EP1196246A1 - Free-stream centrifuge, especially for cleaning the lubricant of an internal combustion engine - Google Patents
Free-stream centrifuge, especially for cleaning the lubricant of an internal combustion engineInfo
- Publication number
- EP1196246A1 EP1196246A1 EP00936891A EP00936891A EP1196246A1 EP 1196246 A1 EP1196246 A1 EP 1196246A1 EP 00936891 A EP00936891 A EP 00936891A EP 00936891 A EP00936891 A EP 00936891A EP 1196246 A1 EP1196246 A1 EP 1196246A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- housing
- centrifuge
- free jet
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
- B04B—CENTRIFUGES
- B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
- B04B9/08—Arrangement or disposition of transmission gearing ; Couplings; Brakes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
- B04B—CENTRIFUGES
- B04B5/00—Other centrifuges
- B04B5/005—Centrifugal separators or filters for fluid circulation systems, e.g. for lubricant oil circulation systems
Definitions
- the invention relates to a free jet centrifuge which, for. B. can be used for cleaning lubricating oil in an internal combustion engine, according to the preamble of claim 1.
- Free jet centrifuges of this type are known.
- a rotor of a centrifuge is proposed, the manufacture of which is suitable for large series. This consists of several tin pots which are connected to one another by flanging (see FIG. 1 of the document mentioned).
- This association has a central tube 30 into which bushes 31, 32 are pressed. These serve to rotatably support the centrifuge rotor on a housing shaft 16 and to limit the axial play of the rotor in the installation space.
- the rotor can oscillate between the axial limits of the housing, whereby due to the applied oil pressure and possibly an inclined position of the nozzles 28, it tends to rise in the housing.
- the valve 40 closes so that the passage of the oil in the centrifuge rotor is prevented.
- the rotor then comes to a standstill due to the bearing friction of the plain bearings.
- the bearing friction is increased by the fact that the centrifuge rotor lowers on the lower axial stop in the housing, which increases the bearing surface of the plain bearing.
- the described assembly of the rotor has a high level of complexity. This makes economical production difficult.
- the axial position of the rotor is not precisely defined during operation. Sudden pressure fluctuations can e.g. B. also lead to a stop of the rotor against one of the axial stops during operation. For this reason, they must be equipped with similarly favorable sliding properties as the radial area of the plain bearings.
- Another problem is influencing the run-on behavior of the centrifuge as soon as the oil supply is interrupted.
- the centrifuge should come to a standstill as quickly as possible.
- the kinetic energy of the rotor is reduced via the bearing friction.
- the bearing friction should be very low. The more the bearing friction is reduced, the longer the centrifuge runs.
- the object of the invention is to create a centrifuge with a rotor which at the same time achieves a good centrifuging result by realizing high speeds and has short run-on times after switching off. This object is solved by claims 1, 6 and 8.
- the free jet centrifuge according to the invention consists in a known manner of a rotor with an inlet and at least one drive nozzle which is also an outlet.
- the deposition area for the separated suspended matter of the fluid can z. B. be formed by the rotor shell.
- the housing serves to shield the rotor from the environment. This is necessary because the jet of the drive nozzles has to be caught. Any type of casing that protects the surroundings is to be understood as a housing in the sense of the invention. No separate housing has to be provided for the centrifuge. It is also conceivable to use the centrifuge e.g. B. to install in cavities of an internal combustion engine, which belongs to the oil circuit.
- the storage of the centrifuge rotor in the housing also enables it to rotate and limits the axial play of the rotor.
- a power source is provided in the free-jet centrifuge, which on the one hand is fixed in place in the housing of the centrifuge and on the other hand its force development acts on the rotor.
- This power source can, for. B. consist of a coil spring, the ends of which are each supported on the rotor bearing and in the housing, the spring being pretensioned.
- the force of the power source counteracts the axial forces that arise during rotor operation. This creates an equilibrium of forces between the power source and the rotor in operation. Within the scope of its axial freedom of movement, the rotor moves into the position of the equilibrium of forces, whereby it is not connected to any of the axial stops. This enables low-friction operation of the centrifuge at high speeds.
- the power source also acts as a buffer for pressure fluctuations that shift the balance of forces, but do not cause the rotor to rub against one of the axial stops.
