MXPA01003962A - Centrifuge cartridge for removing soot from oil in vehicle engine applications - Google Patents

Abstract

A centrifuge oil filter (52) for removing soot from oil in engines includes a centrifuge filter housing (54) and a replaceable centrifuge cartridge body (74). The top of the housing (54) includes a removable lid (60). The upper end of the body (74) is supported for rotation by a drive shaft (90), the upper end of the drive shaft (90) supporting a turbine (100). In the bottom of the housing is a centrifuge cartridge body lid (88) including a centrifuge hub (174), below the lid (88) is a housing bottom lid (62) including a set of bearings (94). The body (74) has a large surface area containmenttrap (114) which has several levels provided by concentric cylindrical walls and a plurality of partition walls in each level to provide for multiple compartment for soot agglomeration.

Description

CENTRIFUGE CARTRIDGE TO REMOVE FUEL HOLLIN LIQUID FOR APPLICATIONS OF VEHICLE ENGINES Field of the Invention The present invention relates generally to filters and more particularly relates to oil filters for motor and vehicle applications.

BACKGROUND OF THE INVENTION Currently heavy-duty diesel engines place a moderate amount of soot (in the form of unburnt fuel) in the oil pan. This soot is generated because the fuel collides with the walls of the cold cylinder and is then released to the oil collector when the pistons oscillate in the cylinders. Until recently, nitrous oxide emission regulations in the United States and other countries had been high enough, so that fuel injection timing could be such that the level of soot generated was not high. In typical applications, the level of soot would be less than 1% (by weight) of the engine oil at the time of draining the oil. At those low levels, the soot in the oil does not cause any wear problem.

Recently, there has been a movement towards significantly lower nitrous oxide emissions, which requires a much more delayed fuel injection timing, which significantly increases the amount of soot that is generated. At reasonable oil drain intervals, the soot level can be as high as 4 or 5% with a delayed injection timing. When the level of soot becomes high, the lubrication at critical wear points of the engine becomes poor resulting in high wear, decreasing the kilometers for a repair and causing high expenses to the operator. In this way, the engine manufacturer has two choices, suffer high warranty costs and low mileage before repair, or significantly decrease oil drain intervals to maintain high levels of soot out of the oil. None of these choices is desirable, since there is a strong need to have means to keep the soot out of the oil, which is the objective of this invention. A problem with soot removal from oil is that it is very small in size - around 0.1 to 2.0 micrometers. To remove such small particles from it, the use of a filtration barrier is feasible due to the large filter size required and the very high probability that the filter will clog very quickly because it tries to filter such a fine level. A feasible way to remove the soot from the oil is through the use of a centrifuge, a device that removes the soot from the oil using centrifugal force. This type of device is used to separate blood constituents from the blood and has many applications in typical laboratory applications. The use of a centrifuge for an engine entails the requirement to do this in a very cheap and reliable way with the centrifuge being easily changed at the time of oil change. So far, the centrifugal filters have not been able to remove enough soot from the oil, sufficiently retain the soot, and be reliable enough to be used in motor and vehicle applications.

Brief Description of the Invention Therefore, the general purpose of the present invention is to provide a highly practical and reliable filter for removing soot from oil in vehicle and engine applications to maintain or prolong the drain intervals at which the oil should be replaced the engine.

In accordance with these and other objects, the present invention is directed toward a centrifugal cartridge which can rotate at high speeds in a stationary drive housing to remove soot from the oil in the filter chamber or cartridge. The centrifugal cartridge generally has an external housing having a predetermined axis of rotation. There are several aspects of the centrifugal cartridge, which provide each one with high practicality and reliability. One aspect is the provision of a separate filtration trap in the filter chamber to provide a greater soot retention capacity. The soot trap has multiple levels located at different radial distances from the rotational shaft so that the oil flows through it before the oil can leave the cartridge. Each level has an outlet opening to allow the oil to pass to the next level and a reservoir area which is located radially outside the outlet opening to filter heavier particles such as oil soot. The different levels can be provided by multiple concentric cylindrical walls, conical walls, a single sheet wound in a spiral configuration, or other appropriate configuration.

Another aspect of the present invention is the provision of a centrifugal cartridge, which has an inlet in its upper part and an outlet in its lower part. An outlet duct is provided in the centrifugal cartridge which extends the inlet of the outlet to the top of the filter cartridge. The outlet duct ensures that the oil does not drain when the cartridge is free. The lower outlet prevents the oil from creating drag on the cartridge rotation and also keeps the cartridge clean, which in turn makes it easier for the cleaner to maintain service when the filter cartridges are changed. Another aspect of the present invention is the provision of a beveled or conical contact surface which allows the cartridge to be precisely aligned and retained when inserted into the intended stationary drive housing. Another aspect of the present invention is the provision of a lateral oil inlet located radially outwardly of the central axis of rotation. This allows a support member of the intended drive housing to extend through the cartridge without the need to introduce oil through the support member. The objects and advantages of the invention will become more apparent from the following detailed description when taken in conjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIGURE 1 is a sectional view of a first embodiment of the present invention with the centrifuge installed in the filter housing. FIGURE 2 is a sectional view of the housing without the centrifuge installed. FIGURE 3 is a sectional view, in perspective, of the first embodiment of the present invention. FIGURE 4 is a sectional view of the centrifuge body. FIGURE 5 is a top view of the centrifuge body. FIGURE 6 is a sectional view of the lid of the centrifuge body. FIGURE 7 is a front view of a first embodiment of the filter housing. FIGURE 8 is a sectional view of FIGURE 7 taken along line 8-8. FIGURE 9 is a left side view of FIGURE 7.

FIGURE 10 is a sectional view of the lower cover of the housing. FIGURE 11 is a sectional view of the upper cover of the housing. FIGURE 12 is a sectional view of the turbine shaft. FIGURE 13 is a top view of the hexagonal drive. FIGURE 14 is a sectional view of FIGURE 13 taken along line 14-14. FIGURE 15 is a plan view of the means of the containment trap. FIGURE 16 is a side view of FIGURE 15. FIGURE 17 is an enlarged sectional view in area 17 of FIGURE 16. FIGURES 18 and 19 are sectional views of another embodiment of the present invention, wherein FIGURE 16 is a sectional view of FIG. 18 shows the filter housing. FIGURE 19 is a sectional view of the centrifugal cartridge for installation in the filter housing of FIGURE 18. FIGURE 20 is the same sectional view of the cartridge of FIGURE 19 inserted into the housing of FIGURE 18, shown in FIG. operation with flow lines indicating the flow path of oil through al. Centrifugal cartridge containment trap. FIGURE 21 is a sectional view of another embodiment of the present invention. FIGURE 22 is the same sectional view of the FIGURE 21, but showing the support flanges and position of the nozzle of the upper part and the lower part. FIGURE 23 is a sectional view of another embodiment of the present invention with the centrifugal cartridge installed in the filter housing. FIGURE 24 is a sectional view of FIGURE 23 taken along line A-A FIGURE 25 is the same sectional view of FIGURE 23 without the centrifugal cartridge installed. . FIGURE 26 is a sectional view of another embodiment of the present invention in which the stationary filter housing is the same as that of FIGURE 25., but the centrifugal cartridge is different from that of FIGURE 23. FIGURES 27-30 are alternative embodiments of a filter cartridge according to the invention, illustrated in association with the actuator arrow of the filter. FIGURE 31 is a sectional view of another embodiment according to the present invention. FIGURE 32 is a sectional view of another embodiment according to the present invention. FIGURE 33 is a top view of the deflection plate for the centrifugal cartridge of the embodiment shown in FIGURE 32. FIGURE 34 is a cross-sectional view of a centrifugal oil filter including a centrifuge housing and a centrifugal cartridge replaceable according to the preferred embodiment of the present invention. FIGURE 35 is a cross-sectional view of the centrifugal housing shown in FIGURE 34. FIGURE 36 is a cross-sectional view of the replaceable centrifugal cartridge illustrated in FIGURE 34. FIGURES 37 and 38 are top and bottom perspective views of FIG. the containment trap of the replaceable centrifugal cartridge illustrated in FIGURE 36. FIGURES 39 and 40 are perspective views of an outer coating used in the filter housing of FIGURE 35. FIGURE 41 is a top view of an insulator of vibration located in the housing of FIGURE 35. FIGURE 42 is a perspective view of the outer tubular member used in the cartridge of FIGURE 36. FIGURE 43 is a top end view of the containment trap illustrated in FIGURES 37 and 38. FIGURE 44 is a cross section of FIGURE 43 taken around line 11-11. FIGURE 45 is a schematic flow diagram illustrating oil flow through the containment trap of FIGURES 37 and 38. FIGURE 46 is a cross-sectional view of a portion of a centrifugal filter similar to that illustrated in FIGURE 34 but with a thermal expansion and contraction mechanism according to another embodiment of the present invention. FIGURE 47 is a top view of a preferred embodiment including a centrifugal housing of a centrifugal cartridge inserted therein, in accordance with a preferred embodiment of the present invention. FIGURE 48 is a side view of the centrifugal filter illustrated in FIGURE 47. FIGURE 49 is a cross section of the centrifugal filter shown in FIGURE 47, taken around line 49-49. FIGURES 50-53 are sections of the centrifugal filter shown in FIGURE 47 taken around lines 50-50, 51-51, 52-52 and 53-53, respectively. FIGURES 54-60 are perspective views of the individual components of the centrifugal cartridge shown in FIGURE 59. FIGURE 61 is a section of the centrifugal filter of FIGURE 47 taken around line 61-61, with the centrifugal cartridge removed. FIGURE 62 is a section of FIGURE 48 taken around line 62-62, with the centrifugal cartridge removed. FIGURES 63-70 are perspective views of the different components of the detrimental housing shown in FIGURE 61. FIGURES 71-73 are illustrations of a conical wall trap embodiment illustrating partition walls between levels. Although the invention will be described in connection with certain preferred embodiments, it is not intended to limit this to those embodiments. On the contrary, it is intended to cover all alternatives, modifications and equivalent included within the spirit and scope of the invention as defined by the appended claims.

Detailed Description of the Preferred Modality Referring now to the drawings, FIGURES 1-46 illustrate various embodiments of the present invention, which demonstrate certain workable concepts for a successful centrifugal filter. The currently preferred embodiment incorporates many of the concepts of the modalities shown in FIGURES 1-46 shown in FIGS. 47-70 and will be described later in greater detail. As discussed above, the present invention is primarily directed toward use in conjunction with engines, particularly diesel engines, and oil filtration thereof. In addition to having use as a filter to remove soot from the oil, the filter of the present invention can also be used or adapted to other industrial applications where a high speed centrifugal filter is desired. The present invention therefore provides a filter, which is inexpensive to manufacture, resistant, which reaches high speeds, and which is itself endowed with easy maintenance. Among other things, the present invention is directed to the unique characteristics of the centrifugal housing, the replaceable centrifugal cartridge, the containment trap in the centrifugal cartridge, the mechanical drive devices, the method for manufacturing the filter, the method for removing soot from the oil, and the method to allow the centrifugal body to be easily removable and replaced. The present invention is directed towards individual components such as the replaceable centrifugal cartridge and the stationary housing and also to the combination of the centrifugal cartridge and the stationary housing and how the combination with a motor is used to separate soot from the oil in the preferred application. In accordance with those objects and with specific reference to Figure 1, the centrifugal filter 52 in a first embodiment includes an outer housing 54 having a substantially cylindrical shape with an upper end closed by a top cover of the removable housing 60, and a bottom closed by a lower cover of the removable housing 62, as will be discussed in more detail here. As can also be seen in Figure 1, as well as in Figures 2-3 and 7-8, the housing 54 includes mounting brackets 64 for joining a motor. Figures 7-9 also indicate that the housing 54 includes an oil inlet 66, an oil drain hole in the turbine 70, and a drain hole in the filter oil 68. It can be seen that within the housing 54, the body Centrifugal 74 is mounted to rotate. Centrifugal body 74 is typically made of plastic to facilitate its incineration and disposal. As best illustrated in FIGURE 5, the centrifugal body 74 includes a substantially cylindrical external wall 80 having stress-relieving flanges 82, and an upper end 86 with a hexagonal cavity 76. As will be discussed in more detail herein, the hexagonal cavity 76 interacts with a hexagonal actuator 106 for the purpose of rotating the centrifugal body 74. As shown in FIGS. 4 and 5, a plurality of oil outlets 78 are provided around the periphery of the hexagonal cavity 76. The outlets of Oil 78 provides a mechanism by which the filtered oil can be returned to the engine manifold in the direction indicated by the arrows 108 of FIGURE 1. The lower end 78 of the centrifugal body 74 is closed by the centrifugal cap 88. As shown better in FIGURE 1, the centrifugal body 74 includes threads 110 which are engaged with threads 112 on the centrifugal cap 88 to allow the cap 88 to be easily removed and attached to the centrifugal body 74 for installation and inspection of the containment trap 114 and / or the centrifugal body 74. This centrifugal cover can also be ultrasonically attached or bonded to the body. When mounted, it can be seen that the centrifugal cap 88 includes a bushing 116., which serves as a surface around which the centrifugal body 74 rotates. A ball bearing 94 is provided within the bottom cover of the housing 62 to support this rotation. It should also be noted from FIGURE 1 that the bottom cover of the housing 62 includes threads 118 which are adapted to engage the threads 120 provided in the housing 54 to allow the cover of the bottom portion of the housing 62 to be removed. An O-ring 96 is provided between the bottom cover of the housing 62 and the flange 122 of the housing 54 to prevent leakage. The upper end of the centrifugal body 74 is supported for rotation by the drive shaft 90. As shown in FIGS. 1 and 12, the drive shaft 90 includes an upper end 12 which is adapted to support the turbine 100. more specifically, a projection 128 is provided below the upper end 124 to support the turbine 100. The lower end 130 of the drive shaft 90 includes threads 132, which are adapted to be coupled to the hexagonal actuator 106, so that the rotation of the turbine 100 reduces the rotation of the drive shaft 90, which in turn causes the rotation of the hexagonal actuator 106, which in turn causes the rotation of the centrifugal body 74. Placing the turbine 100 on top of the filter 52, the centrifugal body 74 can be replaced from the bottom, creating a maintenance benefit, since such maintenance is typically performed from a pit below the l vehicle As shown in FIGURE 12, the lower end 130 is supported for rotation by first and second sets of slow-moving, angular contact ball riders 91 and 92 separated by the spacer 136. The ball bearings 91 and 92, as well as the separator 136 are, in the preferred embodiment, press fit into the cylindrical channel 138 of the housing 54. The channel 138 and the housing 54 are preferably manufactured from die-cast aluminum and the spacer 136 is preferably made of steel. The hexagonal actuator 106 is threaded on the drive shaft 90 strong enough to preload the bearings. An adhesive is used on the threads to keep the preload intact. The bearings 91 and 92 are held in place vertically by the retaining ring 140. The bearings receive the rotational force of the turbine, the actual light weight load of the moving part, and the heavy actual load and the processional forces ( gyroscope) generated as a result of vehicle movement. It is expected that the actual loads in the movement are light since the centrifuge is filled with oil and in this way will cushion the excessive movement. Since the bearings are permanent and reusable, the cost of engine maintenance is kept to a minimum. With respect to the hexagonal actuator 106, it is shown more specifically in FIGS. 13 and 14 as having a hexagonal shape adapted to complement the hexagonal force of the cavities 76 to securely couple the drive shaft 90 with the body. centrifugal 74, so that the rotation of the turbine 100 causes the centrifugal body 74 to rotate as well. The hexagonal actuator 106 includes an inner channel 142, which is in fluid communication with the inner channel 144 of the drive shaft 90 to allow the passage of the oil to be filtered. Therefore, after the filtered oil enters the housing 54 through the inlet 66, it hits the blades of the turbine 100 causing the turbine 100 to rotate. This, in turn, causes the centrifugal body 74 to rotate with a portion of the oil flowing through the channels 142 and 144 and towards the centrifugal body 74 through the tube 146. The pre-concentrated oil is intended to pass through the tube 146 , without preconcentrated oil by operating the turbine 100. The • pre-concentrated oil is oil treated to facilitate agglomeration of the soot into the oil into large particles. The tube 146 includes an upper end 150 which includes threads 152 for joining the upper cover of the housing 60 in the receiver 148. Therefore, 'when the lower cover of housing 62 is removed and ^) 10 the centrifugal body 74 is removed, the tube 146 remains attached to the housing 54 together with the turbine 100, the drive shaft 90 and the hexagonal actuator 106. After the oil passes through the turbine 146, the oil passes radially outwards to through containment trap 114, the structure of which will be described in more detail here. However, after passing through the containment trap 114, the oil soot will be retained within the containment trap and the filtered oil will pass through. towards the annular thrust chamber 154 between the containment trap 114 and the centrifugal body 74. The filtered oil will then pass upwards through the centrifugal body 74 and out of the body 74 in the direction indicated by the arrows 108 to the passageway. 156. In the passage 156 the filtered oil in the funnels then passes through the outlet 32 and returns to the engine. The passage 156 also serves for the purpose of preventing the used oil from crashing against the blades of the turbine 76 for damaging coupling with the centrifugal body 74 and thus slowing down the rotation speed. More specifically, after the oil hits the turbine 100, it can be observed that the oil is directed via the conical surface 158 of the housing 54 downwards towards the drainage holes 160. Alternatively, the oil can be drained directly of accommodation 54 through one side thereof. However, if the oil passes through the drain holes 160, it will flow down and may be collected by the passage 156. As indicated above, the passage 156 will direct the oil through an outlet in the housing. The passage 156 will therefore again protect the oil against contact and slowness of rotation speed of the centrifugal body 74. Therefore, it can be seen that the conical surface 158 and the passage 156 combine to serve as protection to prevent the shock oil against the turbine 100 comes into contact with the centrifugal body 74. With respect to the actual construction of the containment trap 114, it can be seen from FIGS. 15-17 that in the preferred embodiment of the present invention, the trap of containment 114 is comprised of a flat sheet 162 wound in a spiral pattern to provide multiple levels, which the oil must pass in a radially outward manner to clean the trap. The flat sheet 162 is preferably manufactured from Noryl GTX 626 plastic resin having a thickness of about 0.30"(0.762 cm) .The plastic is extruded and includes a plurality of depressions 164 which are formed vacuum in it. , as will be discussed hereinafter, which serve to collect the oil soot, with the ridges 166 between the depressions 164 containing oil outlets .168, which allow the oil to pass radially outwardly as the centrifuge rotates and allowing the Soot is collected within the depressions 164. To form the containment trap 114, the flat sheet 162 includes a plurality of spiral openings 170 which are adapted to be fixed to complementary projections on a rotating mandrel. (not shown). The mandrel is then rotated to allow the flat sheet 162 to be wound in a spiral pattern with the depressions extending radially outwardly, and therefore the ridges 166 extend radially inwardly when the flat sheet 162 is rolled up. The rotating mandrel is then removed and the centrifugal cap 88 is attached to the lower end of the containment trap 114. More specifically, the central hub 174 of the centrifugal cap 88 engages the central cylinder of the containment trap 114. The end cap 176 is then attached to the top of the containment trap 114 and the cap 176 includes an open center 174 on the which is sized to frictionally engage legs 180 extending downwardly from the hexagonal cavity 76 and thereby center the containment trap 114 within the centrifugal body 74. With specific reference to FIGURES 18 and 19, a second embodiment of the present invention is described generally as a centrifugal filter 252. Centrifugal filter 252 in this embodiment includes an outer housing 254 having a substantially cylindrical shape with an upper end 256 closed by an upper cover of the removable housing 260, and a lower end 258 closed by a lower cover of the removable housing 262. FIGURE 18 indicates that the housing 254 includes an external oil inlet hole 266, an oil drain hole of the turbine 270, and a filter oil drain hole 268. Although two outlet drain holes 270, 268 are shown in the present embodiment, an alternative embodiment may include a single outlet drain hole in which the expanded turbine oil and oil Filters are mixed to return to the engine's oil pan. As can be seen in FIGURE 18, housing 254 includes external mounting brackets 264 for attachment to a motor. The upper cover of the housing 260 is removably attached to the outer housing to allow inspection and maintenance of the internal components of the filter within the housing 454 near the upper end 256. In the present embodiment, threaded fasteners 310 attach the upper cover 260 to the outer housing 254. The upper cover of the housing 260 provides the oil inlet hole 266 for receiving engine oil, an axially extending annular flange 312 that is received closely by the internal cylindrical surface of the housing 254 and a portion of the central stem. extending axially inwardly 314. Edge 312 provides an annular groove 316 substantially sealed between two O-ring seals 297, 298 that communicate via a passage (not shown) with oil inlet hole 266 to receive pressurized engine oil. The annular groove 316 is connected to an axially extending passage 318 in the rod 314 via a transverse passage (not shown) for feeding oil to the housing 254. The upper cover of the housing 260 also supports a nozzle 320 communicating with the groove. annul 316 via a passage (not shown) to discharge and direct pressurized air. Bottom lid 262 includes threads 322 which engage with threads 324 of lower end 258 of housing 254 to allow cover 262 to be removed and easily attached for inspection, installation and replacement of centrifugal body 274. Bottom cover 262 preferably it includes guide projections 326 which pilot the threads of the cap 322 on the threads of the housing 324 during joining. An O-ring-shaped seal 296 is compressed between the lower cover 262 and the lower end 258 of the outer housing 254 to prevent leakage of the filter 252 and contaminants entering the filter. The outer housing 254 also includes a support floor 328 which generally divides the interior of the housing 254 into a turbine drive chamber 330 and a centrifuge chamber 284.

