner end of retainer 100 
and the inner end of the blind bore 88 there is positioned a thin 
cylindrical sleeve 106. Sleeve 106 and split rings 82 are made from a 
smooth plastics material such as RULON (trade mark). 
A plurality, such as four, of axially extending blind bores 108 extend into 
the inner end face of retainer 100, each bore 108 receiving a stainless 
steel compression spring 110, which springs normally extend beyond the 
retainer inner face and support the relief valve 40 thereon. Each spring 
110 typically has a spring force of about 7 lbs. 
The relief valve 40 is best shown in FIGS. 4 and 5 wherein it is seen as a 
lobed disk having outer lobes 112 separated by arcuate recesses 114. The 
lobes 112 are formed with a transversely rounded edge 116 which is adapted 
to contact the sleeve 106 and to be centered thereby. The face 118 of 
valve 40 which faces inwardly has an annular, generally trapezoidal groove 
120 therein, the radially outer and inner walls 122, 124 of the groove 
converging towards the face 118. Groove 120 receives an O-ring 126 (FIG. 
3) which projects slightly beyond face 118 for sealing engagement with the 
annular valve seat 92. In order to prevent the high pressures encountered 
in the unit 30 from dislodging the O-ring 126 the groove 120 communicates 
with the exterior of the relief valve via radially directed grooves 128 
which extend to the recesses 114. 
The gas chamber 38 is closed by way of a plug 130 which sealingly is 
secured within the bore 72. Preferably the plug 130 is removable for 
disassembly of the unit 130 and hence mating threads can be provided on 
the plug 130 and the bore 72, the enlarged head 132 of the plug being used 
to apply a rotational force thereto to remove the plug. The plug at its 
inner end has the cylindrical actuating rod 42 formed integrally 
therewith, the rod extending through the gas chamber 38 axially thereof 
and into the axial bore 94 of the piston 34 to adjacent the face 118 of 
the relief valve 40. 
The preload or bias spring 44 is also contained within gas chamber 38 and 
extends inwardly thereof from plug 130, surrounding actuating rod 42. A 
spring retainer 134 secures one end of the spring 44 to the plug 130, the 
other end of spring 44 extending into blind bore 84 of the piston and 
engaging the boss 86 therein. Typically the spring 44 will apply a spring 
force of about 55 lbs. against the piston 34 in operation. If plug 130 and 
spring 44 are removed a threaded rod (not shown) may be threaded into the 
threads 96 in piston 34 to remove the piston from the unit or to push it 
further into the lubricating chamber 36. 
Gas port 136 in the housing 32 communicates the gas chamber 38 with the 
passage or conduit 46 which in turn leads to the high pressure area 60 in 
the blower housing 10. 
At the lower end of lubricant chamber 36 there is a piston stop and flow 
directing member 138. Member 138 has a cylindrical flange 140 sealingly 
engaging the wall of bore 72 and a cylindrical foot 142 extending to the 
end face of hemispherical end 74. A bore 144 in member 138 receives a 
cylindrical flow divider 146 which in turn has an axial bore 148 
communicating with port 78. Radial ports 150 in the foot 140 communicate 
with the port 80. 
Lastly, the retainer 100 is provided with a blind bore in the end facing 
the lubricant chamber 36, which bore receives therein a set of magnets 152 
held therein by a non-magnetic retainer 154. The magnets 152 are all 
oriented to have the same magnetic pole facing outwardly. The magnets 152 
are intended to cooperate with an indicator device 156 positioned exterior 
to housing 32 so as to provide a visual indication of the piston position 
with the balancing unit 30. 
Indicator device 156 includes a base 158 secured to the housing 32 in any 
suitable manner and having an arcuate cut-out or recess 160 therein. An 
arcuate, protractor-like bar 162 is attached to base 158 in any suitable 
manner and may carry appropriate chart means or indicia such as coloured 
zones (green for normal operation, red for danger) and/or degree or 
position markings. A pointer 164 is pivotally mounted to base 158 and has 
a magnet 166 closest to housing 32 being opposite to the outer pole of 
magnets 152. The opposite end 168 of pointer 164 is adjacent the bar 162 
so that upwards or downwards movement of piston 34 is magnetically 
detected by the magnet on pointer 164 and indicated by the position of 
pointer end 168 relative to bar 162. 