- the power source presses the rotor against one of the axial stops. This creates a braking torque that can brake the rotor to a standstill. A long run-on is prevented, whereby z. B. no running noise of the centrifuge can be heard when the internal combustion engine is idling.
- the power source also has the positive effect that the bearing partners are kept under tension. This prevents the bearings from knocking when the centrifuge is rotated due to their bearing play, which can also cause unpleasant noises. In addition, the risk is avoided that damage occurs due to the striking of the bearings, which shorten the service life. This is particularly necessary when using roller bearings to support the rotor. But plain bearings also benefit from the shortened ones Follow-up times. In this operating state, the lubrication of the bearing is no longer completely guaranteed due to the low oil pressure. A long overrun would therefore lead to increased bearing wear.
- the external support from the power source will act in the direction of gravity. This is related to the typical installation position of oil centrifuges. In centrifuges according to the state of the art, gravity is the necessary counterforce for the axial forces that arise during rotor operation. By using the power source described, however, the need for a vertical installation position using the gravity of the rotor is no longer necessary. This can be completely replaced by the power source, which also z. B. an installation of the rotor with a horizontal axis of rotation is possible. This allows greater design freedom when using the free jet centrifuge z. B. in an internal combustion engine.
- the spring If, as described, the spring is used as a source of force, it develops a force which is dependent on the axial travel of the rotor in the housing in accordance with the spring characteristic.
- This is a particularly simple embodiment that creates a self-regulating system for the free jet centrifuge.
- the spring is designed in such a way that the resulting amount of spring force is always less than or equal to the amount of axial force generated by the rotor operation within the intended operating range.
- the operating range is defined by the speed of the rotor and the oil pressure. Only when the operating range is left downward does the spring force exceed the axial force of the rotor, so that it is pressed against one of its axial stops and braked.
- the power source can e.g. B. consist of a hydraulic cylinder that is controlled by a third party.
- an electromechanical drive e.g. B. a motor-transmission combination is conceivable.
- the pressure cans frequently used in the motor vehicle sector also provide a sensible solution for the externally actuated drive of the power source.
- the centrifuge With the help of external actuation, the centrifuge can be braked down from any operating state by pressing against the axial stop by activating the power source.
- Useful operating states in which braking of the rotor is sensible, result on the one hand in the idling state already described, and on the other hand in the event that an insufficient supply of the internal combustion engine with lubricating oil threatens.
- the externally operated power source can be used to switch off the centrifuge, so that the bypass flow of the oil required to operate the centrifuge is available directly for lubrication. This function is otherwise ensured by appropriate valves in the oil circuit, which can be dispensed with in the solution described. This results in an additional saving effect, which leads to a higher cost-effectiveness of the solution or outweighs the additional effort for the externally operated power source.
- a particularly favorable embodiment results in a free jet centrifuge which has a sliding bearing on one side as the bearing means, which is also the inlet. Lubrication then takes place through the liquid introduced.
- a roller bearing is used as the second bearing, which leads to extremely low friction losses. This is completely outside the liquid flow to be centrifuged.
- the power source is clamped between a support in the housing and the roller bearing, so that the roller bearing is axially displaceable. When the roller bearing is moved, the centrifuge rotor is moved at the same time. This axial movement is permitted in the plain bearing.
- the rolling bearing can, for. B. be attached to the rotor with its inner ring while the power source engages the outer ring.
- An alternative way of braking the rotor is to implement a thrust reverser. This is achieved by actuating nozzles on the centrifuge rotor, which enable a drive in the opposite direction to the normal direction of rotation.
- the nozzle heads of the centrifuge rotor can be rotated so that the thrust reversal can be achieved by rotating the nozzles by 180 °.
- Another possibility is the attachment of additional brake nozzles, the spray direction of which is opposite to that of the drive nozzles.
- the control of the nozzles can be controlled by the pressure in the rotor.
- a further alternative embodiment of the invention provides that a pair of friction surfaces is provided outside the bearing means, one of the friction partners being fixed in the housing and the other being fixed to the rotor.
- This pair of friction surfaces can be used as a brake.
- An advantageous possibility is to design the friction partners in a ring shape and to accommodate them in the area of one of the rotor lid surfaces and the housing.
- the function of this pair of friction surfaces is comparable to the axial stop of the bearing already described.