The support floor 328 includes three projections 332 that provide threaded holes 334. A window 336 fluidly connects the actuating chamber to the centrifugal chamber 284. The centrifugal body 274 is shown in FIG.

FIGURE 19 and is designed to be placed in the centrifuge chamber 284 as shown in FIGURE 20. Centrifugal body 274 is preferably made of plastic to facilitate incineration and removal. Centrifugal body 274 includes an externally slightly conical or substantially axially cylindrical 280 lateral wall which preferably angles slightly radially from the bottom to the top with a plurality of stress relieving flanges 282, and a trap chamber of the filter 338 positioned between the upper and lower closed ends 285, 287. The upper closed end 285 can be integrally connected with the side wall 280 and provides a central centrifugal inlet 276 and a plurality of centrifugal outlets 278 positioned radially around it. The lower closed end 287 is provided by the lower end cap 288 which is threadably engaged, is ultrasonically joined, or glued or otherwise bonded to the side wall 280. A seal 340 is preferably seated between the bottom end cap 288 and the side wall 280 to prevent contaminants from leaving the centrifugal body 274. A trap of containment 342 is placed in the trap chamber of the filter 338 to filter fluids such as the oil flowing from the centrifugal inlet 276 to the outlets 278. An actuating shaft 290 is mounted to rotate the housing 254 and is secured to the centrifuge body 274 to spin the body. The drive shaft 29 has an inclined upper surface with a central section of larger diameter 290a, and sections of progressively smaller diameter 290b, 290c at the upper end of the arrow 344 and sections of progressively smaller diameter 290d, 290e, 290f, 290g at the lower end of the arrow 346. The larger diameter portion 290a has a hexagonal external surface 328 which is received narrowly in the hexagonal openings 350, 352 at the upper and lower ends 285, 287 of the centrifugal body 274 for the radial retention of the centrifugal body 274 on the drive shaft 290. To provide an adjusted axial and radial retention in the case of the plastic centrifuge body 274, the hexagonal openings 350, 352 are recessed to the desired precision after the centrifugal body 274 is molded taking into consideration the different coefficients of thermal expansion of plastic and metal to the. The radial retention and the torsional transfer are provided by the hexagonal geometry of interengagement of the openings 350, 352 and the external hexagonal surface -348 of the larger diameter section 290a of the drive shaft 290. The axial retention is provided by a metal nut 354 having threads 356 which are threaded onto the corresponding threads 358 on the second smaller diameter section 290e of the driving shaft 290. The nut 354 engages an annular rim 360 on the centrifugal body 274 for pushing Centrifugal body 274 upwards. The centrifugal body 274 includes a radially inward cap 362 which fits tightly over the first smaller diameter portion 290d and engages the larger diameter portion 290a to resist the nut 354 and axially retain the centrifugal body 274 on the arrow Actuator 290. The centrifugal body preferably includes an elastic seal 364 seated in a groove 366 of the annular rim 360 and compressed between the nut 354 and the centrifugal body 274 to prevent leakage therebetween and to prevent the steel nut 354 from "loosening". "due to the vibration. The last smaller diameter section 290g of the drive shaft 290 includes a hexagonal periphery to allow the tools to hold and hold the drive shaft 290 when the steel nut 354 is being threaded onto and removed from the drive shaft 290. To retain the drive shaft 290 in the housing 254 and to permit rotation thereof, the filter 252 includes upper and lower bearing flanges 368, 370 or other bearing supports that interact with the upper and lower ends 344, 346 of the driving shaft 290. The lower bearing flanges 368 have a central bushing 372 and a plurality of radially extending legs 374. The legs 374 are connected to the lower cover 262 by elastic fasteners 376, elastic connectors. or other forms of vibration insulators to reduce or dampen vibrations or shock loads transmitted through them. In the preferred embodiment, each elastic fastener 376 includes a split threaded shaft 290 having one end threadably engaged with a projection 332 and another end threaded through a smooth opening or threaded on a leg 374 of the bearing flange 368. A piece of elastic rubber 434 or other resilient member is secured between the partition and surrounding the threaded shaft 290 and is compressed between the leg 374 and the projection 332. A nut and washer indicated in FIG. 342 hold the leg 374 by compressing the rubber part 434 to axially retain the bearing flange 368. The central hub 372 of the bearing flange 368 supports ball bearings 292 pressed into it which closely receives the third smaller diameter section 290. of the lower end 346 of the driving shaft 290 for the radial retention of the driving shaft 290. The outer race of the ball bearing 294 is secured between a clamp or snap ring 378 and a radially inward flange 381 of the bushing 372. The ball bearing 290 allows the arrow 290 to rotate relative to the flange 368. Likewise, the upper bearing * flange 370 has a central bushing 380 and a plurality of radially extending legs 382. The legs 382 are connected to the threaded projections 332 of the support floor 328 by means of resilient fasteners 384, elastic connectors or other vibration isolators. Elastic fasteners 384 also include a threaded shaft, a piece of rubber and a nut and washer and operate in the same manner as for the upper bearing flange 368. The central hub 380 supports ball bearings 294 placed therein under pressure narrowly the second smaller diameter section 290c of the upper end 344 of the drive shaft 290 for radial and axial retention of the drive shaft 290. The ball bearing 294 facilitates the rotation of the arrow 290 relative to the flange 370. The outer track of the ball bearings 294 is secured by a clamp or snap ring 386 and a radially inward flange 388 of the bushing 388. To provide axial retention, a nut 391 and a lock washer 392 threaded onto the threaded end 344 of the drive shaft 290 or other locking device engages with the inner race of the ball bearings 294 by pushing them against a sec larger diameter 290b of driving shaft 290. An advantage is that only two ball bearings 292, 294 are required in the preferred embodiment, which minimizes frictional losses because they allow higher rotational speeds of the centrifuge. An advantage is that the two ball bearings support the axial and radial loads of the arrow 290 and the centrifugal cartridge 274 during the operation, while allowing the centrifugal cartridge 274 to rotate at high speeds, preferably about 11,000-12,000. rpm to achieve a force of approximately 10,000 times the gravity. An advantage of the preferred embodiment is that the vibration isolators supporting the lower and upper bearing flanges 378, 370 cushion the ball bearings 292, 294 against vibrations induced by the vehicle, engine, or other source. By using the elastic fasteners 376, 384 as vibration isolators, the vibration is damped against the induction of undesirable radial and axial shock loads on the ball bearings. This increases the life span of the ball bearings 292, 294 and the filter 252. The rubber insulators also serve the desirable purpose of inhibiting the vibration and noise resulting from the rotating parts of the centrifugal housing 254, where large surfaces can amplify noise. The elastic nature of the elastic fasteners 376, 384 also provides for easier installation and replacement of the centrifugal filter cartridges. Without the lower cover 262 installed, the arrow 290 hangs from the upper flange 370 in a cantilevered manner. When the lower cover 262 and the lower bearing flange 368 slide over the drive shaft 290 the elastic nature of the upper rubber / steel fasteners 376, 384 tolerates small misalignments between the two ball bearings 292, 294 thereby facilitating , an easier installation. This also allows greater tolerances in the formation of various filter components, thereby lowering the costs of manufacturing and mounting the filter. The centrifugal body 274 and the drive shaft 290 can be driven by a turbine 300 that includes a plurality of blades driven by pressurized oil directed by the nozzle 320. However, in alternative embodiments, the drive shaft and the centrifugal filter can be driven by an air motor, an electric motor, mechanically from the motor, or by other suitable driving means. The turbine 300 is secured to the upper end 344 of the drive shaft 290 for transferring torque by means of a grooved or keyed connection (not shown), or by providing flat coupling surfaces between the arrow 290 and the turbine 300, or by any other acceptable coupling means. The turbine 300 is slidably positioned on the first smaller diameter section 290b of the upper end 344 of the drive shaft 290 and is axially retained by being sandwiched between the inner race of the upper ball bearing 294 and the larger diameter portion 290a of the drive shaft 290. The drive shaft 290 projects through a central opening 394 in the support floor 328 to connect the turbine 300 to the centrifuge body 274. The support floor 328 is generally in the shape of a bowl or outer side walls extending upwardly 296 and inner walls 398 near opening 394 to form a passage 400. During operation, passage 400 collects the oil that drives turbine 300 and returns the oil to the turbine's oil outlet orifice 270. Some of the oil that hits the turbine 300 splashes and is carried by the air, which advantageously produces an impregnated atmosphere with oil through the turbine chamber 330, which lubricates the upper ball bearings 294. The -atmosphere impregnated with oil is communicated through the hole 336 in the floor 328 to lubricate the lower ball bearing 292 as well. The turbine 300 preferably includes a screen or skirt 4 to prevent oil from leaving the turbine 300 and entering the central opening 394 and producing a slow torsional advance on the rotary drive shaft 290 and the centrifugal body 274 during operation. Turning to other features of the present invention, a radially extending flat or upper end cap 428 is positioned within the centrifugal body 274 in spaced relation to the upper end 285 of the body 274. The upper end cap 428 serves as a barrier to prevent the oil or fluid flows from the inlet exiting prematurely through the outlets 278. Radially extending ribs 440 molded at the upper end 285 or other separation means separate the upper end cap 428 from the upper end 285 to provide flow passages 432 from the inner periphery 275 of the centrifugal body 274 to the outlet 278. The end cap 428 has an outer diameter smaller than the inner diameter of the side wall 280 near the upper end 285 to provide flow openings 438 so that the cleaned centrifuged oil enter the passages 432. The. centrifugal containment trap 342 also acts as separation means for fixing the axial position of upper end cap 428. Centrifugal containment trap 342 includes a plurality of conical shaped trap walls 404 selectively arranged in centrifugal body 274 to trap particles Large, heavy contaminants in them. The lower lid 288 of the centrifugal body 274 includes a plurality of flanges 408 and channels 410 for receiving the respective lower ends 406 of the walls of the trap 404. The lower cover 288 preferably includes external cavities 412 for receiving a tool (not shown) as a spanner for screwing a lower cover 288 onto the centrifugal side wall 280. The inner top cover 428 also includes flanges 408 and channels 410 for receiving the respective upper ends 406 of the walls of the trap 404. The ends 406 of the walls of trap 404 are saturated with adhesive between adjacent ledges 408 in channels 410 otherwise fixed thereto. Each conical trap wall 404 is contained within another wall, and has an internal surface that is angled inward from top to bottom, or from bottom to top (alternatively), which directs oil radially inward before the Oil can move radially outward to the next outer wall. Thus, each conical wall provides a separate level to which the oil must pass to clean the trap. Exit slots 416 are provided near or at the point where adjacent walls 404 meet or connect. In the preferred embodiment, the angle of lateral inclination is approximately 1 degree, which provides a suitable angle for filtering soot from the oil. There are multiple walls 404 and the walls 404 are larger than the radius of the centrifugal body 274 to provide a displacement distance to include several times the radius of the centrifugal body 274, thus helping to provide a consistent, prolonged residence time, for the fluid to the containment trap 342. It is also seen in FIGURE 20 that each wall 404 facilitates the flow of oil mainly in an axial direction that is opposite to the direction of the anterior adjacent inner wall 404. As mentioned above, the centrifugal body has an inlet 276 and a plurality of outlets 278. In order to communicate fluid to the inlet 276, the arrow 290 includes a sleeve portion 418 of the upper end 344 that closely receives the shank 314 of the top cover of the housing 260 and a axially extending passage 420 connecting an inlet hole 422 of the stem of the cover 314 to the inlet 376 in the body nitrifuge 274. The drive shaft 290 provides radially outwardly extending passages 424 that drive the flow radially outwardly from the passages 420 to the centrifugal inlet 276 and to the centrifugal body 274 during operation. During rotation of the centrifugal body 274, the fluid flows radially inwardly along the inner surface of each wall of the trap 404 and then radially outward through an exit slot 416 to the next level or outer wall of the trap 404 as indicated by flow lines 426. When rotated, the centrifuge will contain oil equal to the diameter of the upper outlet slot 416 and outward, plus some extra oil in the conical trap closest to the centerline of unit. The heavier particles will migrate radially outwards along each conical wall 404 and will congregate and be trapped at the base of each conical wall 404 in the areas indicated by the letter S and the heavier particles will displace the now lighter particles towards the next radially outward wall 404. Therefore, the centrifugal body facilitates the communication or movement of lighter fluid, such as oil radially outward faster than fluid or heavier particles such as soot. Once the oil passes all the walls of the trap 404, it is collected in a collection chamber 430 between the wall of the uppermost trap and the side wall of the centrifugal body 280. The oil fills this chamber 430 and moves back towards inward towards the inner holes 278 where the centrifugal action ejects the oil centrifugally outwardly against the inner surface of the housing 254 where it flows by gravity along the inner surface of the lower end 258 of the housing 254 where it is collected and exits through the filtered oil outlet 368. Flowing mainly along the housing 254 and not the centrifugal body 274, the slow torsional advance is minimized. There are several advantages of the tapered containment trap 342. The innovative method of the present invention provides a centrifugal body 274 that is inherently balanced around the central axis (in contrast to the spiral configuration, which is inherently unbalanced and can increase its imbalance during the operation). The balance is achieved because the cross section of each wall 404 at each point along its axial length is a circle whose center is the axis on which the centrifuge 474 rotates. This reduces loads on the bearings and reduces creep and friction losses, thereby increasing the speed and effectiveness at which the filter can operate at a particular oil working power provided by the nozzle 320. The walls of the containment trap 404 can be easily formed from injection molded plastic. with little cost. In addition, the heavier and more polluting particles remain radially outward in the containment trap 342 and are less likely to move outward thereby reducing the possibility of escape, outward, which provides more effective filtration of the oil or other fluid. The innermost tube or wall 404 of the containment trap 342 is angled out from top to bottom, so that the oil flows by gravity and creates a downward moment towards the centrifugal body 274. When the device stops rotating, the substance in the centrifugal body 274 is contained on the inside of the unit, which prevents the substance inside the centrifuge from escaping during the removal of the centrifugal body for replacement with a new cartridge. In accordance with the objective of controlling the residence time of the fluid in the containment trap 342, the size of the inlet orifice 422 is controlled by restriction or otherwise selectively dimensioned between the inlet 266 and the inlet 276 the centrifugal body 274. For the preferred application of removing soot from oil in automotive applications, the objective is to dimension the inlet 422 or other restrictions, so that the flow rate to the centrifuge in gallons per minute (3.785 liters) is approximately one fifth to one tenth of the amount of oil (in gallons (liters)) contained in the centrifuge when it is spinning. In this embodiment the size of the oil inlet orifice 422 is approximately 0.009 inches (0.02286 cm) in diameter. This will give approximately five to ten minutes of residence time which is approximately the residence time required to centrifuge oil soot in diesel engine applications. The oil flow rate for the centrifuge separated from the oil flow through the nozzle 320 to the turbine 300 is much lower than the flow rate. To provide higher speeds, the nozzle is appropriately dimensioned and well machined to obtain a powerful well-contained flow directed in the turbine at an angle at a distance which provides a maximum speed for the centrifuge 274. The centrifuge can be adapted to rotate at high speeds. speeds of around 11,000 to 12,000 rpm. An alternative way to achieve these high speeds is to provide an electric motor, pneumatically driven motor or other suitable drive means to drive the centrifuge fast enough to separate the desired contaminants from the fluid. Another advantage of this preferred embodiment is the serviceability and serviceability of the filter 252. In addition to those serviceability advantages mentioned above, it should be noted that the arrow 290 is easily installed and removed simply by removing the clip 392 on the outer track of the upper bearing 294 so that the arrow 290, the upper bearing 294, or the turbine 300 can be easily installed or replaced if necessary. Similarly, the lower ball bearings 292 can be removed from the lower housing cover 262 by removing the clip 378 on the outer track. Alternatively, the arrow and all the parts joined together with the upper bearing flange can be provided as replacement parts of a single service. Those could be easily removed by removing the three nuts that hold the upper flange 382 to the vibration isolators 384, then the entire assembly could be pulled from the top of the unit. As mentioned, the centrifugal body 274 is inherently well balanced. Preferably, the centrifugal body 274 is more precisely balanced by mounting the centrifuge mounted on a balancing machine by means of shaft rotation (not shown) to the A and B levels. Off-balance conditions can be corrected by removing part of the flanges of plastic 408 on the lower cover 288 or by adding material in those areas. From the foregoing, it can therefore be seen that this embodiment of the present invention provides a novel and improved centrifugal filter for removing soot from engine oil. Through the unique structure of the present invention, the oil is adapted to drive a turbine to spin the centrifuge with an oil that strikes the turbine without interfering with the rotation of the centrifuge. In addition, the soot removed from the oil is contained within the containment trap and can not contaminate the filtered oil again. The centrifugal housing is adapted to be permanently attached to the motor and is provided by a mechanism whereby the centrifuge and containment trap can be easily removed for repair and replacement purposes. In addition, by manufacturing the polluting body of recyclable materials, the costs of manufacturing and replacement, as well as the impact on the environment, are minimized. Turning next to another embodiment described in FIGURES 21 and 22 it will be understood that the filter 452 has the same parts and operates much in the same manner as the first embodiment described in FIGS. 18-20, and therefore only the parts configured in a different way will be referred by reference characters and will be discussed later. A difference of the second embodiment is that there is a space 603 provided between the floor opening 590 and the drive shaft 490. A space 603 provides the arrow 490 with a range of motion to better accommodate vibration and prevent frictional losses. The screen or skirt 602 of the turbine 500 is bent outwardly at a greater angle to accommodate the larger opening 594. The alternative embodiment of FIGURE 18 also eliminates the way the seal 366 receives and the elastic rubber seal 364 replaces the latter. with a Belleville washer 564, spring washer or other elastic means that are compressed from the annular rim 560 of the centrifugal body 474 and the steel nut 554, which is threadably attached to the drive shaft 490. The Belleville washer 564 pushes the centrifugal body 474 up against the larger diameter section 490a of the drive shaft 490 to axially retain the position of the centrifugal body 474 on the drive shaft 490. Also shown in the alternative embodiment is the cover 488 of the housing centrifugal 474 having a slightly different configuration. More specifically, the end cap 488 is thicker in the axial plane, which deflects the ends 606 of the walls of the containment trap 604 axially inward toward the top of the filter 452. In addition to those differences already noted , this mode operates with much in the same way as the modality described in FIGURES 18-20. Turning then to the embodiment described in FIGURES 23, 24 and 25, it will be understood that the filter 452 has the same parts and operates much in the same manner as in the embodiments described in FIGS. 18-22 and therefore only the Differently configured parts and the different operation function will be noted and described below. Instead of using an oil driven turbine, the filter 652 of this mode uses an electric motor 700 and other driving means such as a motor for driving a centrifugal body or cartridge 674 within a stationary housing 654. The motor 700 is supported by the stationary housing 654, and is preferably supported by the upper multi-leg bearing support flange 770, through vibration isolators 834 to an internal support floor 728 of housing 654. Electric motor 700 is mounted inside the filter by external armature 846 secured by fasteners 848 to upper bearing support flange 770. Electric motor 700 includes an external housing 850 supporting a stator assembly 852 including motor windings. The armature 846 and the bearing flange 770 provide an outer annular cavity 854 which closely receives the motor housing 850 to support and secure the motor 700 both axially and radially. Mounted to rotate within the stator assembly 852 is a rotor 856 which comprises magnets which are secured to the upper end of the drive shaft 690, through hexagonal coupling surfaces, a grooved connection, or other connecting means. The drive shaft of the centrifuge 690 can also briefly stop the motor 700 and be connected to a motor shaft separated by a torque-transmitting device such as a hexagonal shaft. By providing an electric motor 700, the speed of the drive shaft 690 and the centrifugal cartridge 674 can be easily operated and controlled more precisely. The present embodiment also utilizes the two ball bearings to support the drive shaft 690, with the lower bearing assembly being of the same configuration as that of the embodiment of FIGS. 21-22. In this embodiment, the upper ball bearings 692 support a drive shaft 690 both axially and radially, but the configuration of the shoulder of the bearing 770 is modified to accommodate the electric motor 700. The ball bearings 692 are sandwiched between a portion of the ball bearings 692. larger diameter of the arrow 690 and a nut 840 and the washer 842 for the axial retention of the drive shaft 690. A key 844 or other locking means blocks the nut 840 against vibration loss of the drive shaft 690. Another difference of the present embodiment is that the external inlet hole 666 of the filter 652 enters from the side of the housing 654 instead of the upper part of the housing. The inlet port 666 extends axially inward via an inlet passage 824 towards the center of the centrifugal cartridge 674 to discharge oil to the inlets 67.6 of the centrifuge. The stationary housing inlet includes an inlet orifice 822 or restriction that are selectively dimensioned to control the rate at which the oil flows into the centrifuge 674 and hence the residence time of the oil within the centrifugal cartridge. The size of the restriction of the inlet 822 is determined by dividing the effective fluid retention volume of the centrifuge (during operation) by the desired residence time within the centrifugal cartridge 674.

