Lubricating oil reconditioning system

Apparatus and methods for improved in-line contaminant removal from engine lubricating oil are provided which employ gravity to achieve a desired flow rate of oil. The invention is adapted for use with an existing engine oil lubrication system and continuously processes a side stream that after processing, is returned to the engine oil. During processing, the oil is first filtered and then drained and deposited upon the upper central surface portions of a heated dome whereon the oil forms a thin film from which relatively low boiling volatile impurities (especially water) are rapidly separated in a gaseous state. The gas is vented through a pressure relief valve to the manifold while the recovered reconditioned oil is collected and recycled.

FIELD OF THE INVENTION 
This invention relates to an improved apparatus and methods for the 
continuous removal of contaminants from the lubricating oil of an 
operating fuel combusting engine. 
BACKGROUND OF THE INVENTION 
In fuel combusting engines, particularly those of the internal combustion 
type using a liquid fuel such as gasoline or diesel oil, it is known that 
filtering of the circulating lubricating oil does not remove liquid 
contaminants from the oil. These liquid contaminants substantially 
comprise relatively low boiling condensates, especially water, whose 
presence in the oil causes engine corrosion and wear. 
Lubricating oil reconditioning systems that remove such liquid contaminants 
from circulating engine lubricating oil have previously been proposed for 
use in association with operating fuel combusting engines. Such prior art 
systems suffer from various disadvantages so that typically they are not 
energy-efficient, and not highly effective. 
For example, in the prior art, a filter assembly is commonly located below 
a vaporization chamber in an oil heating device, thereby relying on 
pressure for the oil to enter the chamber. Thus, prior art devices inject 
oil under pressure into the chamber making it difficult if not impossible 
to achieve a sustained thin film for impurity vaporization purposes. 
Additionally, variations in oil pressure due to changes in engine rpm vary 
the amounts of oil that are input into the chamber further reducing the 
effectiveness of the device. 
Menyhert U.S. Pat. No. 5,198,104, for example, discloses a device for 
removing volatile components from oil in which the oil is filtered before 
being subjected to a volatilization procedure using a heated plate with 
multiple protrusions. However, in such a device, the filter is positioned 
below the volatilization chamber so that oil accumulates in the filter and 
is wasted during a filter change. 
In Menyhert, a cartridge-type heater is used which characteristically does 
not distribute heat evenly to the vaporizing surfaces. Also, such a heater 
must be partially exposed to the outside elements, thereby increasing the 
likelihood of heater failure due to shorts and corrosion. 
Also, although Menyhert alleges that his "walls" maintain a thin film in 
conjunction with a swivel mount, since oil is fed under pressure into his 
chamber, it will spray and so the swivel mount is not effective for heavy 
duty use which requires strong stationary mounts. Also, his swivel mount 
places undue stresses on the inlet and outlet hoses and fittings. The only 
vaporizing surface in Menyhert is the centermost wall. The oil pools 
(collects) in the valleys of the concentric wall members and does not 
travel in a thin film. Since the oil enters under pressure, the oil, under 
increased pressure, sprays into the chamber and misses the first 
vaporizing wall surface. Menyhert cannot maintain a uniform thin oil layer 
during the volatilization procedure. 
In addition, for Menyhert to achieve a correct seal between his oil inlet 
and filter, the filter and the evaporator plate, and the cap and the outer 
canister, great effort must be extended to adjust and readjust the tension 
on the clamps and adjustable threaded center post. This leads to the 
generally unacceptable result of oil leaking through the seals and not 
being processed completely. 
For another example, in Engel U.S. Pat. No. 4,289,583, a heater post must 
contact the evaporator plate and transmit heat to the wall surfaces. This 
is a highly inefficient arrangement. Also, Engel '583 has the same spray 
introduction and uniform oil volatilization problems as Menyhert and other 
prior art heated plate pressure fed systems. The techniques taught for 
connecting and sealing the cap to the outer canister with bolts causes the 
bolt ears and castings to break under undue stress, thus causing major 
leaks. 
So far as is now known, no one has previously developed a lubricating oil 
reconditioning system wherein the oil is first filtered and then passed as 
a thin film over a heated, generally dome-configured platen using gravity 
as a primary means for controlling oil flow over the platen. 
SUMMARY OF THE INVENTION 
This invention relates in one aspect to a new and very useful improved 
process for carrying out in-line contaminant removal, especially the 
continuous removal of filterable particulates and relatively low boiling 
liquids, such as water and hydrocarbons, from an oil, particularly a 
lubricating oil that is being used in an operating internal combustion 
engine. 
By this process, a side stream comprising a minor fraction of the total 
volume of lubricating oil that is being pumped and circulated in an 
internal combustion engine from a collecting zone such as the engine oil 
pan to engine bearing surfaces is continuously separated and charged to a 
contaminant removal zone. In the contaminant removal zone, the side stream 
is first filtered preferably at a relatively low flow rate and then is 
discharged onto the central region of a heated, generally dome-configured 
heat exchange surface or platen so that the filtrate spreads as a thin 
fluid film over such surface. Components of the oil film particularly 
liquid contaminants, that have relatively low boiling points, such as 
water and hydrocarbons derived from engine fuel, are vaporized and thereby 
separated therefrom. The resulting oil continuously moves downwards, is 
collected from about the periphery of the domed surface, and is 
recirculated and admixed with the engine oil, preferably with engine oil 
in the engine oil pan. 