- the pair of friction surfaces replaces exactly this axial stop in the bearing, namely that which is opposite to the axial movement tendency of the rotor during operation. Outside the intended operating range of the rotor, it lowers on the friction pairing and is thereby braked.
- This process can be supported by a power source according to one of claims 1 to 5.
- the effect can be achieved solely through the force of gravity acting on the centrifuge rotor.
- the ideal material pairing can be selected for both tasks.
- the friction partners can be accommodated in the vicinity of the outer circumference of the rotor, as a result of which the braking torque is additionally increased by their geometric arrangement.
- the following materials in particular can be selected for the friction pairing for braking the rotor.
- Material of one friction partner PA (possibly glass fiber reinforced), POM, PTFE.
- Another advantageous embodiment of the invention is the arrangement of a
- Brake band in the housing which, for. B. can interact with the outer surface of the rotor.
- the braking effect described can be achieved by tightening the brake band.
- the rotor By providing the described means for braking the rotor, be it additional friction pairs or power sources for increasing the friction in the bearings, the rotor can be braked to a standstill from any operating state. This results in a possibility of reducing the flow through the centrifuge to a minimum, since the volume flow at the nozzles only reaches appreciable amounts at high speeds due to the dynamic pressures generated in the interior of the centrifuge. At standstill, the volume flow through the narrow nozzle bore is negligible. This means that valves for actuating and controlling the centrifuge can be completely saved, the leakage flow being accepted through the nozzle opening when the rotor is at a standstill. By saving the control valves, the efficiency of the centrifuge can be significantly increased.
- FIG. 2 shows the detail X from FIG. 1
- FIG. 3 shows the detail Y from FIG. 1
- FIG. 4 shows the schematic cross section of a centrifuge, the representation of perspective A - A according to FIG. 1 following and an additional brake nozzle being provided on the circumference and
- Figure 5 shows the cross section of a centrifuge with brake band, which is externally actuated by evaluating various motor parameters.
- a free jet centrifuge according to FIG. 1 has a housing 10 in which a rotor 11 is rotatably mounted using a slide bearing 12 and a roller bearing 13.
- the slide bearing 12 allows axial displacement of the rotor, which is immersed in this bearing with a central tube 14.
- Axial limitation in the direction of the plain bearing is ensured by friction surfaces 15a, 15b.
- the roller bearing 13 is fixedly connected to a nozzle 16 on the centrifuge rotor.
- the nozzle extends into an inner ring 17 of the rolling bearing.
- the outer ring 19 of the rolling bearing is fixed radially in a receptacle 18 in the housing.
- a displacement of the roller bearing 13 is possible in the axial direction, this being limited by a helical spring 20 acting on an outer ring 19 of the roller bearing.
- the spring has an abutment in a support 21 in the housing.
- the rotor 11 is pressed onto the friction surface 15b accommodated in the housing by the spring 20 with the friction surface 15a, which is attached to a cover surface 22 of the rotor. If the oil pressure rises in an inlet 23, the rotor acts like a hydraulic cylinder and rises in the slide bearing 12 as soon as the force resulting from the oil pressure exceeds the spring force.
- the oil passes through the central tube 14 into a separating chamber 24, from there into nozzle channels 25 and is sprayed into the housing through drive nozzles 26, from where it runs out through an outlet 27.
- the drive nozzles cause the rotor 11 to rotate, as a result of which the oil Chen suspended solids 28 are deposited on the deposition surfaces 29 of the rotor.
- a balance is established between the spring force of the spring 20 and the axial forces acting on the rotor 11, on which the axial position of the rotor depends. In the operating area, this axial position is above the axial stop formed by the friction surfaces 15a and 15b.
- the axial force on the rotor is mainly determined by the oil pressure present at the inlet 23. If this falls below a certain value which defines the lower limit of the operating range, the spring force of the spring 20 leads to a lowering of the rotor in such a way that the friction surfaces 15a, 15b touch and the rotor is braked to a standstill.
- Figure 2 shows an alternative way of arranging pairs of friction surfaces.
- the pair of friction surfaces does not necessarily have to consist of materials attached to the parts of the centrifuge for this purpose. It is also possible to use the material of the housing 10 and rotor 11 itself.
