EP2090758A1 - Schmierkreislauf - Google Patents

Schmierkreislauf Download PDF

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Publication number
EP2090758A1
EP2090758A1 EP09151591A EP09151591A EP2090758A1 EP 2090758 A1 EP2090758 A1 EP 2090758A1 EP 09151591 A EP09151591 A EP 09151591A EP 09151591 A EP09151591 A EP 09151591A EP 2090758 A1 EP2090758 A1 EP 2090758A1
Authority
EP
European Patent Office
Prior art keywords
oil
valve
combustion engine
circuit
internal combustion
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.)
Withdrawn
Application number
EP09151591A
Other languages
English (en)
French (fr)
Inventor
Christian Noiret
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
PSA Automobiles SA
Original Assignee
Peugeot Citroen Automobiles SA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Peugeot Citroen Automobiles SA filed Critical Peugeot Citroen Automobiles SA
Publication of EP2090758A1 publication Critical patent/EP2090758A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity

Definitions

  • the invention relates to a lubrication circuit of an internal combustion engine.
  • the circuit described in the present invention has a device for regulating the pressure of the oil despite the variations in viscosity of the latter.
  • an internal combustion engine In operation, an internal combustion engine involves many moving mechanical elements. To prevent wear of moving parts, as well as to limit friction and associated energy losses, these parts must be lubricated.
  • the engine therefore comprises a lubricant circuit responsible for supplying oil to the various components of the engine to be lubricated.
  • At least one positive displacement pump ensures adequate oil circulation in the circuit. It may be a pump mechanically actuated by the engine, or an electric pump, or a set of several pumps of similar or different technologies.
  • this valve In order to regulate the pressure in the circuit to a sufficient but not excessive level, there is traditionally a discharge valve in parallel with the pump, which makes it possible to return the excess oil in the circuit upstream of the oil pump.
  • this valve which can be a ball valve closed by a calibrated spring, opens, allowing a return of the oil upstream of the pump and a regulation of the pressure to the desired level .
  • the viscosity of the oil traditionally used for the lubrication of an internal combustion engine varies significantly with its temperature.
  • the oil circuit relief valve is sized to perform its function most of the time, i.e. within a given oil viscosity range corresponding to the viscosity of the hot engine oil. .
  • the viscosity of the oil being higher at low temperature, when the oil is cold, the valve does not allow sufficient opening to return enough oil upstream of the pump and thus maintain the oil pressure close to the pressure hot regulation.
  • the cold oil pressure is unnecessarily high in the circuit, which generates significant energy losses and an increase in engine consumption. Note that the increase of the passage section of the valve is not a solution, because the regulation of hot pressure would then be effective.
  • KUBOTA adds a second discharge valve in parallel with the first valve.
  • This second valve is actuated by a thermostatic element.
  • this valve has a virtually “all or nothing" opening, which is incompatible with a fine regulation of the pressure in the circuit.
  • this solution only functions correctly over a reduced oil viscosity range, thus for an extremely reduced operating temperature range.
  • the object of the present invention is to provide a device allowing a fine regulation of the oil pressure in the lubricant circuit, over the entire operating temperature range of an engine, that is to say generally from -30 ° C to 140 ° C, and therefore over the entire viscosity range of the oil as part of its use for the lubrication of an internal combustion engine.
  • the solution to this problem is to use a special constitution device positioned in a branch of parallel unloading of the discharge valve, allowing, depending on the temperature of the oil or the pressure in the circuit, to return a suitable portion of the oil upstream of the pump, to allow the discharge valve to play are fine regulating role of the pressure in the circuit.
  • the device in parallel with the discharge valve can be, according to different variants of the invention, a variable-section valve or a solenoid valve.
  • a valve with a variable section is thus positioned in parallel with the discharge valve, in a branch of load shedding of the valve.
  • the valve in play consists of two chambers, these chambers being at least partially contained in one another or adjacent, the first chamber being in communication with the oil circuit on one side of the pump, typically downstream (respectively upstream), and the second chamber being in communication with the circuit on the other side of the pump, typically upstream (respectively downstream).
  • the two chambers are in communication via one or more orifices substantially slit-shaped.
  • a piston more or less discovers this orifice, thus varying the passage section between the two chambers.