This invention further relates in another aspect to a new and very useful 
improved oil reconditioning apparatus for carrying out the inventive 
contaminant removal process. 
This apparatus employs a filter containing assembly and a platen containing 
assembly. Each assembly is suited for positioning and mounting in the 
engine compartment of a vehicle. Each assembly is provided with its own 
associated housing. The subassemblies are interconnected by conduit means. 
The platen assembly housing encloses upper surface portions of the platen 
and defines over such portions platen a vapor collecting chamber. A 
lubricating oil stream to be reconditioned is charged first into the 
filter. Oil filtrate from the filter flows upon the central portion of the 
domed platen, moves downwardly thereover as a thin film, collects at the 
platen periphery and flows downwardly into in a basin from where the 
collected oil is recirculated. Vapors collecting in the chamber can be 
recirculated to the engine intake manifold or released through a relief 
valve when the chamber pressure rises above a preset value or otherwise as 
desired. 
The dome-configured platen is preferably a spherical segment, more 
preferably a hemispherical shape, but other concavely upwardly curved 
configurations for the platen can be utilized, if desired, such as a dome 
configuration with concentric ridges therein. 
Optionally, the filtered oil can be sprayed into the vapor collecting 
chamber. Preferably, the spraying occurs over and above the apex of the 
dome-configured platen. Thereby, vaporization of contaminants is more 
efficient. 
The filter assembly accomplishes preparation of a freshly prepared filtered 
oil feed for charging to the platen assembly. A maximized amount of 
particulates, including sludge and like separatable contaminants, are 
removed from the oil undergoing reconditioning before that oil is charged 
to the platen assembly and formed thereon into a thin flowing film 
preferably commencing at the apex of the controllably heated domed platen. 
This procedure enhances the ability to efficiently remove a maximum amount 
of volatile contaminants, such as water, with a minimum amount of heat 
energy. 
The inventive apparatus permits the use of gravitational force to achieve 
the desired process flow pattern particularly in the region of the platen. 
Thereby, the amount of lubricating oil pumping capacity and pumping 
pressure required for a vehicular oil pump of the type needed for use in 
utilizing the reconditioning system of this invention is reduced to a 
level comparable to that used for an oil pump in a conventional engine 
lubricating oil recirculation system. 
The inventive process and apparatus are functionally associatable with an 
existing engine with a minimum amount of equipment alteration and with a 
minimum amount of labor and without redesigning the oil lubricating system 
of the engine. 
By regulating the flow of oil onto a centermost portion of a domed platen, 
any brief tilt of the unit or briefly applied centrifugal or inertial 
force, such as occurs in normal vehicular use, does not substantially 
disrupt the thin film or the oil dwell time on the platens evaporation 
surface. 
Other and further objects, aims, features, purposes, advantages, 
embodiments and the like will be apparent to those skilled in the art from 
the teachings of the present specification taken with the accompanying 
drawings and the appended claims.

DETAILED DESCRIPTION OF THE DRAWINGS 
Referring to FIG. 1, there is shown one embodiment of an engine lubricating 
oil reconditioning system of the present invention, such system being 
generally designated by the numeral 20. 
In system 20, lubricating oil that has drained and collected in a 
conventional engine oil pan 21 is withdrawn by conventional oil pump 22 
via interconnecting conduit 23 through a conventional oil screen structure 
24 located in oil pan 21. From pump 22, the oil is passed as a main 
lubricating oil stream successively through respective conduits 26 and 27 
into a conventional replaceable oil filter 28 or the like. 
In filter 28, oil under partial pump 22 pressure from conduit 27 is 
conventionally filtered to remove filterable contaminants, such as 
particulates including sludge; and the filtered oil passes into a conduit 
system 33 through which it is conveyed to engine bearings 34 for 
conventional lubrication purposes. From the bearings 34, the oil drains 
down (not detailed in FIG. 1) and is again collected in the oil pan 21 for 
recycling through pump 22. 
Conduits 26 and 27 are connected together through a by-pass valve or 
proportional flow divider 29 which divides the oil entering from conduit 
26 into two streams, a main oil stream in conduit 27 comprising more than 
50 volume percent of the oil that enters and flows through conduit 26 and 
a side oil stream in conduit 31 comprising the remaining volume percent of 
the oil. The side stream that enters and flows through conduit 31 feeds 
into an embodiment of oil the reconditioning apparatus of this invention, 
such embodiment being generally designated by the numeral 32. 
From conduit 31, the side oil stream under partial pressure generated by 
pump 22 enters into oil reconditioning apparatus 32 and is processed as 
described herein to separate filterable contaminants as well as low 
boiling contaminants from the oil. The resulting processed and 
reconditioned oil exits from apparatus 32 through interconnecting conduit 
36 and preferably passes (route not specifically detailed in FIG. 1) into 
oil pan 21 or the like for recycling and reuse in engine lubrication. The 
volatiles separated from the oil in apparatus 32 are discharged from 
apparatus 32 into conduit 37 and are preferably conveyed to the engine 
intake manifold (not detailed) or the like. 
The system 20 is well suited for installation in combination with a 
previously manufactured vehicular engine or the like using a kit or the 
equivalent. Such a kit can comprise, for example, the proportional flow 
divider 29, the oil reconditioning apparatus 32 and the interconnecting 
conduit components such as conduit 31. Observe that, in the system 20 
there are essentially two lubricating oil reconditioning systems, one 
system involving the main oil stream that is charged to conduit 27 in 
which the filter 28 is used for oil processing, and the second system 
involving the side oil stream that is charged to conduit 31 in which the 
apparatus 32 is used for oil processing. It is a feature of the system 20 
that it can be functionally associated with a vehicular engine without 
redesigning the originally installed lubricating oil system. Thus, usually 
even the originally installed lubricating oil pump (which is commonly 
located in the oil pan) can be used in the system 20. 