- friction surfaces 15c, 15d can be accommodated in the area of the slide bearing. In the manner described, these form the axial stop, the friction surfaces leading to an abrupt increase in the friction in the bearing as soon as the axial stop in the rotor comes into contact with the friction surfaces.
- Figure 3 shows a variant for the rolling bearing of the rotor without an additional power source.
- the roller bearing 19 is fixedly mounted in the housing 10.
- the connector 16 of the rotor 11 is axially displaceable in the inner ring 17 of the rolling bearing, a shoulder 30 limiting the axial movement.
- the gravity acting on the rotor 11 acts as a restoring force, which in the manner described is in equilibrium with the axial forces acting on the rotor.
- FIG. 4 shows a centrifuge consisting of the rotor 11 and the housing 10.
- the inlet 23 and the outlet 27 can be seen.
- the rotor is equipped with a brake nozzle 31.
- the nozzle channels 25 are equipped with valves 32, which are provided with a pressure actuation 33. The pressure actuation switches the valves in such a way that the brake nozzle 31 is activated below the operating pressure range and within the operating pressure range ches the drive nozzle 26 is unlocked. If the pressure drops z. B. at idle
- FIG. 5 shows a centrifuge in the representation corresponding to Figure 4.
- a brake band 34 is provided, which by a schematically illustrated pneumatic cylinder 35, the z. B. can also be formed by a vacuum can, operated externally.
- the pneumatic cylinder 35 By actuating the pneumatic cylinder 35, the brake band 34 is pressed against an outer wall 36 of the rotor. This creates a braking torque that depends on the pressure applied to the pneumatic cylinder.
- the pneumatic cylinder is controlled by an actuating valve 37, which is connected to a pressure accumulator 38.
- a control unit 39 is provided for switching the actuating valve, which, depending on the parameters such as speed n and oil pressure p of an engine 40, forwards the switching signal s to an actuating valve 37.
- the centrifuge can be brought to a standstill from any operating state.
- the drive nozzle 26 of the stationary centrifuge acts as a throttle, so that a valve for supplying the centrifuge with oil is not necessary.
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19933040A DE19933040A1 (en) | 1999-07-15 | 1999-07-15 | Free jet centrifuge, in particular for cleaning the lubricating oil of an internal combustion engine |
DE19933040 | 1999-07-15 | ||
PCT/EP2000/005598 WO2001005515A1 (en) | 1999-07-15 | 2000-06-17 | Free-stream centrifuge, especially for cleaning the lubricant of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1196246A1 true EP1196246A1 (en) | 2002-04-17 |
EP1196246B1 EP1196246B1 (en) | 2003-10-29 |
Family
ID=7914798
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00936891A Expired - Lifetime EP1196246B1 (en) | 1999-07-15 | 2000-06-17 | Free-stream centrifuge, especially for cleaning the lubricant of an internal combustion engine |
Country Status (5)
Country | Link |
---|---|
US (1) | US6620090B2 (en) |
EP (1) | EP1196246B1 (en) |
AT (1) | ATE252947T1 (en) |
DE (2) | DE19933040A1 (en) |
WO (1) | WO2001005515A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10148405A1 (en) * | 2001-10-01 | 2003-04-10 | Otto Altmann | Double-walled cyclone for fluids purefication flows fluid spirally down to outlet past walls slotted to transfer contained impurities to outer walled volume and separate collectors. |
US7065043B2 (en) | 2001-12-24 | 2006-06-20 | Innomedia Pte Ltd. | Method and system for connecting to a proxy server with the lowest workload through querying a load monitor |
US6766967B2 (en) * | 2002-05-07 | 2004-07-27 | Gp Companies, Inc. | Magnet-driven rotary nozzle |