For the application of oil soot removal, a residence time of about 10 minutes is desirable. Therefore (for a centrifugal cartridge of approximately .5 gallons (1.89 liters) 674), a flow rate of about .05 gallons per minute (.18 liters per minute) is desirable for the preferred embodiment. However, in residence times of less than about 2 to 3 minutes they can also work for soot removal applications, which would also allow a higher flow rate of the oil and therefore more oil would be filtered. The replaceable centrifugal cartridge 674 of this embodiment is also different from the previous modes. Centrifugal cartridge 674 includes an axially extending side wall 680 with stress-relieving flanges 682. A lower end cap 688 is threadably engaged or is otherwise connected to side wall 680 at the lower end of the centrifuge. At the upper end of the centrifuge, the side wall 680 extends radially inward to provide a substantially closed upper end portion 686. The upper end portion 686 has a plurality of end flanges 831. An upper end cap 828 is housed within the cartridge centrifugal 674 and is secured to the upper end portion 686. In the preferred embodiment of FIGURE 23, the ridges 831 provide deformable bolts or rivets 827 that are received through upper openings 829 in the upper end cap 828 and are ultrasonically bonded or otherwise deformed onto the corresponding openings 829 to thereby secure the upper end cap 828 and the closed end portion of the upper end 686. Between the flanges 831, the closed end portion 686 and the upper end cap 828, passages are provided. flow 832 that extend radially inward to connect the internal periphery 675 of the side wall 680 to a plurality of centrifuge outlets 678. The upper outer lid 828 provides a cylindrical opening 750 which is received by a larger diameter segment 690a from the driving shaft 690. To provide balance to the centrifugal cartridge 674 during the operation and strong axial retention of the centrifugal cartridge 674 on the drive shaft 690, the aperture 750 has a tightly controlled tolerance and is preferably machined to fit tightly on the larger diameter segment 690a. the centrifugal cartridge 674 also includes the central tube 858 which slidably receives the drive shaft 690 and angles radially outward from top to bottom. The central tube 858 has an upper end 860 saturated with adhesive for the upper end stage 827 and the lower end 860 saturated with adhesive for the lower end cover 688. The central tube 858 prevents the oil from leaking radially outward between the centrifugal cartridge 674 and the drive arrow 690 both during operation and when it is free. Preferably, the central tube 858 includes a plurality of axial support flanges 862 (FIGURE 24) that provide additional support for the upper and lower ends of the centrifugal cartridge 674. Similar to the above embodiments, the centrifugal cartridge 674 of the present embodiment has inlets 676 and outlets 678 positioned very close to its axis of rotation and at the upper end of the cartridge 674, so that the flow through the centrifugal cartridge is from the inlets 676, downwardly, and radially outwardly in the centrifugal body 674 and then back radially inward, towards outlet 678, as indicated by the flow lines in FIGURE 23. The outlets of centrifuge 678 are positioned radially outwardly of the inlets of centrifuge 676, so that the fluid flows out of the outlet 678 during rotation of the centrifugal cartridge 674. However, the centrifugal cartridge 674 of this embodiment provides only a chamber 738 or level for centrifuging oil. As shown in FIGURE 23, the external centrifugal side wall 680 is preferably angled radially inward from bottom to top to facilitate the migration of the heavier particles to the bottom during the rotation of the centrifuge. During the operation and rotation of the centrifugal cartridge, the oil flow is dosed to the centrifugal cartridge 674, by an oil pressure function and the size of the selected inlet hole 822. The oil is directed by an outward angled guide wall 864 and falls vertically by gravity downward toward the centrifugal filtration chamber 738 where it forms an annular high-pressure oil ring whose internal diameter is approximately the diameter of the centrifugal outlets 678. The heavier soot particles migrate downward due to the slope of the centrifugal wall 680 and aggregate, assemble and preferably adhere to the centrifugal wall 680. The lighter oil migrates upwards and is forced radially inward, towards the outlets 678 due to the oil pressure of the annular 0 ring inside the body centrifugal 674. The outlets 678 expel centrifugally radially outward, against the surface of the inner periphery 653 of the stationary housing 674 where it flows therethrough to an oil outlet port 668 near the bottom of the housing 654. When the centrifugal cartridge 674 is free, the oil is stopped in the filling chamber for centrifuge 738 by gravity due that the outlets 678 and the inlets 676 are located vertically above the chamber 738, which advantageously retains the soot inside the centrifugal cartridge 674. Any oil remaining in the inlet passage 824 can fall to the centrifugal cartridge 674 through the the help of the funnel-shaped guide surfaces 866 at the inlets 676. There are several advantages of using the electric drive as shown in the present embodiment. One advantage is that the electric drive can provide a more reliable source of energy, which can more reliably provide the desired high speeds to separate oil soot which is the preferred application, while generating less noise. The electric motor 700 can also reduce costs and be more convenient in terms of the location of the inlet holes, and the oil passages in the filter. Another advantage of the third embodiment is that the arrow is solid, and therefore easier to manufacture, which also simplifies the construction of other components at the upper end of the filter. Turning next to the embodiment described in FIGURE 26, it will be understood that the filter 952 has the same parts and operates much in the same manner as the third embodiment described in FIGURES 23-25, however the present embodiment uses a cartridge replaceable centrifugal 974 which is similar in many respects to those shown in FIGS. 18-22. More specifically, this embodiment provides a containment trap 942 within the centrifugal body 974 that provides multiple levels of soot capture. It is noteworthy to mention that centrifuges with multiple levels may require a greater total residence time of the fluid within the centrifuge than those with a level. The reason is that the fluid can be mixed when it proceeds outward, to the next level with time adjustments necessary for an effective centrifugal separation of the fluid and contaminant at the given rate. FIGURES 27-30 illustrate alternative embodiments of the filter cartridge according to the present invention and are shown in association with a drive arrow 690 of the filter 652 shown in FIGURE 23. The centrifugal cartridges of FIGURES 27-30 are similar in Many aspects to the filter cartridges of the modalities of FIGURES 18-26. The embodiment of FIGURE 27 provides a centrifugal cartridge 1074 that includes a steel body or basket 1073 having a side wall 1080 and a radially inwardly extending upper end 1086. A stamped steel lower end cap 1088 is attached to the side wall of the basket via a double seam 1270 to close the lower end of the filter cartridge 1074. The side wall 1080 of the steel basket 1073 is straight in this embodiment and does not angulate inwards or outwards. The upper end 1086 includes a central opening 1150 for providing inlets to the centrifuge 1076. positioned radially inward of the outlets of the centrifuge 1078. Placed inside the centrifugal cartridge 1074 is a central tube 1258 and an end cap or deflection plate 1228 The tube 1258 on the lower end 1257 placed in or otherwise secured to the lower end cap and an upper end 1259 including an internal opening 1261 sized to be received closely by the drive shaft 690. The central tube 1258 is preferably it angles radially inward from bottom to top and engages as a seal to the lower end cap 1088. The deflection layer 1228 is positioned within the basket in spaced relationship with the upper end 1086 of the basket 1073. The plate 10 deflection 1228 is maintained in axially spaced relation by a plurality of flanges 1027 on central tube 1258 for e molding the deflection plate 1228 against the upper end 1086 of the basket 1073. The deflection plate 1228 includes a central hub portion 1272 that is received in the upper opening of the basket 1150 and includes an annularly extending axially extending net. 1254 which divides the opening 1270 into centrifuge inlets 1076 and outlet 1078. The deflection plate 1218 also includes tabs 1276 on its radial periphery which help to align the deflection plate 1228 radially within the basket 1073. Between the tabs 1276 and the inner periphery 1075 of the basket 1073 there are flow openings 1278 which allow the oil at the periphery 1075 of the basket 1073 to flow back radially towards the outlet 1078. The flexing plate 1228 may also include spacers or other separation means for locating the deflection plate axially in spaced relationship to provide flow passages 1232 from the openings 1278 to the outlet 1078. The central tube 1258 and the deflection plate 1228 can be made of plastic or other suitable material. An advantage of the embodiment of FIGURE 27 is that it provides a lower cost method for the mass production of replaceable centrifugal cartridges if incineration of the filter cartridge is not necessary. The embodiment of FIGURE 28 also includes a steel basket 1073a and a attached lid or lower end cap 1088a attached to the side wall 1080a of the basket 1086a to close the lower end of the filter cartridge 1074a. Nevertheless, in FIGURE 28, the outer side wall 1080a or the surface of the inner periphery 1075a thereof is conical angled radially inward from bottom to top. The tapered side wall 1080a of the basket 1073a may be preferable to facilitate a better migration of the soot and heavy particles towards the larger diameter, which is near the double junction in an area indicated by 1275. The central tube 1258a of this mode includes an axially outward flange 1277 to support the deflection plate axially. The outward flange 1277 includes several holes 1279 to allow fluid or oil in the centrifugal cartridge chamber. The deflection plate 1228a has axially extending spacers 1027a integrally connected thereto which engage the basket 1073a. The separators 1027a or the separator means locate the deflection plate 1228a in an axially spaced relationship that provides flow passages 1232a of the inner periphery 1075a of the steel basket 1073a to the outlet 1078a. The deflection plate 1228a and the central tube 1258a can be molded of plastic material. The cartridge 1074b of FIGURE 29 includes a plastic centrifugal body 1073b with a one-piece part 1229 that includes a central tubular portion 1258b and a portion of the deflection plate 1228b. The part of the piece 1229 can be molded of plastic material using a division in the matrix. In addition to the central part of a piece 1229, the cartridge 1074b of the embodiment is structurally and functionally similar to what is described in FIGURE 23. The cartridge of the centrifugal filter 1074c of FIGURE 30 includes an external cartridge body 1073c which is made of die-cast aluminum. A lower end cap of pressurized aluminum 1088c is threadably coupled with the side wall 1080c of the centrifugal body 1073c. an advantage of this embodiment is that the unit could be cleaned and reused if desired by unscrewing the lower end cap 1088c for washing. Similar to the embodiment of FIGURE 28, the central tube 1258c includes a radially outwardly flange 1277c that supports a deflection plate 1228c. Screws 1027c are used to separate the means for fixing the separated axial relationship between the centrifugal body 1073c and the deflection plate 1228c to hold the deflection plate 1228c to the die-cast aluminum body 1073c. To summarize some of the advantages common to most cartridges of the preferred embodiments, the cartridge can be constructed with a containment trap with a plurality of telescopic conical walls positioned within the centrifugal cartridge as shown in FIGS. 18-22, and 26 or with conical walls as shown in FIGURES 23 and 27-30. For the preferred application of removing oil soot in engine applications, each of the filter cartridges described in the various embodiments preferably has a diameter of approximately 5 inches (12.7 cm) and a retention volume of approximately one half gallon (1.89). L) and at the same time it is strong enough to withstand rotational speeds of approximately 11,000-12,000 rpm around its central axis with fluid in it without failing or otherwise separating. The high speeds that the cartridge is able to reach make it particularly adaptable to remove very fine particles of fluid such as removing soot from oil which, in other circumstances, could not be removed effectively by centrifugal force. The internal diameter surfaces of the cartridge are narrowly dimensioned and preferably machined for a perfect fit on the drive shaft to better balance the cartridge so that radial loads are minimized. The components of the centrifuge include cylindrical or conical walls, the central tube, the deflection plate or the internal top end cap, and the centrifugal body are symmetrical around the axis of rotation when mounted on the drive shaft, which provides a highly balanced centrifugal cartridge that reduces the induced loads on the drive shaft and the ball bearings. Each cartridge mode includes inlets and outlets in the upper part thereof, which retain fluid in the cartridge when the centrifuge is free or unoccupied. The centrifuge outlets are preferably positioned adjacent to the centrifuge inlets, so that the capacity of the centrifugal cartridge is maximized, thereby providing a long residence time to the fluid in the cartridge during the operation and facilitating the processing of more fluid. Typically a ring-shaped bushing or wall divides the central opening in the upper part of the cartridge into inlets and outlets. A plate is placed within the cartridge near the upper end of each of the embodiments to provide flow paths for oil or lighter clean fluid from the inner periphery of the outer wall of the cartridge radially inward of the outlets. Preferably, the outer side wall or the inner peripheral surface of the side wall is conical, which facilitates the migration of heavier particles down and the lighter particles upward toward the outlets during the centrifugation operation. Turning to the embodiment of FIGURE 31, there is provided a filter 1052d which is similar in many structural aspects to the modality described in FIGURE 23, and therefore only the differences between the modalities will be noted. Similar to the embodiment of FIGURE 23, the filter 1052d includes an electric motor HOOd for driving a drive shaft 1090d and a centrifugal cartridge 1074d. However, in the preferred embodiment of FIGURE 31, the inlet discharge orifice 1222d for feeding oil or fluid to the centrifuge is provided by a mounting block 1295 that is supported and fixed to the upper bearing flange 1170d. Similar to the above embodiments, the size of the inlet discharge orifice 1222d is selectively dimensioned with restrictions therein to provide the desired residence time of the fluid within the centrifugal cartridge 1074d during operation. The mounting block 1295 includes a threaded opening 1297, a fastener or other hose connector for receiving and securing a flexible or rubber hose (not shown). The other end of the rubber hose can then be connected to the engine oil circuit to feed pressurized oil to the filter 1052d. An advantage of the embodiment of FIGURE 31 is that the inlet discharge orifice 1222d is moved with the drive shaft 1090d and the centrifugal cartridge 1074d, so that the oil is directed toward the inlet even when the vibrations or loads of Shock induced by the vehicle causes slight misalignment between the stationary housing 1054d and the bearing flange 1170d through the vibration isolators 1184d, 1185d. The centrifugal cartridge 1074d of the embodiment of FIGURE 31 also includes many notable differences, the cartridge includes an external steel body or basket 1073d including an axially extending conical side wall 1080d and an upper end extending radially inwardly 1086d. . The upper end 1086d provides a central opening 1150d for the inlet and outlet of oil or other fluid. A lower end cap 1088d is attached to the side wall 1080d near the lower end of the centrifugal cartridge 1074d. A cylindrical steel central tube 1258d is glued to the lower cover 1088d to effect a leak-proof joint to prevent leaks when idle. An internal top end cap 1280 is placed in the basket 1073d and is provided by two separate flow divider caps, including a joining cap 1284 and a deflection plate 1282, both of which can be stamped steel components that can be burnished and polished to obtain the precise diameters for their radial location. The deflection plate 1282 can be supported from the bottom by the central tube 1258d and includes a radially extending disc-shaped portion 1286 and an axially extending conical hub 1287. The conical-shaped hub 1287 extends axially outside the opening 1150d and radially inwardly at a small angle to closely engage the drive shaft 1090d to transfer radial loads thereto into a 1 position very close to the 1092d ball bearings. An advantage is that this reduces the bending moments in the 1090d arrow and reduces the potential for the natural frequency of the arrow to cause problems. This allows greater efficiency and higher speeds while increasing the life of the 1094d, 1092d ball bearings and total reliability. The radially extending portion 1286 is maintained in spaced relationship to the upper end 1086d to provide flow passages 1346 from the inner periphery 1075d of the basket 1073d