Those skilled in the art will readily also appreciate that, particularly in 
the case of relatively small vehicular engines, the apparatus 32 can be 
employed as a replacement or alternative for a conventional oil filter 
assembly, such as the replaceable oil filter 28 or the like. 
Referring to FIGS. 2-4, the structure and operation of apparatus 32 is 
shown. Conduit 31 is connected to a circular, flattened cap block or plate 
38 (see, for example, FIG. 3) that is itself conveniently comprised of a 
body of cast and machined metal. The connection with conduit 31 is 
accomplished by means of a threadably joined conventional compression 
fitting 39 or the like. In block 38, the oil entering from conduit 31 
passes generally radially in a channel 41 and enters an axial passage or 
bore 52 that is defined in a stud 43 which is threadably connected to 
block 38, the stud 43 here having chambered opposite ends. The upstanding 
circumferential outer surfaces 43A of stud 43 are threaded and adapted to 
be matingly threadably engaged with the threaded axial input orifice 47 
(not detailed but shown in phantom) of a canister-type replaceable oil 
filter assembly 44 (not detailed but shown in phantom). 
In this filter, oil flows from the outside in as is conventional. (Most 
standard auto filters have a "check valve" that will not allow inside out 
flow.) 
In addition, the face plate 48 of the filter 44 is provided with a 
conventional gasket-retaining shoulder 46 that outstands circumferentially 
in the face plate 48 in radially spaced relationship to the orifice 47, 
and a square section gasket ring 49 or the like is seated inwardly 
adjacent to shoulder 46 on face plate 48. The upper surface of block 38 is 
provided with an upstanding circular shoulder 51 that extends in radially 
spaced relationship to the passage 42 and whose outside upper surface is 
flattened. When filter 44 is threadably connected to stud 43, gasket ring 
49 sealingly seats against the shoulder 51. 
The axial bore 52 in stud 43 whose outer (oil entering) end is optionally 
but preferably fitted with an inset metering jet 53. Thus, pressurized oil 
from passage 42 enters bore 52 at a regulated pressure and flow rate and 
is discharged (preferably sprayed) into the filter 44. 
After passing through the filter medium 54 (not detailed, but shown in 
phantom) in filter 44, the filtered oil exits the filter 44 through its 
exit ports 56, passes through a cavity 55 and deposits upon and in a 
shallow, flat bottomed well 57 defined in the top of block 38 between stud 
43 and shoulder 51. A plurality of circumferentially spaced, diagonally 
downwardly and inwardly extending channels 58 (four are shown for 
illustrative purposes) extend from the bottom of well 57 through the block 
38. The channels 58 are thus adapted for the passage of oil therethrough 
from well 57. 
The peripheral bottom facial surface regions of the block 38 are flattened 
and adapted for face-to-face engagement with the upper, circumferentially 
extending rim edge 61 of a housing 59 that is itself conveniently 
comprised of a body of cast and machined metal. Housing 59 is shown 
preferably as a one-piece structure having in axial vertical section a 
generally W-shaped configuration. The outside wall 62 of housing 59 
upwardly extends circumferentially and terminates in the rim edge 61. 
Between, and joined to, the bottom regions of wall 62 at a cross-over 
region 63 is a hemispherically shaped thickened dome 64. Within the dome 
64 is cast a conventional type of spirally extending, electrically 
energizable, electrically insulated, resistance heated wire-like conductor 
or heater 66. 
Mounted across the bottom opening mouth 71 of the dome 64 by means of 
button head cap screws 72 or the like that are threadably received in the 
adjacent portions of the dome 64 is a flattened cover plate 67. A center 
hole 73 in plate 67 is conveniently provided with a conventional army-navy 
type rubber grommet 68. Through the center hole of the grommet 68 lead 
wires 69 interconnect with respective opposite ends of the spirally 
extending heater 66. When the apparatus 32 is being employed with a 
vehicular engine, the heater 66 can be selected so as to be operated by a 
12-volt energy source (such as a conventional vehicular battery) with the 
wattage being determined by such variables as the type of heater 66 
employed, the type of temperature control utilized and the like. Various 
types of conventional temperature control means can be used with a present 
preference being a temperature switch attached to the bottom surface of 
dome 64. The switch cuts the current to the heater at a predetermined 
upper limit and thereafter cycles the heater on and off to maintain the 
desired vaporization heat. The operating temperature for the heater 66 can 
be as desired. However, a present preference for use with the apparatus 32 
when associated with a conventional internal combustion engine is about 
180-190.degree. F. 
To connect the housing 59 with the block 38, a plurality of (for example, 
four) circumferentially spaced, transverse bores (not detailed) are 
provided about the perimeter of plate 59 which are each aligned with a 
plurality of corresponding circumferentially spaced, thickened wall 
portions 74 in the housing wall 62. A cap screw 76 with an associated lock 
washer 77, or the like extends through each plate 38 bore and is 
threadably received in a mating bore (not detailed) in each thickened wall 
portion 74. To achieve a seal between the block 38 and the housing 59, a 
flat gasket 78 is interposed therebetween. 