  • the piston is actuated in the invention by a thermostatic element, whose expansion is substantially proportional to the temperature. Its position therefore varies almost linearly with temperature. If the gap between the two chambers had a constant width (rectangular shape seen from the front), the passage surface would then evolve in proportion to the temperature of the oil. However, the viscosity of the oil does not evolve linearly with temperature, but substantially hyperbolic, it is preferable to adapt the shape of the slot so that the passage section changes proportionally to the viscosity of the oil and not at its temperature.
  • the slot may therefore have a substantially trapezoidal shape, seen from the front, or a more elaborate form (hyperbolic section) allowing a perfect match between the opening of the valve and the viscosity of the oil.
  • a solenoid valve is positioned in parallel with the discharge valve.
  • the solenoid valve is controlled by a control system.
  • the solenoid valve can operate "all or nothing", that is to say do not have a variable section.
  • the regulation of the amount of oil returned by the solenoid valve upstream of the pump is achieved by imposing on the valve a succession of opening and closing.
  • the section of the valve is known, or, for better accuracy, a calibrated fitting can be positioned in the branch of the circuit.
  • the command applied to the solenoid valve can be predetermined according to the conditions of speed and oil temperature, that is to say with an open loop control system.
  • the RCO control will be performed in closed loop.
  • the circuit must have a proportional pressure sensor, which gives the control system of the valve information on the pressure in the circuit.
  • the pressure sensor is positioned in the lubrication circuit at the engine inlet.
  • the oil circuit of an internal combustion engine comprises in particular a main branch passing through an oil tank 1 serving as a reservoir for containing the lubricating oil 2, and a pump 3 ensuring the circulation of the oil 2 in the circuit .
  • a pump 3 ensuring the circulation of the oil 2 in the circuit .
  • the latter therefore generates a pressure difference between the upstream part 5 of the main branch and the downstream part 6 of the main branch, with respect to said pump.
  • the passage section of this valve ensures good regulation when the lubricating oil is hot. When cold, the viscosity of the oil may be too great for the valve to properly perform its function.
  • the figure 9 shows us how much the viscosity of the oil is dependent on its temperature. On the abscissa is the temperature of the oil considered in degrees Celsius (° C), the ordinate is carried the viscosity of this oil in centipoises (cPs) according to a logarithmic scale.
  • the line curve continuous corresponds to an automotive oil type 10W-40, while the dotted line corresponds to a type 5W-30 automotive oil.
  • an internal combustion engine can be operated throughout this temperature range, that is -30 ° C during a cold start in extreme conditions at 140 ° C hot .
  • the only discharge valve 4 can not be sized to ensure a fine regulation of the oil pressure over all of this range of temperature and viscosity, it is proposed in the invention shown figure 2 to provide the circuit of a load shedding branch 11 in parallel with the discharge valve 4 and to equip this shedding branch 11 with a device 7 for unloading the discharge valve 4 from an adequate part of the oil to return upstream of the pump 3 to allow a fine regulation of the oil pressure in the lubricant circuit by the valve 4, and this over the entire operating temperature range of an engine, that is to say generally say -30 ° C to 140 ° C.
  • variable section valve 71 is provided in the lubricating circuit in parallel with the discharge valve 4.
  • variable section valve is actuated by a thermostatic element 8.
  • valve 71 When cold, the valve 71 is open and closes as the temperature of the oil rises. When the oil is hot enough, the valve is completely closed, and only the relief valve 4 regulates the pressure of the oil in the circuit.
  • the figure 4 presents an optional embodiment of this variant of the invention.
  • the circuit in the branch incorporating the variable-section valve 71 that is to say the branch parallel to the discharge valve 4, is associated with a safety solenoid valve 9 making it possible to close this branch in case blocking valve of the variable section 71, which may for example be caused by a failure of the thermostatic element 8.
  • a blocking of the variable section valve 71 in the open position would prevent obtaining sufficient pressure to the good lubrication of the hot engine, which would jeopardize its proper functioning and could quickly lead to a mechanical failure, or even destruction.
  • the safety solenoid valve 9 if the pressure detected in the downstream circuit 6 of the pump 3 is low, falls, or barely established, the safety solenoid valve 9 is closed.
  • variable opening valve device 71 One of the major points of this variant of the invention is the adoption of a variable opening valve device 71.
  • Known devices performing this type of function are often complex control, or may be influenced by the level sudden pressure.
  • variable opening valve thus proposed consists of two chambers 711 and 712 located respectively downstream and upstream of the oil pump 3.
  • An orifice 713 allows communication between these two chambers.
  • a piston 714 makes it possible to more or less obstruct this orifice 713.
  • the piston 714 is thus moved in translation in the chamber 711 by the action of a thermostatic element 8.