US7182724B2 (en) * | 2004-02-25 | 2007-02-27 | Fleetguard, Inc. | Disposable centrifuge rotor |
US8500042B2 (en) * | 2008-01-24 | 2013-08-06 | Hydra-Flex Inc. | Configurable rotary spray nozzle |
WO2017053267A1 (en) | 2015-09-24 | 2017-03-30 | Cummins Filtration Ip, Inc. | Utilizing a mechanical seal between a filter media and an end cap of a rotating filter cartridge |
DE202016100479U1 (en) * | 2016-02-01 | 2017-05-04 | Reinz-Dichtungs-Gmbh | oil separator |
DE102017202069A1 (en) | 2017-02-09 | 2018-08-09 | BRUSS Sealing Systems GmbH | Active oil separator |
WO2018236921A1 (en) | 2017-06-20 | 2018-12-27 | Cummins Filtration Ip, Inc. | Axial flow centrifugal separator |
US20220349324A1 (en) * | 2019-06-12 | 2022-11-03 | Innio Jenbacher Gmbh & Co Og | Internal combustion engine |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1302031A (en) * | 1917-11-28 | 1919-04-29 | Sharples Specialty Co | Centrifugal machine. |
GB581622A (en) * | 1944-09-20 | 1946-10-18 | Morris Motors Ltd | An improved centrifugal lubricating oil cleaner |
GB668766A (en) * | 1950-01-06 | 1952-03-19 | Albion Motors Ltd | Improvements in or relating to centrifugal oil cleaners |
FR1070737A (en) * | 1952-03-04 | 1954-08-10 | Albion Motors Ltd | Centrifugal Oil Purifiers Improvements |
DE1918531A1 (en) * | 1968-04-12 | 1969-12-18 | Sorvall Inc Ivan | Turbine drive device |
DE2314369B2 (en) * | 1973-03-22 | 1976-10-14 | Shin Nippon Machinery Co., Ltd., Tokio | HANGING CENTRIFUGAL SEPARATOR |
US4106689A (en) * | 1977-04-06 | 1978-08-15 | The Weatherhead Company | Disposable centrifugal separator |
US4165032A (en) * | 1977-06-17 | 1979-08-21 | Dana Corporation | Disposable centrifugal separator with baffle means |
US4346009A (en) * | 1979-10-09 | 1982-08-24 | Hastings Manufacturing Co. | Centrifugal spin-on filter or separator |
US4284504A (en) * | 1979-10-09 | 1981-08-18 | Hastings Manufacturing Company | Centrifugal spin-on filter or separator and method of making and assembling the same |
SU1017390A1 (en) * | 1982-01-14 | 1983-05-15 | Ярославский Ордена Ленина И Ордена Октябрьской Революции Моторный Завод | Liquid cleaning centrifugal machine |
SU1639765A1 (en) * | 1988-03-28 | 1991-04-07 | Государственный Всесоюзный Научно-Исследовательский Технологический Институт Ремонта И Эксплуатации Машинно-Тракторного Парка | Centrifugal oil cleaner |
DE4100414C1 (en) * | 1991-01-09 | 1992-04-23 | Erich 5010 Bergheim De Wagner | |
DE4444344C1 (en) * | 1994-12-14 | 1996-04-04 | Hengst Walter Gmbh & Co Kg | Centrifugal sepn. of solids from liqs. |
GB2302049A (en) * | 1995-06-10 | 1997-01-08 | Glacier Metal Co Ltd | Centrifugal separator |
GB9526523D0 (en) * | 1995-12-23 | 1996-02-28 | Glacier Metal Co Ltd | Centrifugal separator |
GB9703685D0 (en) * | 1997-02-21 | 1997-04-09 | Glacier Metal Co Ltd | Centrifugal separator |
DE19911212A1 (en) * | 1999-03-12 | 2000-09-14 | Mann & Hummel Filter | Shaft bearing with spherical cap |
-
1999
- 1999-07-15 DE DE19933040A patent/DE19933040A1/en not_active Withdrawn
-
2000
- 2000-06-17 WO PCT/EP2000/005598 patent/WO2001005515A1/en active IP Right Grant
- 2000-06-17 AT AT00936891T patent/ATE252947T1/en not_active IP Right Cessation
- 2000-06-17 EP EP00936891A patent/EP1196246B1/en not_active Expired - Lifetime
- 2000-06-17 DE DE50004263T patent/DE50004263D1/en not_active Expired - Lifetime
-
2002
- 2002-01-15 US US10/045,030 patent/US6620090B2/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0105515A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE50004263D1 (en) | 2003-12-04 |
DE19933040A1 (en) | 2001-01-18 |
ATE252947T1 (en) | 2003-11-15 |
US20020107132A1 (en) | 2002-08-08 |
US6620090B2 (en) | 2003-09-16 |
EP1196246B1 (en) | 2003-10-29 |
WO2001005515A1 (en) | 2001-01-25 |
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