To mount the apparatus 32 to a surface, such as a vehicular firewall or the 
like (not detailed), the housing wall 62 is provided with a side 
projection 79 to which is affixed a mounting bracket 81 that is held to 
the projection 79 by means of hex-headed bolts 82 or the like. 
In operation, freshly filtered oil (not shown) from filter 44 passes down 
through the channels 58, deposits upon the central upper outer surface 
region of the heated dome 64, spreads and forms a thin film upon the 
heated surface of the dome 64. Volatiles, such as water, are rapidly 
boiled away or flashed from the oil film and enter into the gas space of 
the chamber 83 that is defined by the walls 62, the dome 64 and the plate 
38. When the gas (vapor) pressure in the chamber 83 reaches some 
predetermined value, a normally closed pressure relief valve 84 or the 
like automatically opens, thereby relieving the pressure in the chamber 
83. When the pressure within chamber 83 drops to some predetermined lower 
value, the relief valve 84 automatically closes, thereby returning the 
chamber 83 to its normally isolated state. 
The relief valve 84 is functionally connected to the conduit 37 using a 
compression fitting 86 or the like which, as indicated above, is in turn 
connected to the engine intake manifold (not shown). Thus, vapors released 
from the chamber 83 are not released directly to the atmosphere, but are 
injected into the heated manifold where combustion (oxidation) of 
combustible (oxidizable) components in the released vapors can occur (as 
is desirable for pollution control and abatement purposes). 
The oil on and from the surface of the dome 64 flows downwards by gravity 
and collects in a flat bottomed sump 87 between the bottom regions of wall 
62 and dome 64 over cross-over region 63. Oil in sump 87 is withdrawn 
through conduit 36 which is threadably connected though an aperture 
defined in a thickened portion 88 of wall 62 which aperture is connected 
to the conduit 36 by means of a threaded compression fitting 89. 
The housing 59 is also preferably provided (see FIG. 4) with another 
thickened portion 91 that is provided with a threaded aperture (not 
detailed) which is fitted with a threadably engaging plug 92 for purposes 
of optionally changing the location of fitting 89 and conduit 36 to 
achieve a direct routing back to the oil pan 21 in a particular 
application of apparatus 32. 
While the dome 64 (as shown) is preferably generally hemispherical in 
configuration, those skilled in the art will appreciate that other 
spherical segment configurations can be employed for the dome 64 (such as 
parabolic shapes, elliptical shapes, conical shapes and the like) and also 
that, broadly, any convexly curved or vertically centrally up-raised upper 
surface can be employed in the dome 64. The filtered oil is preferably 
deposited in the region of maximum upward projection of the dome 64 upper 
surface so that the flow path downwards (by gravity) of the oil comprising 
the thin film on the dome upper surface is of maximum length for achieving 
the preferred heat exposure to a thin film. 
Both the heating of the dome and the rate of oil film flow over the dome 
surface should preferably be relatively uniform with relatively "hot" or 
"cold" spots on the dome being avoided and with dome localized surface 
irregularities being avoided which could cause localized variations in oil 
film flow rate (and oil exposure time). 
While some residual pressurization of oil being processed in apparatus 32 
is maintained during residence of oil in apparatus 32, the force of 
gravity in accomplishing the desired oil flow characteristics plays an 
important role in the operation of apparatus 32. 
In normal operation, the oil pressure existing in, for example, the 
conduits 33 and 31 of system 20 is predictable and has a reliable value 
(over a set range) since the oil pump 22 of a given engine operates at 
about a constant pressure by engineering design. Also, in normal operation 
of a given engine, the pressure existing in the manifold falls within a 
predictable range, the exact pressure at any given instant being dependent 
upon such operating variables as engine rpm (revolutions per minute) 
engine load, rate and extent of fuel consumption, engine operating 
temperature and the like. Typically, the bulk average temperature of the 
oil in an operating internal combustion engine is below 212.degree. F. 
(100.degree. C.) at atmospheric environmental conditions. Thus, the flow 
rate of oil through apparatus 32 can be adjusted by a proportional flow 
divider 29 so that, during normal operating conditions, the oil level in 
sump 87 is sufficient to cover the aperture in thickened portion 89 
leading to the conduit 36. Thereby, an operating condition is avoided in 
which this oil level is below the top aperture so that gas in chamber 83 
can vent through conduit 36. 
Typically, in normal operation, the release gas pressure for valve 84 is 
set to be substantially above the oil fluid pressure normally existing in 
conduit 31. Thus, liquid oil enters into line 36 from sump 87 at any given 
time by a resultant combined pressure comprised of pressure in conduit 31, 
gravitational force and gas pressure in chamber 83. The release pressure 
for valve 84 is preferably chosen so as to be above the average manifold 
pressure so that, when valve 84 is open, manifold gases do not vent 
through conduit 37 back into chamber 83. The gas pressure in chamber 83 
thus aids in recirculating oil from apparatus 32. 
For purposes of enhancing the filtering of oil prior to the thin film 
flashing on the platen dome, particularly when the lubricating oil of a 
relatively large size engine is being reconditioned in accord with the 
present invention, filter subassemblies of large filtering capacity are 
preferred. For example, in the oil reconditioning apparatus 32, the single 
oil filter 44 can be replaced by a filter assembly 96 such as shown in 
FIGS. 7 and 8 that incorporates a pair of oil filters 97 and 98 (also 
conveniently both being of the same structure as the replaceable spin-on, 
canister-type filter 44). The assembly 96 is incorporated into an 
alternative system such as shown in FIG. 5 that is designated by the 
numeral 101 which utilizes the alternative apparatus such as shown in FIG. 