through the flow holes 1238d near the outer peripheral edge of the deflection plate 1282. towards the 1078d centrifugal outlet. In the present embodiment, the external flow orifices 1238d are positioned within a solid continuous external rim 1296. The rim 1296 includes a slightly annular profile which locates the deflection plate 1282 radially and concentrically within the basket 1073d. Additional internal flow ports 1294 are positioned radially inwardly of the external flow openings 1238d, so that the deflection plate 1282 can be described as perforated. The advantage of moving the external flow orifices 1294 away from the inner periphery 1075d of the basket 1073d is that the centrifugal cartridge 1074d has a greater capacity to retain heavier contaminants such as soot and sludge. The particular centrifugal force at any given point in the centrifugal filter 1074d is a function of the rotational speed and, more importantly, a linear function of the radius of each point. The points radially inward receive less centrifugal force than the points radially outward, which means that the lighter fluids will migrate radially inward while the heavier particles migrate radially outward. By moving the flow orifices 1238d, 1294 radially inward, the present embodiment ensures better that the lighter oil particles are returned via the passages 1232d to the outlets 1150d and not the heavier soot and mud particles. The radially outwardly extending portion 1282 and the portion of the conical bushing 1287 meet in an annular through portion 1288 which includes openings 1299 to allow oil to enter the cartridge 1074d. The through portion 1288 extends inward toward the lower end of the centrifugal cartridge 1074d to direct the oil to the cartridge and better prevent the oil from short-circuiting prematurely with the flow openings 1238d, 1294 on the deflection plate 1286. The lid 1284 includes a conical portion of angled annular wall 1290 extending radially inward from bottom to top and a supporting portion 1292. Support portion 1292 is supported by deflection plate 1282 and upper end 1086d of the basket and also provides means for separating the deflection plate 1282 and the inner upper end cap 1280 a distance from the upper end 1086d of the basket 1073d. The conical portion 1290 similarly extends out of the central opening 1150d and near the discharge orifice 1222d. This advantageously locates the centrifugal inlet 1076d very close to the inlet discharge orifice 1122d to more reliably receive it. The conical portion 1290 divides the central opening 1150d into an inlet 1076d to receive unfiltered oil and an outlet 1078d to discharge filtered oil. The support portion also includes holes 1298 to accommodate the flow passages 1232d. An advantage is that the axially extending wall 1290 extends outwardly of the opening 1150d and acts as a collector to prevent oil from entering the centrifugal cartridge 1074d. Another advantage is that the wall 1290 or the inner peripheral surface thereof is angled slightly outward from top to bottom, so that the rotating action of the centrifugal cartridge 1074d aids the oil at 4 °. move down towards the 1974d cartridge. Similarly, the tapered bushing 1287 helps guide the oil to the centrifugal cartridge 1074d. The embodiment of FIGURE 32 uses the same stationary housing 1052e as in the embodiment of FIGURE 31. However, the centrifugal cartridge 1074e of the embodiment of FIGURE 32 is structurally different from that of FIGURE 31. Although the centrifugal cartridges of FIG. embodiments of FIGURES 31, 32 are structurally different, the cartridges remove soot from the oil in substantially the same functional form. Therefore, only the different structural details will be noted. The centrifugal cartridge 1074e of the embodiment of FIGURE 32 utilizes a conical steel basket 1073e and a lower tie-down lid 1088e similar to that shown in FIGURE 31. However, the embodiment of FIGURE 32 instead includes a plaque of FIG. 1280e unit deflection, which can be die-cast aluminum, as the internal top end cap. The deflection plate 1280e includes a central bushing 1306 connected by a plurality of spokes shaped ribs 1304 to an outer circular or annular rim 1310. Flow ports 1238e are provided between the spokes 1304e which provide a flow passage 1232e to the outlet of the cartridge 1078e. Central bushing 1306 includes an inner bushing portion 1306a and an outer bushing portion 1306b connected to a plurality of flanges 1316c therebetween. Preferably, the outer annular inner hub portions 1306a, 1306b extend axially outward of the central opening 1150e of the basket 1073e. The inner portion of the hub 1306a has a cylindrical opening 1150e which can be precision machined to closely receive the drive shaft to transmit radial loads. The inner bushing 1306a includes an internal cavity 1308 that is adhesively bonded to the central tube 1258e. The central bushing 1306 provides an inlet 1076e between the inner and outer portions of the bushing 1306a. 1306b. The inner portion of the bushing 1306a includes a conical outer peripheral surface and the outer portion of the bushing 1306b is also conical in shape. To secure the deflection plate 1280e within the upper end 1086e of the basket 1073e, two annular ribs 1300, 1302 are provided as separation means for aligning the deflection plate 1289e in axially spaced relationship with the upper end 1086e of the basket 1073e. The first annular rib 1300 is formed in the conical side wall 1080e and is coupled to an outer peripheral annular rim 1312 that encompasses the outer peripheral rim 1310 to prevent axial movement of the deflection plate 1280e downwardly. The annular rim 1312 also pilots the deflection plate 1280e radially within the basket 1073e to align the concentric deflection plate or otherwise symmetrically about the axis of rotation. The second annular rib 132 is formed at the upper end 1086e of the basket 1073e and comes into contact with the spokes 1304. The second annular rib 1302 pushes the deflection plate 1280e down against the first annular rib 1300 to prevent movement toward above the deflection plate 1280e. Preferably, the cartridge 1074e is dynamically balanced about its axis of rotation by means of an equilibrium machine (not shown). To dynamically balance the centrifugal cartridge 1074e, weights (not shown) can be adhered to the second annular rib 1032 in an area indicated by the reference character 1314 or other appropriate location. Referring to FIGURE 34, a centrifugal filter 14o2 is illustrated according to another preferred embodiment of the present invention. The centrifugal filter generally comprises an outer centrifugal housing 1454 for mounting to the frame of a vehicle and a replaceable centrifugal cartridge 14 which is adapted to rotate within the housing to remove soot from oil or other such contaminants. Before going on to a more detailed description of the preferred modality, some general structural and operative details of the centrifugal filter 1452 will be provided to facilitate a working understanding of the filter 1452. The centrifugal housing 1454 generally comprises an inlet of the housing 1466 for receiving unfiltered oil from the engine and a housing outlet 1468 for returning oil filtering to the motor and drive mechanism 1499 for rotating the centrifugal cartridge 1474 within the housing 1454. The centrifugal cartridge 1474 generally includes a cartridge inlet 1476 for receiving unfiltered oil from the housing 1454, a centrifugal filter trap 1510 for removing fine particles such as oil soot during the rotation of the cartridge 1474 and an outlet of the cartridge 1478 to discharge filtered oil. Referring now more closely to the housing of the filter 1454 and referring to FIGURE 35, the housing 1454 includes a stationary frame 1512 that is adapted to be mounted to the frame of a vehicle via mounting projections 1464 (FIGURES 39 and 40) in which Threaded fasteners are received. The armature 1512 is preferably cast of aluminum material to provide a rigid support structure to be mounted to the vehicle frame and resist shock and vibration loads induced by the vehicle and which at the same time provides support for the cartridge and other rotating components. . The armature 1512 includes a substantially cylindrical outer wall 1480 having a closed upper end 1458 and an open upper end 1456 vertically above the lower end 1458. Between the lower and upper ends 1458, 1456 is a centrifugal chamber 1484 which receives the centrifugal cartridge 1474. The housing 1454 is mounted in the vertical orientation illustrated in FIGURES 34 and 35, so that an automotive or mechanical technician can service the 1452 filter, from the top of the vehicle instead of from a pit below the vehicle. replace the 1474 cartridge and perform other such service operations. The lower end 1458 is closed by a lower end portion 1456 integrated to the integral wall 1480 and extending radially inward from the side wall 1480 and a lower bearing and motor assembly 1514 mounted in the central opening of the end portion 1456. The open upper end 1456 is closed by a cover 1460 that is received exactly therein. The cap 1460 can be manually removed from the armature 1512 to expose the open upper end 1456 of the armor 1512 and thereby allow a service technician to access the cartridge 1474 within the housing 1454 for removal and replacement. A pair of annular seals 1498 are positioned and compressed between the cylindrical end periphery of the cap 1460 and the cylindrical periphery of the armature 1512 to prevent contaminants such as dust, water and the like from entering the housing 1454. Seals 1498 seal in a manner more important is an oil inlet flow path to the filter 1452 as will be explained later in greater detail. The lid 1460 is positively retained on the armature 1512, by a metal strap 1518 which has an end rotatably connected to the housing by a pivot bolt 1520, which is secured between two teeth of a 1522 assembly fused to the armature 1512 and a second end secured to the armature 1512 by a screw in t 1524 or another such fastener via a threaded hole 1526 in a cast mounting flange 1528 of the armature 1512. The screw in t 1524 can be selectively tightened to maintain the proper retention of the lid 1460. Advantageously, the screw in t 1524 can be handled manually without the need for any special tools. The cap 1460 includes a radially outwardly flange 1530 which sits against a radially flat seating surface 1534 provided by the armature 1512. The screw in t 1524 can be removed to also remove the metal strap 1518 and thereby provide the manual removal of the lid 1460 to provide access to the centrifugal housing 1454. Advantageously, this allows a mechanic to easily access the filter cartridge from the top of the filter 1452, so that the mechanic can service the filter 1452 for removal and replacement of the cartridge by remaining on the floor instead of needing the requirement that the mechanical is below in a force below the vehicle. Access from the top can be achieved by mounting the filter unit 1452 to the vehicle frame instead of the vehicle engine. However, it will be appreciated that various features of the present invention may also be used in a unit mounted in a motor or in a lower access unit in an alternative embodiment. The cap 1460 is also a relatively rigid support structure to which an upper bearing support assembly 1536 is mounted. The cap 1460 can be easily molded or molded of aluminum material. The cover 1460 provides multiple mounting projections 1532 that allow the upper bearing support assembly 1536 to be easily mounted to the cap, while axially separating the cap mounting assembly 1460. The cover portion 1538 of the cap 1560 is angled upwardly from a dome-shaped cover portion 1540, the center of which engages with the retaining strap 1518 for balanced retention of the lid 1460. The dome portion 1540 also provides an empty space 1542 between the projections 1532 to better accommodate the upper bearing support assembly 1536. Between the upper and lower bearing mounting assemblies 1536, 1514, a drive shaft 1490 is hinged, preferably made of stainless steel. The drive shaft 1490 includes a larger diameter central portion 1544 and two progressively smaller diameter portions 1546, 1548 joined by a conical surface 1552, 1554 at its upper end and a smaller diameter portion 1550 at its lower end. The drive shaft 1490 also provides a projection similar to a raised ring 1556 that also provides a tapered contact surface 1558. The intermediate smaller diameter portion 1546 also provides threads 1560 in which a hex nut 1562 or other fastener is used to secure releasably the cartridge 1474 on the arrow of • drive 1490. Specifically, the cartridge 5 is slidably mounted on the drive shaft 1490 and is securely and tightly held between the hex nut 1562 and the raised projection 1556 to provide torsional transfer between the filter cartridge 1474 and the arrow 1490. The hexagonal nut ^ 10 1562 provides another conical surface 1564 oriented towards the conical surface 1558 of the projection 1556. The filter cartridge 1474 includes conical coupling surfaces 1568, 1570 which engage in beveled contact with the surface conical 1558 of the drive shaft 1490 and the conical surface 1564 of the hex nut 1562 to provide both radial and axial transfer and other loads Similar ™ near both upper and lower ends of the 1474 cartridge. The use of beveled contacts keeps the rotating element in the body in the radial and axial directions, so that there is no movement between the centrifugal element and the arrow. This helps increase the natural frequency of an arrow, which is designed to be greater than 12.00 rpm, sufficiently greater than the rotational speed of the filter 1452 to prevent amplification of vibrations. This also achieves a much more highly balanced cartridge 1474, which advantageously results in a more balanced rotation of the cartridge 1474 and therefore a longer life of the bearings, motor and other filter components. The beveled contact surfaces also prevent wear of the material of the drive shaft 1490. The mounting assembly of the lower bearing 1514 includes the drive mechanism 1499 for driving the shaft 1490 and therefore the centrifugal cartridge 1474. The preferred embodiment of the The drive mechanism includes a brushless electric motor with three phases of alternating current 1500, however, it will be appreciated that other drive mechanisms such as a turbine driven by fluid or oil, or another type of electric motor, a mechanical link or other mechanism Appropriate drive that provides sufficient speed and power to remove soot from the oil can also be used. The brushless electric motor 1500 provides a relatively simple, highly reliable mechanism to achieve the high speeds needed to remove soot from the oil, which requires at least approximately a force of 10,000 g (10,000 times the force of gravity). The 1500 motor is located vertically below the cartridge so as not to interfere with the removal and replacement of the cartridge when the 1452 filter is of the above access type. Assembly of the lower bearing assembly 1514 includes lower bearing assemblies 1572, 1574, preferably made of cast aluminum, which are secured to the outer frame 1512 and which house the motor 1500 therebetween. The lower bearing assembly 1574 also serves as an outer cap for closing the lower end 1458 of the filter housing 1454. The motor 1500 generally includes a permanent magnet 1580 fixed via a sleeve 1582 to the drive shaft 1490 to serve as a rotor for impart movement to the drive shaft 1490. The stator portion of the motor 1500 including coils 1584 and lamination stacks 1586 are separated from the magnet 1580 by a small air space which may be approximately .015 inches (0.3 millimeters) of radial distance. The lamination stack 1586 has an external radial peripheral portion fixed in a cavity 1588 provided by the bearing assemblies 1572, 1574. The motor 1500 accelerates the cartridge 1574 as fast as possible to overcome the low natural resonant frequency of the total rotating mass with the rubber mounts, thus investing little time at a rate at which the natural low resonance frequency occurs. The 1500 engine is located between two sets of 1493 ball bearings, 1494 in which the arrow 1490 is articulated and retained. The internal tracks of the two sets of bearings 1493, 1494 are press-fitted onto the drive shaft 1490 with the outer tracks contained in the bearing assemblies 1572, 1574. An elastic washer 1590 couples the outer race of the upper bearings 1493 to maintain an axial force on the upper bearings against the sleeve 1582. The outer race of the lower bearings 1494 is secured by a pressure ring to ensure axial retention of the lower bearings 1494. The two sets of bearings 1493, 1494 in the The arrow motor end reliably maintains the small gap between the rotor and the stator of the 1500 electric motor. The two sets of bearings minimize the likelihood of contact between the rotor and the stator during high-speed rotation of the 1474 cartridge within of housing 1454. Although two bearings are shown, it is also possible to raise the rotating element of the filter the upper part of the electric motor using widely spaced bearings at the lower end of the motor, but this is less desirable from the point of view that the filter unit is required to be very high. The mounting assembly of the lower bearing 1514 which includes the stator of the electric motor 1500 is secured to the external armature 1512 by a vibration isolator 1578. An upper bearing assembly 1576 of the mounting assembly of the upper bearing 1536 is also secured by an insulator similar vibration 1578. The outer race of an upper set of ball bearings 1492 is secured to the upper bearing assembly 1576 by a snap ring. A live center 1592 is secured to the inner race of the bearings 1492 by a snap ring. The 1592 Live Center provides a conical coupling surface 1594 ia which is coupled with the corresponding conical surface 1554 of the drive shaft 1490.