Three further features of the present invention will be described before 
discussing the operation of the invention. First of all in FIG. 1 a hand 
pump 170 is shown connected to a lubricant reservoir 172 via line or 
conduit 174 and, via line 176 and check valve 178, to the conduit 26. By 
using the pump 170 the balancing system may be topped up with lubricant 
from reservoir 172 should the necessity arise. Secondly, with reference to 
FIG. 2, a heat exchanger 180 may be provided on the conduit 28 and/or on 
the conduit 26 to cool the lubricant flowing through the conduit(s) to the 
bearings. A suitable coolant, such as water, may flow through the heat 
exchanger in the direction of the arrows to remove heat from the 
lubricant. This feature will be very useful for equipment used in hot 
environments or wherein a great deal of heat, perhaps upwards of 
300.degree. C., is generated within the rotary equipment. Finally, it may 
be desirable to machine a spiral groove 182 in the shaft 20 so as to 
promote movement of the lubricant towards the bearing 24. 
OPERATION 
At static conditions, without the shaft 20 rotating, and the lubricant 
system topped up with lubricant, the bias or preload spring 44 will apply 
a preload force of about 12 to 14 p.s.i. on the piston 34, ensuring that 
there is always lubricant supplied to the bearings 22, 24. As the shaft 20 
and the rotary equipment connected thereto come up to speed there will be 
a considerable increase in pressure in the areas 58, 60 and that pressure 
will be communicated, via port 70, passage 46 and port 136, to the gas 
chamber 38. Such pressure, over and above the preload on the piston 34 
from spring 34, will act on the piston 34 and hence on the lubricant in 
chamber 36, lines 26, 28 and in the bearing spaces. Due to the preload 
from spring 44 the lubricant pressure should always be slightly greater 
than the gas pressure and that should be sufficient to keep any gas from 
infiltrating into the lubricant, as for example across the lip seal 64. 
In a real life, however, pressurized gas, albeit in very small volumes, 
does infiltrate the pressurized lubricant and can cause considerable 
damage when the pressure in the rotary equipment is reduced to 
atmospheric. When that happens with the present invention the pressurized 
gas in the lubricant attempts to expand in the lubricant chamber 36. That 
has the effect of driving the piston 34, due to the pressure differential 
thereacross, towards the gas chamber 38. During such movement the relief 
valve 40 encounters the end of actuating rod 42, is prevented thereby from 
moving with the piston, and hence the seal between O-ring 126 and seat 92 
is broken. The pressurized gas from the lubricant can escape through bores 
104 in retainer 100, past the O-ring 126 and seat 92, through the axial 
bore 96 in piston 34 to gas chamber 38 and then to atmosphere through the 
rotary equipment. Once the gas has escaped and the pressure within the 
lubricant chamber has fallen to normal the spring 44 will move the piston 
34 backwards so that the relief valve 40 will close thereagainst. 
Should there be a prolonged loss of lubricant without topping up, as for 
example across lip seal 64, the piston 34 will move lower in bore 72 due 
to the depleted lubricant. Such movement will be apparent from the 
movement of pointer 164 and should signal an operator that topping up is 
required. Pointer 164 could even actuate an audible or visible alarm in 
the event that too much lubricant is being lost. Should the piston 34 move 
so far down in bore 72 that it encounters stop member 138 there could 
still be enough pressure to keep whatever lubricant remains flowing to the 
bearings since the gas pressure would open the relief valve 40 and then 
operate directly on the lubricant itself. This of course is not desirable 
but it is better than failure due to inadequate lubrication. 
Although the present invention was devised for the type of rotary equipment 
described herein it is clear that the invention could be used with other 
types of rotary equipment which are subjected or exposed to high pressures 
and require constant lubrication of bearings and other rotating parts. It 
is expected that a skilled practitioner could effect changes within the 
confines of the present invention without departing from the spirit 
thereof. Hence the protection to be afforded this invention is to be 
determined from the scope of the claims appended hereto.