6 that is designated by the number 102. Components in FIGS. 5 and 6 that 
correspond to components in FIGS. 1-4 are similarly numbered but with the 
addition of prime marks thereto for convenient identification purposes. 
In system 101, lubricating oil that has drained and collected as in FIG. 1 
in a conventional engine oil pan (not shown) is withdrawn by a 
conventional oil pump (not shown) and enters interconnecting conduit 31' 
as shown in FIG. 1. 
Oil in conduit 31' is delivered to apparatus 102 as shown in FIG. 5. 
Apparatus 102 is here generally the same as shown in FIG. 3 but is further 
associated with a cooperating adapter plate 103. 
Oil in conduit 31' enters plate (or block) 38', as shown in FIG. 5, passes 
through channel 41' through bore 52' and into channel 104 in plate 103. 
The lower face of plate 103 is threadedly associated at aperture 111 with 
outer circumferential threads 43A' of stud 43'. A compression fitting 112 
threadably engages plate 103 at the mouth of channel or bore 104 so than 
an associated conduit 106 receives the entering oil from conduit 31' and 
conveys this oil to filter assembly 96. The base of assembly 96 comprises 
a manifold structure 99 that is preferably comprised of cast and machined 
metal. In manifold structure 99, channel means is provided by which the 
input oil from conduit 106 is fed in separate streams to the filters 97 
and 98. One such stream is fed through each of two threaded studs 107 and 
108 upstanding from manifold structure 99 into the filters 97 and 98 that 
are associated therewith. Oil entering each filter 97 and 98 is filtered 
and then drains down from each filter first into a collection sump 113 
that is similar in function to sump 87. From each such sump, the filtered 
oil is collected and enters into return conduit 109 through which the 
filtered oil is returned to the mouth of the input bore 111 of plate 103. 
Conduit 109 is here threadably connected to the mouth of aperture or bore 
111 by a compression fitting 114. In bore 111, the filtered input oil 
drains down through the channels 58' onto the central region of heated 
dome 64' thereby forming a thin film of oil from which volatiles are 
separated. 
The manifold structure 99 is formed with an integral bracket structure 112 
which enables the assembled oil filter assembly 96 to be mounted to a 
firewall or the like in a vehicle (not shown) adjacent to the apparatus 
102. 
For ease in use, each opposing end of the manifold 99 is provided with an 
input port 116 and an output port 117 (see FIG. 10) for ease of use in 
connecting manifold 99 with conduits 106 and 109. Only one pair of ports 
116 and 117 is used in a given installation with each of the non-used 
ports being closed by a threaded plug (not detailed). 
In the practice of the process of the present invention, it is found to be 
desirable and preferably for oil that is being reconditioned to be 
filtered to an extent sufficient to separate therefrom substantially all 
particulates above a particle size in the range of about 1 to about 5 
microns. Since conventional typical full-flow oil filters are understood 
to remove particulates above about 40 microns, and since conventional 
typical by-pass oil filters are understood to remove particulates above 
about 10 to about 15 microns, conventional vehicular oil filters are not 
used for achieving such preferred filtration. Also, conventionally used 
oil flow rates through oil filters are typically understood to be above 
about 20 gallons per hour which is believed to be excessive for purposes 
of achieving particulate filtering down to a particle size in the range of 
about 1 to about 5 microns. For such preferred purposes, oil flow rates 
through an oil reconditioning system of this invention in the range of 
about 4 to about 10 gallons per hour are presently preferred. Higher flow 
rates do not result in the desired filtration of all particles larger than 
about 5 microns while lower flow rates apparently not only appear to be 
impractical, but also appear to interfere with the achievement of 
desirable residence times for oil flowing as a thin film upon surface 
portions of a domed platen in the platen assembly. 
Oil flow rates in the range of about 4 to about 10 gallons per hour are 
believed to be best when associated with average oil pressures that are 
preferably in the range of about 20 to about 110 psi and more preferably 
in the range of about 25 to about 100 psi. Higher oil pressures are 
believed to be generally undesirable since they usually require use of a 
pressure reducing valve and can lead to pressure problems in the platen 
assembly, such as in the chamber over the platen. Lower oil pressures are 
generally impractical for usage in a system of this invention. 
As those skilled in the art will readily appreciate, various filter 
structures are known and are available commercially which will function to 
filter engine oil to remove therefrom particles down to the desired 
particle size of about 1 to about 5 microns. One presently preferred 
filter structure is available commercially from Parker Hannifin Corp., 
Raycore Div., Modesto, Calif. as its filter assembly Model No. LFS-801 or 
LFS-802. As shown, illustratively, for example, in FIGS. 12-14, such a 
filter assembly structure 121 incorporates a relatively large housing body 
122 with elongated, generally cylindrically configured sides 123 and with 
an integrally formed closed terminal end 124. The body 122 is comprised of 
a cast metal, such as an aluminum alloy or the like. The opposite or open 
end 124 of body 122 is flared and is interiorly circumferentially threaded 
for mating engagement with a exteriorly circumferentially threaded cap 
126. Locations on diametrically opposite sides of the cap 126 each have 
pivotably mounted thereto a different one of a pair of projecting legs 127 
of a flattened U-shaped bracket 128 by means of adjustable bolt assemblies 
129. The bracket 128 has a leg interconnecting flattened base 131 which 
provides a surface that is suitable for mounting the filter assembly 121 
to a firewall or the like in an engine compartment of a vehicle. 