The belt 1518 exerts downward force on the cap 1460, which in turn, produces the coupling between the live center 1592 and the drive shaft 1490 to transfer radial and axial loads therebetween. The upper vibration isolator 1578 also stores energy to provide a constant axial force which maintains the continuous coupling (except at extreme shock loads) between the live center 1592 and the arrow 1490. This provides axial and radial support to the rotary shaft 1490 and therefore the cartridge 1474 in points both above and below the cartridge 1474, so • which extends the life of the bearing and provides a more balanced rotation of the rotating elements of the filter 1452. Furthermore, since there is no relative movement between the beveled contact surfaces 1594, 1554 of the arrow 1490 of the live center 1592, there is no wear resulting from the surface, which is advantageous to provide a service life • prolonged arrow and restrict the inner bearing track. Specifically, the live center 1592 through the beveled contact allows the rotation of the arrow 1490 for millions of revolutions without "wear" (removal of material) from the arrow or part that retains the inner bearing track, since there is no need for radial space between the surface as required with two concentric cylindrical constraints. Referring to FIGURE 41, each vibration isolator 1578 includes two rigid members and an elastic member in the form of an inner metal ring 1596, an outer metal ring 1598 and a rubber ring but relatively rigid fixed 1600 of safe way between them. The outer metal rings 1598 are securely fastened or otherwise secured to the cap 1460 on the upper part of the frame 1512 and the lower part of the frame 1512. Each inner metal ring 1596 is securely or securely fastened otherwise to the bearing assemblies at the respective ends. The rubber ring 1600 allows a smaller controlled interval of relative axial and radial movement between the inner and outer metal rings 1596, 1598. One advantage is that the vibration isolators 1578 serve to reduce engine vibrations and shock loads induced by the vehicle that interfere with the rotation of the cartridge 1474 in the housing 1554 and therefore maintain a long life for the bearings. The vibration isolators 1578 through the elasticity of the rubber rings 1600 also serve an alignment function to allow a slight angular and displacement alignment of the three sets of bearings 1493, 1494, 1492 without having to make the components of the centrifugal housing with very narrow and virtually impossible tolerances. In most machinery, the use of three bearings on a single arrow is considered a bad practice. However, using vibration isolators, the use of three bearings is not a problem. The elasticity of the rubber rings 1600 allows the three bearings 1493, 1494, 1492 are easily aligned to receive the arrow and thus allow the lid 1460 to be easily removed and replaced for maintenance purposes. By using three sets of bearings, the centrifuge is more highly balanced and the space between the stator and the motor rotor 1500 is kept narrower thereby preventing all or substantially all contact between the rotor and the housing. These advantages result in a longer life of the 1500 engine and the 1493 bearings, 1494, 1492. As shown in FIGURE 41, the rubber ring 160 includes larger portions 1602 and smaller portions 1604. The rigidity of the rubber-rings 1600 is predetermined by selectively sizing the larger and smaller portions 1602, 1604. Either way, the rings have a continuous periphery to provide a sealing function, which is particularly advantageous at the lower end 1458 of cartridge 1474, where the rubber parts are exposed. This prevents the oil from leaking from the filter 1452 and that external contaminants enter the system. Another feature is that the range of motion of the vibration isolator 1578 is controlled by the damping of the radial movement of the rotating member to thereby prevent the cartridge 1474 from hitting the housing 1454 during the operation of things such as high shock loads. induced by the vehicle. Specifically, the housing 1454 provides mechanical stops 1608 spaced at a distance 1606 from the outer diameter of the inner metal ring 1596 to dampen movement, thereby adjusting the maximum radial movement distance of the cartridge 1474. The protrusions 1532 of the cover 1460 provide the mechanical stop 1608 at the upper end of the filter 1452 while the internal circular periphery of the armature 1512 provides a mechanical stop 1608 at the lower end. This provides a highly desirable reliability feature for the filter 1452 incorporating the vibration isolators 1578. Another novel feature is the way in which the oil is fed to the filter 1452. The housing 1454 includes an external input orifice connector 1610 on the outer periphery of the armature 1512 that is fed into an orifice 1612 on the inner periphery of the armature 1512 at a location in fluid communication with a fluid passage in the cap 1460 in the form of an annular groove 1614 in the portion of the cylindrical rim 1616 of the lid 1460. The groove 1614 is between the seals 1498, which are compressed between the cover 1460 in the armature 1512 to ensure a sealed fluid passage. The interior of the flange portion 1616 includes a hose connector 1618 which is connected by a suitable length of flexible hose 1620 to a hose connector 1622 on the upper bearing assembly 1576. The bearing assembly 1576 includes an external orifice 1626 in fluid communication with the hose connector 1622 which feeds oil to the cartridge 1474. An advantage of this configuration is that there are no hoses or wires to be disconnected during the removal and replacement of the cartridge in which the cover 1460 is removed. Tightening the strap 1518 on the lid 1460, the fluid connection. between the inlet connector 1610 and the outlet hole is very reliable and also very clean with the use of seals 1498. In addition, the cover 1460 can be connected in any angular orientation to complete the inflow path. A fixed orientation cap can also be provided in an alternative embodiment. Another advantage of using a bearing assembly 1576 to feed oil into the cartridge 1576 is that the outlet orifice 1626 moves with the centrifugal inlet 1476 during the vibrations and shock loads that are supported in part by the vibration isolators 1578. outlet orifice 1626 remains precisely aligned with the inlet 1476 and thus prevents leakage or spatter of the cartridge 1474 during normal operation. This also helps maintain a clean operation. To control the amount of oil flowing to the filter cartridge 1474, a restriction is provided in the flow passage in the housing 1454 at some point upstream of the filter cartridge 1474. In the preferred embodiment, this is effected by sizing exactly the outlet port 1626 so as to act as a metering orifice to accurately control the amount of oil entering the cartridge 1474. Alternatively or additionally, a metering orifice such as a restriction upstream of the cap 1460 or the armature may be placed. external 1512 or other appropriate place. Advantageously, the metering orifice controls the residence time of the oil in the cartridge 1474. With the oil pressure in the dosing orifice and the size of the known metering orifice being, the flow rate in the cartridge can be determined. Because the engine oil pressure is relatively constant, the flow velocity can thus be controlled. An adjustment mechanism (not shown) may also be provided to control the size of a metering orifice and therefore the flow rate to the cartridge 1474. As indicated, the minimum g-force level necessary to remove soot from the oil is about 10,000 times the force of gravity, depending to some extent on the residence time of the oil in the centrifuge. The force at level g is directly proportional to the internal radius of the element and to the square of the angular velocity as shown in the following formula: force level G = (2.838 X 10"5) N2R where: N = Revolutions Per Minute; and R = Radius in inches (cm) A force field level of 10,000 g for a centrifuge of 7 inches (17.78 cm) in diameter requires approximately 10,034 rpm. This means that the outside of the centrifuge is traveling at a linear speed of 209 miles (336.3 km) per hour. This is a very high speed that requires extreme care in the design of the unit to obtain good bearing life, minimize vibration and minimize the wear of the different parts to obtain a longer life of the filtration unit. Another important element of removing soot from the oil using a centrifuge is to allow adequate time for the soot removal process. At a force of a level of 10,000 g, we find that it takes approximately an average residence time of eight minutes to adequately remove the soot from the oil. Therefore, the necessary flow rate to the centrifuge is calculated by dividing the volume of centrifuged oil in the centrifuge by the desired residence time, in this case eight minutes. We find that shortened residence time below eight minutes in certain volume units is counterproductive. For a centrifuge with a capacity of 1.5 gallons (5.7 L) of the preferred mode (taking into account only the centrifugation of oil in the centrifuge at any time), a flow rate of 0.18 gallons (6.66 L) per minute is necessary. . In this way, this is actually a relatively large centrifuge with a relatively low flow velocity as long as motor applications are involved. Referring to FIGURE 36, the filter cartridge 1474 generally includes a top end bracket 1624 and a bottom end bracket 1628, both of which may be made of aluminum or otherwise formed of a relatively rigid material. The brackets 1624, 1628 provide end cap portions and a central tubular portion of the cartridge 1474. In the presently preferred embodiment, the upper end holder 1624 includes an end plate portion 1630, an internal tubular portion 1632, an outer tubular portion 1634. surrounding the inner tubular portion 1632 to provide the centrifugal inlet 1476 therebetween. The inner and outer tubular portions 1632, 1634 are connected by ridges 1636 which are located at spaced apart radial intervals therebetween, so that an inlet flow path 1638 is provided to a filtration chamber 1642 of the cartridge 1474. The internal surface 1646 of the outer tubular portion 1634 is angled out from top to bottom, so that the centrifugal force pushes the oil down towards the filter cartridge 1474. The lower end support portion 1628 includes an end plate portion 1648 and a portion lower tubular 1652 projecting axially upwards therefrom. The lower tubular portion 1652 of the lower support 1628 and the internal primary tubular portion 1632 of the support 1624 are threadedly connected via interlocking threads 1640 connected in another way to secure the upper and lower end supports 1624, 1628. When they are connected, the Tubular portions 1632, 1652 provide a central through hole 1654 about the axis of rotation of the cartridge 1474, which receives the drive shaft 1490 therethrough. The tubular portions 1632, 1652 also provide the tapered contact surfaces 1568, 1570 at the respective ends of the cartridge 1474. A cylindrical surface 1644 is also provided which is exactly tolerated by the external diameter of the arrow 1490 for purposes of radial alignment to ensure a more symmetrical alignment of the cartridge on the drive shaft 1490. Due to the conical contact surfaces 1568, 1570 which provide bevelled contacts at the top and bottom of the cartridge, against the upper hex nut 1562, there may be considerable space between the arrow 1490 and the internal diameters of the cartridge 1474 (specifically the internal diameters of the upper and lower supports 1624, 1648). This makes the movement of the cartridge 1474 in the housing 1454 a much easier task and allows for tolerances of the design tolerances when the supports 1624, 1628 are fused. An external cylindrical can 1656 substantially coaxial about the axis of rotation connects the outer periphery of the upper and lower end supports 1624, 1628 and provides the outer radial periphery of the cartridge 1474. The can 1656 in the preferred embodiment comprises formable metal sheet material but could alternatively comprise appropriate plastic material or other stronger material that can withstand the level of force g of 10,000 times the force of gravity when the cartridge rotates with oil in it. The connecting flanges 1658, 1660 which project axially from the respective plate portions 1630, 1648 are provided at the outer radial periphery of the respective upper and lower plate portions 1630, 1648 to provide the connection of the 1656 can. upper and lower end portions 1652, 1664 of the 1656 can are ground around the. connecting flanges 1658, 1660 for closing the filtration chamber 1642 between the cylindrical can 1656 and the central tubular portion of the supports 1624, 1628. The upper end portion 1662 also extends radially inwardly to cover a plurality of openings 1666 in the upper plate portion 1630. The openings 1666 reduce the material and hence the costs of the upper support 1624. An outer annular seal 1668 is seated in a slot 1670 and compressed between the lower end support 1628 and the can 1656 to prevent the oil and soot are leaked between the can 1656 and the lower end support 1628. External peripheral annular grooves 1672, 1673 are also provided in the upper and lower end supports 1624, 1628 in which the can 1656 is threaded to provide annular ribs 1674 , 1675 which provide axial support and retention and serve to more rigidly retain the 1474 cartridge for both Eg a more balanced axis of symmetry around the axis of rotation of the cartridge 1474. The ribs 1674 and 1675 stretch the metal of the can 1656 to place it in a slight tension to retain the cartridge 1474 more closely together. Located exactly in the filtration chamber 1642 is a filter element 1676 which generally includes upper and lower end layers 1486, 1488, a containment trap 1678 and a tubular outlet member 1680. The ends of the containment trap 1678 are saturated in the respective upper and lower end caps 1486, 1488 as a suitable adhesive compound such as epoxy or plastisol or otherwise secured thereto. Referring to FIGURE 42, the output tubular member 1680 includes a transverse support in the form of a plate portion 1682 which is located between the upper end cap 1486 and the upper end support member 1624 and a pair of tubing tubes. outlet 1684, 1685. The plate portion 16862 includes a central opening 1683 which receives exactly the outer tubular portion 1634 of the upper support 1624. The output tubular member 1680 may be a unitary member formed of molded plastic material. The upper and lower end support members 1624, 1628 are sufficiently threaded, together, to place a filter element 1676 tightly therebetween for purposes of retaining better symmetry. By threading the 1656 can in 1674, 1675, the filter element is placed in light compression to prevent any squeaking and to ensure a more fixed axis of symmetry. The tubular outlet member 1680 preferably includes elastic projections. 1688 that engage the upper end bracket 1624 for storing an axial force preventing axial movement and therefore screeching of the filter element 1676 in the cartridge 1474. Other elastic members such as an elastic washer or rubber ring may also be used. separate to prevent axial movement of the filter element 1676 if desired. The tubular outlet member 1680 includes two outlet tubes 180 ° apart 1684, 1681 for purposes of symmetry. Another novel feature of the present invention is that the outlet pipes 1684, 1685 provide a pair of closed flow passages 1686 having oil inlets 1690 near the top of the cartridge 1474 at a point preferably above the filter element 1676 and an oil outlet 1692 near the bottom of the cartridge 1474 to direct clean oil to the outlet of the housing 1468. This prevents oil drainage with soot with agglomerates near the bottom of the filter during free periods between operations. This also prevents the oil from splashing on the inside of the armature 1521 and flowing between the armature 1512 and the outer can 1656 of the cartridge 1474. Advantageously, this provides maintenance of the clean filter since there is little or no oil to be treated during the replacement of the cartridge. The mechanic can simply hold the used cartridge 1474 to remove it. The location of the oil outlets 1692 near the bottom also prevents the oil from coupling the axial length of the outer can 1656 of the cartridge 1474, which could produce a slow rotational advance that would undesirably slow the rotational speed of the cartridge 1474 and result in less efficient soot removal. Another feature is that the cartridge 1474 includes a handle 1694 at its upper end to facilitate its easy removal by a mechanic. The handle 1694 includes a connection portion 1697 secured to a cavity 1699 of the upper support 1624, a radially projecting manual holding portion 1710 that can be easily held by a. mechanic. The manual holding portion 1710 is round and preferably smooth to prevent the existence of rotation during rotation. The handle is coaxial with the rotation of the shaft to maintain the proper balance of the cartridge 1474 around the rotational axis. The oil outlets 1692 discharge to an annular passage 1696 formed in the lower portion of the armature 1512 of the outer housing 1454. The passage 1696 includes an internal wall 1698 whose upper portion can be radiated to a point having a diameter smaller than the diameter innermost of the oil outlets 1692, so that the oil is directed to the passage 1696 even when the cartridge 1474 is free. The passage 1696 has a recessed segment 1700 to accommodate the housing of the electronic devices 1702 which contain electrical wires for the motor 1500. The housing of the electronic devices 1702 is secured to the mounting assembly of the lower bearing 1514 so that the housing the electronic devices 1702, and therefore sufficient space is provided between the armature 1512 and the housing of the electronic devices 1702 so that the movements of the mounting assembly 1514 (as allowed by the vibration isolators 1578) prevent any collision between the armature 1512 and the housing of the electronic devices 1702. The oil inlets 1690 of the outlet pipes 1684, 1685 are located in a diameter that is larger than the diameter of the outermost diameter of the inlet of the centrifuge 1476 to ensure that the oil does not come out through the inlet of the centrifuge 1476 during the rotation ion. The oil inlets 1690 are preferably located radially inward of the inner periphery of the can 1656, where soot and oil are collected with soot. This better prevents soot and sooty oil from entering undesirably from outlet pipes 1684, 1685. The preferred embodiment, inlets 1690 are located radially inward as possible in radial proximity to the internal diameter of the trap. containment 1678 to provide maximum benefit. In this embodiment, the outlet tubes 1684, 1685 are elbow shaped to include a mainly radial duct 1704 and a mainly axial duct 1706. The axial passages 1706 are angled slightly outward from top to bottom to ensure that the centrifugal force pushes the oil to the oil outlets 1692. The radial passages 1706 are preferably located on top end cap 1486 to accommodate the outlet pipes 1684, 1685, the containment trap 1678 includes axially extending channels 1708 (see FIGURES 37 and 38) that coincide with the separation of the tubes 1684, 1685, the end caps 1486, 1488 include openings 1712, 1714 to allow the tubes 1684, 1685 extend therethrough, and bottom end bracket 1628 includes openings 1716 to allow tubes 1684,1685 to be discharged through the lower end of cartridge 1474. It is also possible to allow tubes 1684,1685 to come out through on the side of the cartridge 1474 at or near the lower end of the cartridge 1474, but such a configuration would, undesirably, result in a less clean environment for maintenance purposes. The annular seals 1718 are positioned between the lower end bracket 1628 and the outlet tubes 1684, 1685 to prevent the sooty oil and soot near the radial periphery of the lower end of the cartridge 1474 from the cartridge 1474. The seals 1718 are sitting in the slots 1720 in elongated abutments near the lower ends of the tubes 1684, 1685.