The cap 126 is additionally provided with an oil input orifice 132 and an 
oil output orifice 133 as shown illustratively in FIG. 12. The input 
orifice 132 is directly and exteriorly connected to a metering jet 134 
that is threadably associated with the oil input orifice 132. The output 
orifice 133 connects threadably with an elbow 136 that is associated with 
a conduct 137 (which corresponds to the conduit 31 in FIG. 1) that conveys 
filtered oil from the filter assembly structure 121 to the vaporizer or 
platen assembly 102 (see, for example, FIG. 6). The filter assembly 
structure 121 thus is adapted to replace the two-component filter assembly 
96 as shown in FIG. 5 and FIGS. 9-11. 
The filter element 138 of the filter assembly structure 121 is generally 
cylindrically configured with an axial channel 139 extending therethrough. 
The filter element 138 is preferably comprised of a computer-controlled 
winding of cotton thread or roving, or the like. Owing to progressive and 
computer directed changes in weave and in tension of overlapping roving, 
the wound layers of roving become progressively more porous with 
increasing radial distance from the axial or core channel 139 of the 
filter element 138. Thus, the wound roving in a layer-like region 141 that 
is adjacent to the axially extending channel 139 of the filter element 138 
is characterized by a capacity to pass therethrough particles having a 
particle size that is less than about 5 microns. 
From one to four or even more additional radially adjacent layer-like 
regions or stages are successively and adjacently formed over the 
innermost axially adjacent layer such as layer-like regions 142, 143, 144 
and 145 of filter element 138 as illustratively shown in the 
cross-sectional diagrammatic view shown in FIG. 14. Each successive one of 
the layer-like regions 142, 143, 144 and 145, as the distance from the 
filter element core channel 139 increases, is wound so that it removes 
particles that are larger than those which are passable through the next 
adjacent radially inner layer. 
For example, suitable and illustrative four and five layered and 
progressive filter elements, such as filter element 138, proceeding from 
largest filterable particles radially inwards to the axial channel 139 can 
be utilized to remove particles. Illustrative progressive reductions in 
particle sizes removed as oil flows radially inwardly from the outer 
surface of filter element 138 inwards to the axial channel 139 for several 
representative filter elements 138 are shown in Table I below. 
TABLE I 
______________________________________ 
Filter Element Stages 
FILTER ELEMENT REMOVES TICLES 
STAGE IN SPECIFIED STAGE LAYER DOWN 
LAYER NO. TO SPECIFIED APPROXIMATE SIZE 
FROM MICRON RANGE 
OUTSIDE IN 
3 stage layer 
4 stage layer 
5 stage layer 
______________________________________ 
1 about 15 to about 15 to about 35 to 
about 30 
about 30 
about 40 
2 about 8 to 
about 8 to 
about 20 to 
about 12 
about 15 
about 35 
3 about 1 to 
about 8 to 
about 10 to 
about 3 
about 15* 
about 20 
4 about 1 to 
about 5 to 
about 5 
about 10 
5 about 1 to 
about 
______________________________________ 
5 
The filter element 138 is inserted into the body 122. The lower end of the 
axial channel 139 seats over a dimple 147 formed centrally in closed end 
124. As so seated, a circumferential spacing 148 exists between outer 
circumferential surface portions of the filter element 138, and inside 
surface portions of the cylindrical sides 123. The upper end of the filter 
element 138 is received restably and matingly into interior portions of 
the cap 126 so that, when the cap 126 is threadably fully engaged with 
flared upper end portions of the cylindrical sides 123, the upper end of 
this filter element 138 is sealingly and abuttingly engaged with adjacent 
surface portions of the cap 126. 
The input orifice in cap 126 connects with the circumferential spacing 148 
and the output orifice connects with the axial channel 139. As indicated 
by the arrows provided in FIG. 12, oil input through input orifice 132 
enters into the circumferential spacing 148, flows radially through the 
filter element 138, enters into the axial channel 139 and is output 
through the output orifice 133. 
The preferred oil flow rates and oil pressures (indicated above) can be 
achieved for oil being charged to a suitable oil filter element in filter 
assembly structure 121 by threadably (or otherwise) associating a suitable 
conventional metering orifice (or so called "metering jet") 134 with the 
cap 126 input orifice 132 and threadably associating the outside end 
portion of the jet 134 with the conduit 137 that delivers the oil to the 
metering jet 134. The orifice size of such a metering jet 134 can vary, 
depending upon such variables as the oil pressure associated with the 
output stream from the associated engine oil pump and/or the total volume 
or flow rate of engine oil being pumped by the associated engine oil pump. 
For typical engine sizes, a metering jet 134 orifice diameter size in the 
range of about 0.025 to about 0.04 inch appears to be suitable with a 
metering orifice diameter size of about 0.031 inch apparently being a 
generally useful size and therefore is presently preferred. 
One of the desirable characteristics of such a progressively staged filter 
element 138 is that it eliminates the effect known as "plugging" or 
"loading", such as occurs with a corresponding prior art filter element 
having only a single range of particle filtering capacity. As soon as 
outer porous portions of that type of filter element become contaminated 
or filled with particles, the filter element becomes ineffective for 
filtering further particles. 
Another desirable characteristic of such a progressively staged filter 
element 138 is that it eliminates the effect known as "channeling" where 
oil under pressure in a filter tends to seek and follow paths of least 
resistance. Such paths are associated with little or no filtering. 
It is believed that charging to the platen assembly a filtered oil feed 
stock wherein the particle size is not above about 5 microns results in 
surprisingly better removal of volatiles from the oil being reconditioned 
in the inventive system compared to a comparable oil feedstock is filtered 
with conventional oil filters of the types such as above indicated. 
It is preferred for a filter assembly structure 121 to have a relatively 
large volume and a relatively large filter element 138. Thus the oil flow 
rate and pressure measured at each of the respective input and output 
locations of the filter can fall into the respective ranges above 
indicated. However, in the filter assembly structure 121, oil flow rate 
and oil pressure are reduced owing to the structure 121 volume and the 
size of filter element 138, thereby to enhance the effectiveness of the 
oil filtering and effectuate desired removal of particulates. Because of 
the size and the performance characteristics of such a filter assembly 
structure 121, separate but preferably adjacently located respective 
housings for the filter assembly and the platen assembly, as illustrated 
for example, in FIGS. 15 and 16 are presently desirable. 
Platen assembly apparatus variables, such as, for example, the domed 
configured platen size or configuration, or the size of the chamber over 
the platen, are somewhat limited by the practical considerations of 
available space in an engine compartment, as those skilled in the art will 
readily appreciate. It is presently convenient and preferred to employ a 
platen which is symmetrically configured relative to a vertically 
extending axis. Preferably, the platen has a diameter that is in the range 
of about 3 to about 9 inches although various platen configurations and 
sizes can be employed. 
An alternative embodiment of a platen assembly 149 that is now believed to 
be well suited for use with functional combination with a filter assembly 
structure 121 in the practice of this invention is illustrated in FIGS. 15 
and 16. A filter assembly structure 121 is shown in phantom in FIGS. 15 
and 16. The platen assembly 149 incorporates a preferably and generally 
cylindrically configured housing 151 that includes a cylindrically 
configured outside side wall 152 and an integrally formed bottom platform 
153 that extends diametrically across the lower end of side wall 152. An 
interior shoulder 154 circumferentially extends around the inside of the 
side wall 152 and defines an interior edge surface upon which perimeter 
adjacent portions of a domed platen 165 can seat and thereby support the 
platen 165 in upwardly spaced relationship relative to the bottom platform 
153. Machine screws or the like (not detailed) mount the platen 154 edge 
portions to the edge of the shoulder 154. 
The domed platen 154 is here illustratively but preferably comprised of a 
formed steel plate, the forming being accomplished by die pressing or the 
like. The under surface of this platen 154 has fixed thereto by adhesive 
or the like (not detailed) by a conventional thermostatically controlled 
electrical element 155. The thermostatic control can be variously located; 
for example it can be located in chamber 161B adjacent to the side wall 
152. 
In effect, the platen 154 divides the housing 151 into an upper chamber 
161A and a lower chamber 161B. A circularly sided cover plate 156 extends 
across and rests against the upper end portions of the side wall 152. A 
plurality of circumferentially spaced, hex-headed machine bolts 157 or the 
like extend through perimeter portions of plate 56 and threadably matingly 
engage threaded sockets formed in the upper end portions of the sidewall 
152. A sealing gasket (not shown) may be positioned between the upper end 
portions of the side wall 152 and the plate 156. 
A central (preferably axial) bore through plate 156 is here threadably 
engaged with a metering jet 158. A conduit 159 interconnects the metering 
jet 158 with the elbow 136 associated with filter assembly structure 121 
so that filtered oil from the output orifice 133 of the filter assembly 
structure 121 is conveyed to and input into the upper central portion of 
the platen assembly 149. The metering jet 158 is preferably adapted to 
output therefrom all the oil fed thereinto and therethrough as a spray 
which is discharged into the chamber 161 in housing 151 preferably over 
the apex of the platen 165. The entering oil is fed downwardly in upper 
chamber 161 preferably axially (relative to platen assembly 149) from the 
end or terminal nozzle of the metering jet 158. The oil spray need not but 
preferably does has a conical pattern that is aligned with the central 
(preferably axial) apex region of the domed platen 165. Spray charging in 
a conically shaped pattern such as shown in FIG. 16 is believed to enhance 
and maximize the surface area of the filtered oil charged into the platen 
chamber 161A. At present, it is convenient and preferred for the diameter 
of the spray cone base at the location where the cone base reaches the 
platen 165 surface to be less than about 3 inches, but other such 
diameters can be used. if desired. 
Oil entering the chamber 161 from metering jet 158 is preferably deposited 
on the upper surface of the apex region of the domed platen 154 and forms 
a thin film (not shown) on platen 154 which flows by gravity downwardly 
and outwardly over upper surface portions of the platen 165 upper surfaces 
to the lower outer terminal peripheral side regions of the platen 165. 
From there, the oil flows through a plurality of circumferentially spaced 
apertures 166 in peripheral side regions of the platen 165 adjacent to the 
shoulder 154 and moves into lower chamber 161B. In chamber 161B, the oil 
flows by gravity downwards onto the interior upper surfaces of the bottom 
platform 153 which surfaces are conically tapered so that the oil flows to 
a central (preferably axial) exit port 167. A connecting sleeve 168 of the 
like is threadably associated with port 167 and external portions of the 
sleeve 168 are threadably connected with a conduit 164. Various 
arrangements can be used to join the exit port 167 with to conduit 164, as 
those skilled in the art will appreciate. The conduit 164 conveys the 
reconditioned oil back to the associated engine; a present preference 
being to charge this oil into the oil pan of the engine (not detailed). 