The soot containment trap 1678 is another novel feature of the present invention. The soot trap 1678 includes several radial levels, in this case five levels, provided between six substantially cylindrical walls 1722-1727 which are generally concentric and coaxial and have progressively larger diameters. The middle portion of each wall 1722-1727 can have a slightly larger cross-sectional thickness as shown in FIGURE 44. Each level is separated into several separate chambers 1728 by separate vertical partition walls 1730. The partition walls 1730 they locate at intervals separated by each level for purposes of balance and strength and endurance. The separation walls 1730 also prevent waves from forming during the rotation of the cartridge 1474, which in other circumstances would produce an imbalance in the rotation of the cartridge. Each chamber 1728 runs axially elongated from the lower end to the other end of the element 1676. With reference to FIGS. 37, 38 and 12 it can be seen that each chamber 172 has a slot 1732 in two of its walls providing an oil inlet in a end of the trap 1768 and another slot 1732 that provides an oil outlet at the other end of the trap 1678. This slot arrangement causes the oil to travel the entire length of the chamber 1728 to reach the adjacent chamber chamber. . To facilitate easier compression of the configuration, the schematic diagram of FIGURE 45 shows a view from the end of the trap provided with flow lines indicating the flow of the oil through the trap and circles schematically indicating slots at the end and squares indicating slots in the lower end of the trap. Each slot serves as an oil outlet for a chamber and an oil inlet for an adjacent downstream chamber. The slots 1732 formed in the containment trap 1678 are axially long enough so that a compound (such as epoxy or plastisol) does not cover the slots 1732 when the end caps 1486, 1488 are attached to the end of the trap 1678. In the Most of the chambers 1728, the slot 1732 is located in the partition walls 1730 near the cylindrical inner diameter wall, to maximize the oil holding capacity of the chamber 1728 during rotation, so that the oil element is Slow through the camera. This also forces the oil to leave the chamber 1728 in a radius shorter than the chamber space volume 1728, thereby allowing the lighter weight oil that is more free of soot to move from a chamber of the chamber. adjacent trap 1728 to the next. The separation volume of the 1728 camera also serves to • provide a greater volume and surface area for the soot agglomeration. Although most slots are located in separation walls, the first and last chambers of each level designated as 1738, 1740 facilitate flow between levels. In particular, a slot 1732 in each of the cylindrical walls 1722-1727 and between the last internal level chamber and the first chamber of the next external level. In the preferred embodiment the oil flows through the containment trap 1678 is divided into two flow paths separately indicated generally in 1742 ,. 1744, as indicated by the schematic diagram of FIGURE 12. The solid partition walls 265 that are 180 ° apart separate the trap 1678 in separate flow paths 1742, 1744. The flow paths Separated 1742, 1744 are provided in the perspective halves of the trap 1678 and are identical to ensure when the cartridge 1474 is fd with oil, the cartridge 1474 remains balanced about its axis of rotation. The number of flow paths Separated can be adapted as desired, but preferably two different flow paths are provided for the initial balance of the filter when it is filled with oil. To ensure that the oil fills the cartridge evenly during the initial operation, the containment trap 1678 also includes separate internally dividing projection streams 1746, opposed to each other, which serve to divide the flow of oil entering the inlet of the container. the centrifuge 1476 between the flow paths 1742, 1744 uniformly. Preferably, the splitting fins 1746 are located adjacent to the first chamber, which receives the inflow in the trap 1678. The trap also includes locating fins 1748 on its outer periphery, which serve to locate the trap concentrically inside the outer can 1656. The trap 1678 has several advantages. One advantage is that the geometry provides a large surface area in which the soot can agglomerate and adhere. The heavier soot particles are more likely to be trapped radially inward and therefore less likely to pass through the centrifugal cartridge 1474. The cylindrical shape of the walls 1722-1727 and the symmetry of the walls of the separation 1730 and oil slots 1732 each contribute to a trap 1678 that is intrinsically balanced about the axis of drive rotation. The trap 1678 is also filled uniformly with the oil at the start with the smaller diameter flanges 1746 ensuring that the inflow flow is evenly divided between flow paths 1742, 1744. The symmetry and balance characteristics ensure a life of the bearing and the longer engine for the centrifugal housing 1454. This is important because it is desirable to have 10,000 to 15,000 hours of operation of the centrifuge without failure, thus having a requirement of 6 to 9 billion rotations of the drive components of the centrifuge. accommodation 1454 without failures. To ensure a more balanced cartridge 1474, the upper surface 1750 of the cartridge is made of steel plate, which provides an area that can receive weights from an operation of the balancing machine after which the weights are attached to balance more effectively. precise the cartridge 1474 around the axis of rotation. Referring to FIGURE 46, another embodiment of a filter 1874 is shown which in all material respects is identical to that illustrated in FIGURE 34, but which also includes a mechanism 1902 that allows thermal expansion and contraction between the tube inner of aluminum and the cartridge 1474 and the steel shaft 1490 of the housing 1454 for continuously holding the rotating centrifugal cartridge 1474 on the drive shaft 1490 over a high temperature range. Aluminum expands approximately twice as much as steel for a given temperature excursion. With a length of 13.5 inches (34.3 cm) of the aluminum tube and a temperature excursion between 40 ° F and 100 ° F (4.44 ° F and 37.7 ° C), the difference in the expansion between the aluminum tube and the Drive arrow 1490 is approximately 0.011 inches (0.028 cm). This contributes to temperature differences when the vehicle containing the filter travels through different geographical regions and climates. The mechanism 1902 generally includes an element secured to the arrow 1490 in the form of a hexagonal nut 1904, a seat member 1906 that moves relative to the arrow 1490 but fixed relative to the cartridge 1474, and an elastic member such as a spring or in this case a locking or locking washer 1908 which is supported by the hexagonal nut 1904 to act on the seat member 1906. The seat member 1906 provides a beveled contact surface 1910 which engages the upper bevelled surface 1568 of the cartridge 1474. The locking or locking washer 1908 is capable of being compressed and expanded over a range of at least the anticipated expansion difference between the hexagon nut 1904 and the seat member 1906, in this case 0.011 inches (0.028 cm). The resilience of the washer 1908 is sufficiently rigid to prevent most vibrations and shock loads of the engine to seat the seat member 1906 from the bevelled contact surface 1568 of the cartridge 1474. To retain the nut 1904, the seat member 1906 and the locking or locking washer 1908 in a mounting to prevent a mechanic from losing a part, a retaining element in the form of a plastic tube 1912 is provided. The plastic tube 1912 has a crenellated end 1914 which is placed in the groove 1916 on the hexagonal nut 1904. The other end 1916 is ultrasonically deflected radially outward to retain a flange 1918 on the seat member 1906. The distance between the flange 1918 and the end 1916 is set higher than the difference of contraction and anticipated expansion. The outer surface 1920 of the tube is angled radially outward from top to bottom at a slight lateral tilt angle to prevent oil from entering. contact with it as it is centrifugally driven upwardly out of the cartridge 1474. Referring to FIGS. 47-70, a preferred embodiment of the present invention is shown, which incorporates some of the concepts demonstrated in FIGURES 1-46 and can incorporate other concepts demonstrated in those previous modalities. The preferred embodiment of FIGURES 47-70 takes the form of a centrifugal filter 2052 which includes a centrifugal housing 2054 and a centrifugal cartridge 2076 mounted in the housing to rotate within the housing to remove soot from oil or other such contaminants. Referring to FIGURES 47, 48, and 61, the centrifugal housing 54 includes a stationary body, which may be comprised of an outer frame 2026 and a removable cover 2028. Preferably, the frame 2026 includes mounting means such as straps or mounting lugs which allow it to be mounted to the vehicle frame. By mounting the frame 2026 to the vehicle frame instead of the motor, a larger filter can be used, which advantageously increases the volume of oil capable of being maintained by the cartridge. The armature 2026 includes a generally cylindrical side wall 2030 and open and closed ends 2032, 2034, designed in such a manner as to indicate which end of which filter cartridge 2024 can be removed. In the preferred embodiment, the closed end is partially formed by the armature itself together with an arrow assembly or alternatively a drive mechanism assembly as illustrated in the above embodiments. The lower end portion of the armature 2026 forms an annular passage 2166 for collecting filtered oil to return it to the engine. The armature includes an external input 2036 and an external output 2038 for receiving and returning oil to a vehicle engine (not shown). In this embodiment, the external inlet and outlet are connected by means of a flow passage 2040 to allow excess oil not entering the cartridge to be directed directly to the outlet. The passageway 2166 is connected to the external outlet 2038. The cap 2028 is threaded onto the frame 2026 and has projection fasteners 2042 which facilitate manual clamping of the cap for screwing the cap onto the frame. The cap provides an inflow passage 2044 extending radially inward toward the intended rotational axis of the filter cartridge. A restriction orifice 2046 is provided in the inlet flow passage for metering fuel at a preselected speed in the centrifugal cartridge 2024. The size of the restriction orifice is determined by the oil pressure at the inlet to the 2044 inlet flow passage. , the effective oil holding capacity of the centrifugal cartridge 2024 and the desired residence time for the oil in the cartridge. The preferred residence time for the oil inside the cartridge is at least approximately eight (8) minutes, when a rotational force of 10,000 G is provided at the outer periphery of the centrifugal cartridge. The cartridge and method for effectively dosing oil in the cartridge and removing soot from the oil in an effective manner has already been described in greater detail with reference to the present specification describing the embodiments illustrated in FIGURES 34-46. In any case, it has been found that in addition to rotating the cartridge at a sufficient speed to remove soot from the oil, the size of the filter chamber needs to be dimensioned selectively relative to the restriction orifice 2046 to provide a residence time. Default oil in the filtration chamber. It has been found that a 2046 metering orifice having a diameter of 0.009 inches (0.02286 cm) (an orifice area of less than 10 thousandths of an inch square) together with a filter cartridge size that is capable of of containing approximately 1.5 gallons (5.7 L) provides a preferable arrangement for a desired residence time of eight (8) minutes in an engine-type environment when a force of 10,000 g is applied. Depending on the actual rotational speed of the centrifugal cartridge and the oil pressure provided at the external inlet 2036, it will be appreciated that those numbers may vary and may also be adapted to provide less efficient soot removal capacity. However, each of the parameters of the rotational speed of the size of the restriction hole of the cartridge, the oil holding capacity of the cartridge are matched to each other to provide an effective removal of soot. To ensure that the inflow passage 2044 connects the external inlet 2036 and the lateral oil outlet 2048, a sealed annular groove 2050 is provided between the cap 2028 and the armature 2026 and along the inflow passage 2044 to secure that the oil is communicated to the cartridge 2024 regardless of which cover is oriented and how the screw cap is tightened on the frame. A pair of large O annular seals 2052 compressed axially between the cap and the armature ensures that the inflow passage 2044 is sealed. The centrifugal housing 2022 further includes a central support arrow 2054 extending along the axis of rotation between the closed end 2032 and the removable cover 2028. The arrow 2054 provides a support element for supporting the entire rotating element within the housing . At each end, a vibration isolator indicated generally in 2056 withstands the arrow, and therefore dampens any engine vibrations or shock loads imposed by the vehicle so that they are not transferred to the bearings, the motor and the rotating element . Each vibration isolator 2056 generally includes an assembly 2058, a resilient member preferably in the form of a piece of vulcanized rubber 2060 and a cup 2062. The mounting 2058 of the upper vibration isolator is attached to the cap 2028. The assembly 2058 of the lower vibration isolator 2056 is secured to the projecting portion of the armature 2026. Each assembly includes a sleeve portion 2064 surrounding the cup 2062 to provide a mechanical stop which stops excessive radial movement of the arrow 254 , relative to the intended rotational axis of the centrifugal filter 2020 to prevent the cartridge 2024 from hitting the inner surface of the outer frame 2026. A bolt 2068 is connected to the arrow 2054 at the lower end and extends through the cup 2062 and the sleeve 2064 to provide the retention of the torsional arrow and axially. The arrow 2054 also includes a slot 2070 at its upper end to facilitate retention of the stationary arrow when changing the filter cartridges. The arrow 2054 has, generally, a central portion of larger diameter and portions of progressively smaller diameter at each end. At the ends of the larger central diameter portion, the arrow 2054 is mounted with a pair of ball bearings 2086 to facilitate cartridge rotation relative to the housing. A drive mechanism in the form of a brushless electric motor 2072 is mounted at the lower end of the arrow 2054. Although an electric motor is illustrated, it will be appreciated that other forms of drive mechanisms such as an air motor may also be used. of air, a hydraulic motor, a mechanism of mechanical gears, or a turbine driven by oil. The key consideration is that the drive mechanism must provide sufficient speed to provide sufficient force capable of removing soot from the oil. The electric motor 2072 is mounted in a motor assembly 2004 which is screwed directly onto the lower threaded portion of the support shaft 2054. In this way, the drive mechanism is also preferably supported by the vibration isolators 2056. The motor 2072 generally includes a rotor which includes a permanent magnet 2076 mounted on a frame 2078, and a stator 2080 which typically includes a rolling stack and coils. The electronic devices for feeding power to the motor 2072 are mounted in a motor housing 2082, which includes a heat sink to cool the electronic devices, on the side of the armature 2026. The armature 2078 is threadedly connected to actuating the tube 2084, which in turn is articulated by the bearings 2086, so that the drive tube and the armature are adapted to rotate relative to the support shaft 2054 and the rest of the housing. The drive tube 2084 is mounted concentrically on the support arrows 2054 with a small gap between them. The drive tube has a slot 2088 at its upper end which allows a service technician to keep the hollow tube fixed relative to the support shaft 2054 when the new cartridge is installed. In particular, a retaining nut 2090 is connected to the thread on the upper end of the drive tube 2084 to hold the cartridge down against the frame 2078. The slot 2088 allows a service technician to tighten and loosen the retaining nut 2090. The armature 2078 provides a conical, bevelled contact surface 209 for coupling the centrifugal cartridge 2024 for accurate alignment of the cartridge about the axis of rotation and for axial and radial retention of the cartridge 2024. Therefore, the conical contact surface has a center coinciding with the axis of rotation of the centrifugal filter 2020. The retaining nut 2090 also includes a conical contact surface 2092 for purposes of radial alignment and retention of the centrifugal cartridge 2024. Turning to the centrifugal cartridge 2024 in greater detail, it can be made reference to FIGURES 49 and 54-60. The centrifugal cartridge generally includes upper and lower end plates 2100, 2102 in a separate relationship and a cylindrical basket 2104 or other frame connecting the outer peripheries of the plates to provide an external housing for enclosing a filter chamber 2106 in which the soot separated from the oil. Large radial sealing gaskets 2108 are compressed between the basket 2104 and the end plates 2100, 2102 for sealing the exterior of the filter chamber 2106. In order to keep the plates in approximately spaced relationship, a central tube 2110 is threadably connected to the bottom end plate 2102 preferably with a threaded seal compound to produce a leak tight seal on the threads. The central tube 2100 is also secured to the upper end plate 2100. To secure the central tube 2110 to the upper end plate, a spring retaining clip 2112 is inserted into a slot in the upper end of the tube to locate the upper end plate 2100 on tube 2110. Next, a nut of the element 2114 is threaded on the upper end of the tube 2110 to retain the upper end plate 2100 on the tube. The upper and lower end plates 2100, 2102 are preferably cast or molded of aluminum and the outer basket 2104 is preferably made of steel sheet and connected to the end plates through a "J-shaped lock" 2116 connection and another element of similar aluminum for the operation of securing the steel. Preferably, balance rings 2116 are provided in each of the upper and lower endplates to provide a place where the material can be removed during a subsequent balancing operation on the balancing machine.

The centrifugal cartridge 2024 includes an inlet 2120 and an outlet 2122. The central tube 2110 is preferably made of the same material as the actuator tube 2084 of the housing 2022, so that the axial length of the cartridge and the actuator tube are substantially expanded to the same speed at different temperatures due to the different environmental conditions under which the vehicles can operate. The upper end plate includes a central bushing 2124 which closely surrounds the central pipe 2110 and a peripheral, outer disk shaped flange 2126 integrally connected to the bushing 2124 by a plurality of flanges 2128. The inlet 2120 is generally defined between central hub 2,124 and outer flange 2126, so that the ring formed and deviated from the predetermined axis of rotation in a position where it is adapted to align with the lateral oil outlet 2048 of the housing. Therefore, the inlet 2120 receives the oil discharged from the lateral oil outlet 2048, and allows it to enter the filter cartridge. A handle 2130 is threadably connected to the upper end plate 2100 to facilitate easy manual removal of the housing cartridge. The handle 2130 has an outward projecting lip which provides a clamping surface that can be easily held for the manual removal of an inflated or exhausted centrifugal cartridge at the insertion of a new cartridge. The inner surface of the handle 2120 or the inner surface of the flange 2126 is slightly conical and angles outwards as its angles downward, so as to ensure that the centrifugal forces force the air to go down towards the cartridge rather than toward above. The outlet 2122 is preferably provided at the lower end of the cartridge to minimize the holding effect of the oil that it could possibly have on the cartridge and also provide a less clean oil removal from the housing filter cartridge. To prevent drainage of the cartridge 2124 when it is free or unoccupied, the outlet is connected by an outlet conduit 2132 which has an inlet 2134 near the upper end of the cartridge. The inlet of the outlet 2134 is located in a radial location at a point just outside the diameter of the inlet 2120 to maximize the oil holding capacity and the filtration capacity of the cartridge 2124 during rotation. To maximize the soot removal capabilities of the cartridge 2122, a separate containment trap element 2136 is preferably inserted and retained within the filter chamber 2106. The containment trap element 2136 generally includes a filter trap 2138 which its ends are saturated with adhesive material such as plastisol, urethane, or epoxy in the upper and lower end caps 2140, 2142. A spring 2144 axially deflects the trap element 2136 towards the lower end plate and has sufficient force to maintain this against the lower end plate during operation in the environment of a vehicle. A gasket 2146 is preferably compressed between the trap element 2136 and the lower end plate 2102 to prevent most or all of the short-circuiting oil from passing along the filter trap 2138. The upper end cap 2140 includes a inlet tube 2148 which provides the inlet of outlet 2134. Lower end cover 2142 lower end plate 2102 each include outlet tubes 2150, 2152 that facilitate fluid connection of outlet conduit 2132 of inlet 2134 or outlet 2122. A radial sealing gasket in the form of a tubular gasket 2154 slides over the outlet pipes 2150, 2152 to seal the outlet flow passage. In a preferred embodiment, a large portion of the outlet duct 2134 is integrally provided by the filter trap 2138 thereby eliminating the need to separate tubes from the filter trap. As can be seen, the trap defines a pair of axially extending passages 2158 for connecting the inlet tube 2148 to the outlet tubes 2150, 2152. Except for the configuration of the outlet passages, the filter trap 2138 is substantially similar to what it is shown in the above embodiments of FIGURES 34-46 and particularly shown in greater detail in FIGS. 37, 38, 43 and 45. Therefore, additional details of containment trap 2158 and the operation thereof can be obtained with reference to those figures and the associated description. However, note that the present embodiment includes the integrally formed axial passages 2156 and therefore does not need the axial cavities formed to receive separate tubes. Additionally, this embodiment also illustrates the fact that at least two separate outlet conduits 2132 are symmetrically provided around the predetermined axis of rotation to maximize a highly balanced filter cartridge 2024 about the predetermined axis of rotation. Referring to the filter trap 2138, it should be noted that a plurality of generally concentric levels are provided by means of the corresponding generally concentric cylindrical walls 2158. Each wall having its center aligned with the predetermined axis of rotation. Each level also includes a plurality of angularly spaced apart partition walls 2160 that divides each level into a plurality of trap chambers 2162. Slots 2168 are provided in the partition walls and arranged at opposite ends of the trap so that the The oil moves along the axial length of the filter trap backwards and forwards axially as it proceeds from chamber to chamber. To transfer oil from one level to the next, each wall of the cylindrical trap has an opening 2168 in it to transmit oil between levels. Preferably, the filter trap is also divided into at least two compartments of equal size, with each compartment providing a separate flow path through the filter trap in this manner, the trap is filled substantially equally and This mode is balanced when a newly installed centrifugal cartridge is initially filled with oil. Another aspect of the present invention is that the centrifugal cartridge 2024 includes a conical contact surface 2164 on the lower end plate 2102 which is concentric about the predetermined axis such that it comes into contact and engages with the corresponding conical surface 2092 on the armature 2078 to provide radial alignment and axial and radial retention for proper balance of the cartridge. Preferably, this contact surface 2164 is precision machined to obtain a more accurate cartridge alignment. The tapered contact surface 2092 of the retaining nut 2092 increases a radial alignment and retention of the cartridge 2024. In operation, the centrifugal cartridge 2024 will be driven by the motor 2072 to drive the mechanism about the predetermined axis of rotation. The engine oil will enter through the external inlet 2036 and some of it will flow back to the engine through the bypass flow passage 2040, while a portion of the oil will flow into the centrifugal cartridge through the oil inlet passage 2044. The restriction orifice 2046 performs a dosing function and is dimensioned in relation to the oil holding capacity of the centrifugal cartridge. The oil enters the centrifugal cartridge through the inlet of the cartridge 2120 and proceeds towards the containment trap element 2136 through the filter trap 2138. The heavier particles, those which are soot, are forced radially outwardly. and in this way they are deposited in the deposit areas that are located in radially outward locations. For example, each of the chambers of the trap 2162 (except for the last chamber of the trap for that level) has a deposit area located on the inner surface of the outermost cylindrical wall 2158 for that level. Lighter materials, such as oil, are forced back in and eventually flow into the outlet conduit and exit the centrifugal cartridge towards an annular passage 2166 formed in the housing and return to the engine via the external outlet 2038. It has been found that the separation walls 2160 also serve the highly advantageous function of preventing waves from forming in the oil when the centrifuge is driven at a certain speed and against vibrations or shock loads induced by the engine or vehicle. Preventing waves from forming, the cartridge remains balanced, which reduces wear and loads on the cartridge bearings and drive components. The cylindrical wall trap modalities of FIGURES 34-70 have such separation walls, which divide each cylindrical level into separate chambers. Because the spiral trap configuration of the first embodiment prevents cylindrical or perfectly circular levels, which in turn would allow circular oil rings to be formed, the configuration of the spiral trap also provides similar means to inhibit the formation of waves in the different levels. The conical trap mode of FIGURE 19 or other cartridge modes including single-level modalities would also preferably include such separation walls or other means to inhibit the formation of waves, see for example FIGS. 71-73. Therefore, it should be understood that the conical trap wall mode would also have partition walls. It should also be noted that in the cylindrical trap mode, the cylindrical walls may have slight inclinations on them as shown in FIGURE 44, but even with slight inclinations, the walls are still considered cylindrical for all purposes. All references cited here, including patents, applications and patent publications are hereby incorporated by reference in their entirety. Although this invention has been described with emphasis on preferred embodiments, it will be obvious to those skilled in the art that variations of the preferred embodiments may be utilized and that it is intended that the invention may be practiced otherwise than specifically described herein. Accordingly, this invention includes all modifications encompassed within the spirit and scope of the invention as defined by the following claims. It is noted that in relation to this date, the best method known by the applicant to carry out the aforementioned invention, is the conventional one for the manufacture of the objects to which it relates.