Although the platen 165 in the platen assembly 149 is preferably uniformly 
heated to a selected temperature in the range of about 180.degree. to 
about 190.degree. F. during operation, platen temperatures generally in 
the range of about 160.degree. to about 200.degree. F. are believed to be 
effective and useful in separating volatiles from contaminated entering 
oil. The chamber 161A over the platen 165, which for convenience can be 
termed herein the platen chamber, is itself heated by the adjacent platen 
165. However, if desired, the side wall 152 and the bottom platform 153 
can be heated, preferably electrically (not shown). 
One preferred configuration for the domed platen 165, as above indicated, 
is spherical, more preferably hemispherical. 
However, in the practice of the presently preferred process of this 
invention, and particularly when a staged filter assembly is being 
employed for oil filtering as above described, the domed platen 165 can 
incorporate certain modifications. For example, the domed platen 165 can 
advantageously incorporate a plurality of radially spaced, concentric, 
ridge-like elevations 162 upon and in its upper surface portions. Each 
elevation 162 has a small height relative to radially adjacent upper 
higher surface portions. Thus, a thin film of oil flowing radially 
downwardly over the platen 165 upper surfaces preferably experiences at 
least two cycles of alternately being thickened and thinned before 
reaching the lower outer perimeter of the platen 165. The ridge-like 
elevations 162 are believe to enhance oil reconditioning by functioning to 
increase the opportunities for volatiles to be separated from oil being 
reconditioned while the oil is in contacting relationship with the platen 
165 as a thin film. 
Under the normal range of operating conditions of an associated internal 
combustion engine, it is convenient to continuously return separated 
volatiles from the platen chamber 161A to the manifold of the associated 
engine from a volatiles outlet 169 that is preferably located in an upper 
medial portion of platen chamber 161A, here preferably in the cover plate 
156. Illustratively, a bore through cover plate 156 is provided in 
adjacent but spaced relationship to the metering jet 158; this bore is 
threadably associated with an elbow 163. In turn, elbow 163 connects with 
a conduit 171 which preferably conveys vapors volatilized from the oil 
being reconditioned to the manifold of the associated engine. 
To enhance separation of processed (i.e., reconditioned) oil from 
volatilized vapors in the chamber 161A, it is now preferred to have the 
processed oil that reaches the lower outside perimeter region of the 
platen 154 flow downwardly and diagonally to a central collection zone or 
sump located centrally below the platen 165 (as above described) to the 
return conduit 164. Such an oil collection procedure minimizes oil 
collection time and exposure to elevated temperatures. 
During operation of the platen assembly 149 under a normal range of engine 
operating conditions, pressures in the platen chamber remain typically 
within a range and at a level which avoids volatilized vapors entering the 
oil return conduit 164. However, should the gas pressure in platen chamber 
161A gas rise above a selected set point pressure, then a conventional 
vent valve (not shown in FIGS. 15 and 16) is provided that can be 
associated with elbow 163 and that opens to release pressure in the platen 
chamber 161A. When the gas pressure falls below a set point pressure, the 
vent valve closes. 
Particularly under start up and initial (cold engine) operating conditions, 
and under certain other engine operating conditions and situations, when 
volatiles tend to collect in engine oil, the platen chamber 161A can be if 
desired, regulated so as to be continuously vented and maintained at 
ambient atmospheric pressures by means of process controls (conventional, 
not detailed) that are associated with the vent valve, thereby to maintain 
the platen chamber 161A at ambient (atmospheric) pressure at such 
operating conditions. By maintaining atmospheric pressure in the platen 
chamber 161A, a maximum pressure differential is achieved between the 
pressure of oil entering the platen chamber 161A and the platen chamber 
161A pressure. Such a maximized pressure differential is believed to 
enhance and maximize the removal of volatiles from oil being processed in 
the platen assembly. 
The filtered oil that enters the platen assembly 149 from the filter 
assembly 121 is first charged into the platen chamber 161A. The location 
of oil charging or entry into chamber 161A is preferably above and in 
vertically spaced relationship to the upper central apex surface region of 
the doomed platen 165. Since, as above indicated, the entering filtered 
oil is preferably and typically pressurized to a pressure that is in the 
range of about 25 to about 100 psig as charged to the platen chamber 161A, 
this so-charged oil experiences an immediate pressure drop upon entry into 
chamber 161A. Resultingly, at least some of the volatiles in the entering 
filtered oil are believed to be immediately evaporated or vaporized 
therefrom in the platen chamber 161A. Thus, the vaporization occurs both 
before and during contract of the filtered oil as a thin film with the 
platen 165 surface regions in chamber 161A. 
The platen assembly 149, as those skilled in the art will readily 
appreciate, can be variously configured. The total volume of the platen 
chamber 161A and the spacing in the platen chamber 161A between the 
nearest location(s) of entry of the filtered oil into chamber 161A over 
the upper central apex surface region of the platen 165 can be fixed and 
selected before or during the fabrication of the platen assembly 149. At 
present, in the platen chamber 161A, a spacing distance between the 
location of entry of filtered oil and the upper central surface apex 
region of the platen 165 is preferably and conveniently in the range of 
about 0.5 to about 1 inch, but other spacing distances can be used, if 
desired. 
As above indicated, to enhance removal of volatiles from filtered oil in 
the platen chamber, it is now preferred to charge the filtered oil to the 
platen chamber as a spray. 
Other and further equivalent embodiments and variations will be apparent to 
those skilled in the art without departing from the spirit and scope of 
this invention.