Claims (63)

1. CLAIMS Having described the invention as above, the content of the following claims is claimed as property. A centrifugal filter cartridge adapted to rotate by means of the filtering fluid, characterized in that it comprises: an external housing having a predetermined axis of rotation, an inlet, an outlet, a filter chamber between the inlet and the outlet, the exit deposited radially out of the entrance; and a filter trap located in the filter chamber, the inlet being fluidly connected to the outlet through the filter trap, the filter trap includes a plurality of levels, each level being located at a radial distance different from the axis of the filter. predetermined rotation, each level includes at least one reservoir area and at least one opening, at least some of the openings is located radially inward of the reservoir area for that level. The centrifugal filter cartridge according to claim 1, characterized in that the filter trap includes a wall surrounding the predetermined axis of rotation and wound in a spiral configuration about the predetermined axis of rotation. The centrifugal filter cartridge according to claim 2, characterized in that the wall includes a plurality of depressions formed therein to provide reservoir areas and a plurality of ridges formed between adjacent depressions, the openings being provided between the ridges for transferring. Oil to the next level radially outward. The centrifugal filter cartridge according to claim 3, characterized in that the wall is constructed of a unitary sheet wound and maintained in the spiral configuration. The centrifugal filter cartridge according to claim 1, characterized in that the filter trap includes a plurality of conical walls, each providing a separate level, the plurality of conical walls being located side by side to include a radially outermost conical wall and an outer radially innermost wall, each conical wall having a center aligned with the predetermined axis, each conical wall having a wide and a narrow end, the reservoir areas being located near the wide ends, the opening located near the narrow wall. The centrifugal filter cartridge according to claim 5, characterized in that the adjacent conical walls have their narrow ends and their respective broad ends at opposite ends of the filter trap, so that the narrow end of an adjacent conical wall is near the wide end of the adjacent conical wall. The centrifugal filter cartridge according to claim 6, characterized in that it further includes a plurality of disc-shaped separating walls connected to the respective broad and narrow ends of the adjacent conical walls, each separating wall includes at least one of the openings. The centrifugal filter cartridge according to claim 1, characterized in that the filter trap includes a plurality of cylindrical trap walls, each providing a separate level, the plurality of conical trap walls being located concentric about the predetermined axis . The centrifugal filter cartridge according to claim 8, characterized in that each level includes a plurality of angularly spaced apart partition walls between the adjacent internal and external cylindrical trap walls, so that the level is separated into a plurality of trap chambers to include a first and last trap chambers, the internal adjacent cylindrical trap wall has an opening therethrough to receive adjacent internal level fluid, each partition wall includes an opening located near the internal adjacent wall to transmit sequentially fluid through the trap chambers from the first to the last chamber of the trap. 10. The centrifugal filter cartridge according to claim 9, characterized in that it further comprises intermediate trap chambers between the first and last chambers of the trap, wherein each intermediate trap chamber is defined between two adjacent separation walls, with an opening in a partition wall located near an end of the trap chamber. the trap and the outlet opening located in the other partition wall near the other end of the trap, whereby the fluid is adapted to move along the trap chamber between the ends of the trap. The centrifugal filter cartridge according to claim 9, characterized in that the filter trap is divided into at least two compartments of equal size, each compartment providing a separate flow path through the filter trap, including the trap of the filter means for filling at least two compartments of equal size in a substantially equal manner during filling with initial fluid of the trap. The centrifugal filter cartridge according to claim 1, characterized in that the housing includes upper and lower end plates, and a frame connected to the effective outer peripheries of the end plates and extending transversely between the outer peripheries of the plates. extreme to enclose the filter chamber. 13. The centrifugal filter cartridge according to claim 12, characterized in that the filter trap includes a trap element and upper and lower end caps, the ends of the trap element are saturated in the end layers with adhesive material. The centrifugal filter cartridge according to claim 12, characterized in that it further comprises a central tube connecting the upper and lower end plates, one end of the tube being threadedly connected to the lower end plate, a ring of retainer threadably connected to the other end of the tube and pressing the upper end plate against the lower end plate. 15. The centrifugal filter cartridge according to claim 14, characterized in that it further comprises at least one compressed spring of the upper end plate and the upper end cap to provide a space therebetween, which further comprises a conduit outlet that includes an outlet in the upper end cap, an outlet passage through the filter trap of an outlet through the outlet of the lower end plate. 16. The centrifugal filter cartridge according to claim 12, characterized in that the upper end plate includes a concentric bushing around the shaft and a surrounding discoidal portion connected by flanges, the inlet being defined between the bushing and the disk portion, thus that the cartridge is adapted to receive oil at a point deviated from the predetermined axis. 17. A centrifugal filter cartridge, adapted to rotate by means of the filtering fluid, characterized in that it comprises: an external housing having a predetermined axis of rotation, an inlet, an outlet, upper and lower end plates, and a frame connected to peripheries of the outer plates of the end plates, the frame extends transversely between the outer peripheries of the end plates to enclose a filter chamber between the end plates, the filter chamber being between the inlet and the outlet of the fluid communication of the inlet at the exit; a trap located in the filter chamber and surrounding the predetermined axis, with the inlet being fluidly connected to the outlet through the trap, the trap includes a plurality of levels, each level being located at a radial distance different from the predetermined axis of rotation each level including at least one reservoir area and at least one opening, at least one of the openings being located radially inward of the reservoir area for that level; and upper and lower end caps for the trap, the opposite axial ends of the trap being saturated with material in the upper and lower end caps. 18. The centrifugal filter cartridge according to claim 17, characterized in that at least one of the upper and lower end caps is integrally provided by at least one of the upper and lower end plates. 19. The centrifugal filter cartridge according to claim 17, characterized in that both of the upper and lower end caps are separate members of the upper and lower end plates. 20. The centrifugal filter cartridge according to claim 17, characterized in that the upper end cap and the upper end plate are spaced apart to provide a space therebetween, and where the entry is located on the upper end plate and the outlet is located in the lower end plate, and in that it also comprises: at least one outlet duct which has an inlet in the upper end cap for receiving oil from the space and one outlet through the outlet in the lower end plate. 21. The centrifugal filter cartridge according to claim 20, characterized in that it further comprises at least one radial seal acting on the lower end plate and the outlet conduit providing a sealed passage. 22. The centrifugal filter cartridge according to claim 20, characterized in that the outlet conduit is integrally provided by the trap. 23. The centrifugal filter cartridge according to claim 20, characterized in that the outlet conduit is provided separated by at least two outlets to be located in symmetrical relation about the predetermined axis. 24. The centrifugal filter cartridge according to claim 17, characterized in that the trap includes a wall surrounding the predetermined axis of rotation and wound in a spiral configuration about the predetermined axis of rotation, the wall includes a plurality of depressions formed therein. and a plurality of flanges formed between adjacent depressions, the openings being provided through the flanges to transfer oil to the next radial outer level. 25. The centrifugal filter cartridge according to claim 17, characterized in that the trap includes a plurality of conical walls, each providing a separate level, the plurality of conical walls are located side by side to include a conical wall radially outermost and a more internal conical wall, each conical wall having a center aligned with the predetermined axis, each conical wall having wide and narrow ends, the reservoir areas being located near the broad ends, the opening being located near the end narrow, and where the adjacent conical walls have their narrow ends and respective broad ends at opposite ends of the filter trap, so that the narrow end of an adjacent conical wall is near the wider or wider end of the other adjacent conical wall , and further includes a plurality of disk-shaped separating walls connected to the The respective wide and narrow ends of adjacent conical walls, each partition wall including at least one of the openings. 26. The centrifugal filter cartridge according to claim 17, characterized in that the trap includes a plurality of cylindrical trap walls, each providing a separate level, the plurality of concentric cylindrical trap walls being around the predetermined axis, and wherein each level includes a plurality of angularly spaced apart walls connected between the adjacent internal and external cylindrical trap walls, so that the level is separated into a plurality of trap chambers to include a first and last trap chambers, the adjacent internal cylindrical trap wall has an opening therethrough to receive fluid of the adjacent internal level, each partition wall includes an opening located near the internal adjacent wall to sequentially transmit fluid through the trap chambers of the first to the last chamber of the trap, and which further comprises intermediate trap between the first and last chambers of the trap, wherein each chamber of the intermediate trap is defined between two adjacent partition walls, having an opening in the partition wall located near one end of the trap and the outlet opening located in the other partition wall near the other end of the trap. the trap, whereby the fluid is adapted to move along the chamber of the trap between the ends of the trap. 27. The centrifugal filter cartridge according to claim 26, characterized in that the trap is divided into at least two compartments of equal size, each compartment providing a separate flow path between the passage and the filter trap, each compartment adapted to filling substantially the same during filling with initial fluid of the trap. 28. The centrifugal filter cartridge according to claim 17, characterized in that it comprises: a central tube connecting the upper and lower end plates, one end of the tube is threadably connected to the lower end plate, a retaining ring connected in a manner threaded to the other end of the tube and pressing the upper end plate against the lower end plate. 29. A centrifugal filter cartridge for mounting in a centrifugal housing to be rotated by the filter fluid, the centrifugal cartridge is characterized in that it comprises: an external housing having a predetermined axis of rotation, an inlet, an outlet, upper end plates and lower, and a frame connected to respective outer peripheries of the end plates, the frame extends transversely between the outer peripheries of the end plates to enclose a filter chamber between the end plates; a cartridge inlet on the upper end plate; a cartridge outlet in the outer housing near the lower end plate, the cartridge outlet being located at a distance greater than the predetermined axis of the cartridge inlet; and an outlet conduit provided within the outer housing, having an inlet in the filter chamber near the upper end plate to prevent drainage of most of the fluid from the filter chamber when the cartridge is free, with the inlet located radially inwardly of the frame at a radial distance from the predetermined axis that is greater than the radial location of the cartridge inlet. 30. The centrifugal filter cartridge according to claim 29, characterized in that it also comprises a filter trap located in the filter chamber, the inlet being fluidically connected to the outlet through the filter trap, the trap of the filter. The filter includes a plurality of levels, each level being located at a radial distance different from the predetermined axis of rotation, each level including at least one reservoir area and at least one aperture, at least one of the apertures being located radially inward of the area. of deposit for that level. 31. The centrifugal filter cartridge according to claim 30, characterized in that the outlet conduit is provided integrally by the filter trap. 32. The centrifugal filter cartridge according to claim 29, characterized in that the outlet conduit is provided by at least one tube projecting axially from the lower end plate. The centrifugal filter cartridge according to claim 32, characterized in that at least one tube includes an axially extending portion having an outlet through the outlet and a radially inwardly extending portion having the inlet, the axially extending portion and the radially inwardly extending portion are connected in an elbow joint. 34. The centrifugal filter cartridge according to claim 29, characterized in that the outlet is provided through the lower end plate. 35. The centrifugal filter cartridge according to claim 34, characterized in that it also comprises at least one seal acting on the lower end plate and the outlet duct, which provides a sealed passage of the outlet through the outlet . 36. The centrifugal filter cartridge according to claim 29, characterized in that the upper and lower end plates include central openings aligned with the predetermined axis, the upper end plate includes a central hub and a discoidal portion surrounding the central hub and connected to the central hub. central hub by a plurality of flanges, the cartridge inlet being defined by inlet holes between adjacent ridges, the discoidal portion and the central hub. 37. The centrifugal filter cartridge according to claim 36, characterized in that the lower end plate includes a conical surface surrounding the predetermined axis to facilitate alignment of the centrifugal cartridge with the intended centrifugal housing. 38. The centrifugal filter cartridge according to claim 36, characterized in that it further comprises a central tube generally concentric about the predetermined axis connecting the upper and lower end plates. 39. A centrifugal filter cartridge for mounting in a centrifugal housing to be rotated by the filter fluid, the centrifugal cartridge is characterized in that it comprises: an external housing having a predetermined rotation axis, upper and lower end plates, vertically separated, and a frame connected to the respective outer peripheries of the end plates, the frame extends transversely between the outer peripheries of the end plates to enclose the filter chamber between the end plates; a cartridge inlet on the upper end plate; a cartridge outlet in the outer housing near the lower end plate; an outlet conduit provided within the outer housing, having an inlet in the filter chamber near the upper end plate to prevent drainage of most of the fluid from the filtration chamber when the cartridge is free, the inlet being located radially into the frame at a radial distance from the predetermined axis that is greater than the radial location of the cartridge inlet; and at least one reservoir area in the filter chamber located radially outside the inlet in relation to the predetermined axis. 40. The centrifugal filter cartridge according to claim 39, characterized in that the upper end plate includes a concentric bushing around the shaft and a discoidal portion 1 5. surrounding connected by flanges, the annular shaped inlet being defined between the hub and the discoidal portion. 41. The centrifugal filter cartridge according to claim 40, characterized in that it further comprises a central tube connecting the upper and lower end plates, one end of the tube being threadably connected to the lower end plate, retaining ring connected in a manner ^ ft 10 threaded to the other end of the tube and pressing the upper end plate against the lower end plate. 42. The centrifugal filter cartridge according to claim 39, characterized in that it also comprises a localized filter trap 15 in the inner chamber, the filter trap provides a plurality of reservoir areas in multiple separate locations, the filter trap includes upper and lower end caps and a trap element, the trap element being connected to the end caps 20, the filter trap being secured in the filter chamber with the outlet duct extending through the filter trap. 43. The centrifugal filter cartridge according to claim 42, characterized 25 because it comprises at least one compressed spring of the upper end plate and the upper end cap to provide a space therebetween, the inlet being defined between the upper end cap and connected by an outlet passage through the filter trap towards the Output output through the lower end plate. 44. The centrifugal filter cartridge according to claim 42, characterized in that it also includes means for sealing the passage of the outlet conduit between the lower end plate and the filter trap. 45. A centrifugal filter cartridge having a predetermined axis of rotation for mounting in a centrifugal housing for rotating by means of the filter fluid, the centrifugal cartridge is characterized in that it comprises: upper and lower end plates, vertically spaced apart, each end plate including a central opening surrounding the predetermined axis; a frame connected to the respective outer peripheries of the end plates, the frame extends transversely between the outer peripheries of the end plates to enclose a filter chamber between the end plates; at least one conical surface on at least one of the end plates, at least one conical surface being provided in the corresponding central aperture in concentric alignment with the predetermined axis; an inlet and an outlet, the outlet being located farther from the predetermined axis than the inlet, the filter chamber being fluidically connected between the inlet and the outlet, the outlet having an inlet in the filter chamber at a radially inward location of the frame; and at least one reservoir area located between the entrance and exit of the frame to trap contaminants from the fluid. 46. The centrifugal filter cartridge according to claim 45, characterized in that it also comprises a central tube that connects the upper and lower end plates, one end of the tube being threadedly connected to the lower end plate, a ring of retainer threadably connected to the other end of the tube and pressing the upper end plate against the lower end plate. 47. The centrifugal filter cartridge according to claim 45, characterized in that the upper end plate includes a concentric bushing around the shaft and a surrounding discoidal portion connected by flanges, the inlet being defined between the bushing and the disk portion, thus that the cartridge is adapted to receive oil at a point deviated from the predetermined axis. 48. The centrifugal filter cartridge according to claim 45, characterized in that a conical surface is provided on each of the end plates. 49. A centrifugal filter cartridge having a predetermined axis of rotation for mounting in a centrifugal housing to be rotated by means of the filter fluid, the centrifugal housing has a lateral oil outlet to feed oil to the centrifugal cartridge at a radial distance from the predetermined axis, the centrifugal cartridge is characterized in that it comprises: an external housing having a predetermined axis of rotation, an outlet and a filter chamber , the end housing includes an upper end plate having a central hub and an outer flange connected by flanges between them; an annular shaped entry through the upper plate defined between the central hub and the outer flange, the external input to align with the lateral oil outlet, having internal and external diameters from the predetermined axis which are respectively smaller and more larger than the radial distance of the oil side outlet, being • the exit of the cartridge placed radially outwards 5 from the inlet with the filter chamber placed fluidically between the inlet and the outlet; and at least one reservoir area in the filter chamber for removing soot from the oil during rotation of the outer housing about the predetermined axis. B 10 50. The centrifugal cartridge according to claim 49, characterized in that it further comprises a handle connected to the upper end plate and projecting vertically therefrom, the handle has a clamping surface which is adapted to be manually held for the removal of a. Centrifugal cartridge used or exhausted from the centrifugal housing. 51. The centrifugal cartridge according to claim 50, characterized in that the handle has an axis of symmetry that coincides with the axis 20 predetermined. 52. The centrifugal cartridge according to claim 49, characterized in that the removal means comprise at least one reservoir area located radially outwardly from the entrance of the reservoir. 25 filter chamber towards the outlet. 53. The centrifugal cartridge according to claim 49, characterized in that the removal means comprise a filter trap located in the filter chamber, the inlet being fluidically disposed at the outlet through the filter trap, including the filter trap a plurality of levels, each level being located at a radial distance different from the predetermined axis of rotation, each level including at least one reservoir area and at least one opening, at least one of the openings being located radially inward of the reservoir area. that level. 54. The centrifugal cartridge according to claim 49, characterized in that it further comprises an outlet conduit provided inside the external housing, having an inlet in the filter chamber near the upper end plate to prevent drainage of the the filtration chamber when the cartridge is free, the inlet being located radially inwardly of the frame a radial distance from the predetermined axis which is greater than the radial location of the cartridge inlet. 55. The centrifugal cartridge according to claim 49, characterized in that the external surface of the inlet is radially outwardly when it extends vertically outwards to thereby guide the fluid towards the cartridge. 56. The centrifugal cartridge adapted to rotate by means of the filtering fluid, characterized in that it comprises: an external housing having a predetermined axis of rotation, an inlet, an outlet, and a filtration chamber between the inlet and the outlet, the outlet being placed radially out of the entrance; and at least one filtration level in the filtration chamber for filtering fluid, each level of filtration including a reservoir area and an exit, the reservoir area being located radially outwardly relative to the predetermined axis; and means for inhibiting the formation of waves in the fluid contained in each level of filtration during the filtration of the housing about the predetermined axis. 57. The centrifugal cartridge according to claim 56, characterized in that the means of inhibition are a plurality of radially extending spacing walls located at an angular spacing about the predetermined axis. 58. The centrifugal cartridge according to claim 56, characterized in that it also comprises a filter trap located in the filter chamber, the inlet being fluidically connected to the outlet through the filter inlet, including the filter trap a plurality of levels, each level being located at a radial distance different from the predetermined axis of rotation, each level including at least one deposit area, and at least one opening, at least one of the openings being located radially inward of the reservoir area for that level. 59. The centrifugal cartridge according to claim 58, characterized in that the filter trap includes a wall surrounding the predetermined axis of rotation and wound in a spiral configuration about the predetermined axis of rotation, whereby the spiral configuration eliminates the presence of circular fluid levels, thereby providing the means of inhibition. 60. The centrifugal cartridge according to claim 59, characterized in that the wall includes a plurality of depressions formed therein to provide reservoir areas and a plurality of ridges formed between adjacent depressions, the openings being provided between the ridges to transfer fluids to the reservoir. next level radially outward. 61. The centrifugal cartridge according to claim 58, characterized in that the filter trap includes a plurality of conical walls, each providing a separate level, the plurality of conical walls are located one inside the other to include a radially conical wall more external and a radially innermost conical wall, each conical wall having a center aligned with a predetermined axis, each conical wall having broad and narrow ends, the deposit areas are located near the broad ends, the opening is located near the end narrow, and where the means of inhibition are a plurality of radially extending separation walls located at an angular spacing about the predetermined axis, the partition walls extend through the conical walls. 62. The centrifugal cartridge according to claim 58, characterized in that the filter trap includes a plurality of cylindrical trap walls, each providing a separate level, the plurality of cylindrical trap walls are concentric located about the predetermined axis, and where the means of inhibition are a plurality of radially extending separating walls located at an angular spacing about the predetermined axis, the partition walls extend through the cylindrical walls. 63. The centrifugal cartridge according to claim 62, characterized in that the filter trap is divided into at least two compartments of equal size, each compartment providing a separate flow path through the filter trap, the filter trap includes means for filling at least two compartments of equal or substantially equal size during the initial fluid filling of the trap.