  • a thermostatic element 8 Such an element is perfectly known in the prior art. This is usually a simple piece made of a material that expands under the effect of temperature.
  • the orifice 713 may have an oblong shape. One can thus speak of slot to designate the orifice 713.
  • variable opening valve is open.
  • the piston 714 completely uncovers the orifice 713. This is the configuration of the valve when the oil is cold and therefore highly viscous.
  • the oil has begun to heat, but is not sufficiently hot and fluid that the only relief valve 5 is sufficient to satisfactorily regulate the pressure in the circuit.
  • the valve has a reduced passage section with respect to the figure 5 but is not yet completely closed.
  • the orifice 713 is partially covered by the piston 714.
  • the figure 9 shows that the viscosity variation of the oil as a function of its temperature is absolutely not proportional. However, it is desired that the passage section of the variable opening valve (section of the orifice 713 discovered by the piston 714) varies proportionally to this viscosity.
  • the shape of the orifice 713 ' is adapted to respond to this constraint.
  • the passage section first evolves slowly, while the viscosity evolves rapidly. The higher the temperature of the oil rises, the more the passage section will grow rapidly because of its shape.
  • the proposed device makes it possible to effectively vary the passage section in proportion to the evolution of the viscosity of the oil.
  • said discharge valve 4 can then correctly play its role of pressure regulator despite the high viscosity of the oil.
  • a solenoid valve 72 is arranged in the lubrication circuit, in parallel with the discharge valve 4.
  • This solenoid valve 72 is controlled by a control means 721, which can control the opening and closing of the valve 72.
  • the control means 72 can control the opening and closing of the valve 72 in an open loop, according to criteria of oil temperature and engine speed.
  • control means 721 can control the opening and closing of the valve 72 in an open loop with a control of the "RCO” type (Cyclic Opening Ratio), according to a map predetermined.
  • RCO Cyclic Opening Ratio
  • control means 721 can control the opening and closing of the valve 72 in a closed loop with a "RCO" type control (Cyclic Opening Ratio), according to a third embodiment of this second variant.
  • a pressure information in the circuit obtained by a proportional pressure sensor, preferably positioned in the circuit between the oil filter and the engine.
  • the figure 10 represents the result achieved by the present invention on a typical automotive application.
  • On the abscissa is the engine speed in revolutions per minute, the ordinate the pressure of the oil in bar in the circuit downstream of the pump.
  • the curve with diamonds corresponds to the pressure of the hot oil, that is to say when the optimum operating temperature of the engine has been reached and is regulated by the cooling circuit.
  • the relief valve 4 plays its regulating role and makes it possible to stabilize the oil pressure in the circuit at a desired and adequate level, here of the order of 4 bars.
  • This pressure curve represents an ideal curve, which one seeks to reproduce whatever the viscosity of the oil.
  • the curve with squares corresponds to the pressure of the cold oil, that is to say with an oil at 20 ° C in our example, without the invention, that is to say in the configuration presented. to the figure 1 .
  • the relief valve does not have a sufficient section to allow passage of the amount of oil required to regulate the pressure of the circuit. In fact, at low speeds, the pressure is set at an unnecessarily high level. energy dissipated in the pump and in the circuit is then important, which generates overconsumption of the engine.
  • the curve with triangles corresponds to the pressure of the cold oil in a circuit according to the invention, as shown in FIG. figure 6 .
  • the pressure is at a level slightly higher than it is hot. This is due to the pressure drops in the branch of the circuit presenting the variable opening valve in parallel with the discharge valve.
  • the invention makes it possible to follow a pressure profile close to the ideal. As the oil temperature increases and its viscosity decreases, the variable opening valve will close. The pressure will then gradually reach the hot pressure profile.
  • the invention thus described thus makes it possible to maintain an adequate pressure in the circuit in all operating situations of the engine, and over the entire typical working range of oil temperature and viscosity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP09151591A 2008-02-13 2009-01-29 Schmierkreislauf Withdrawn EP2090758A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0850891A FR2927358B1 (fr) 2008-02-13 2008-02-13 Circuit de lubrification.

Publications (1)

Publication Number Publication Date
EP2090758A1 true EP2090758A1 (de) 2009-08-19

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Family Applications (1)

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EP09151591A Withdrawn EP2090758A1 (de) 2008-02-13 2009-01-29 Schmierkreislauf

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EP (1) EP2090758A1 (de)
FR (1) FR2927358B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2602485A1 (de) * 2011-12-05 2013-06-12 MAN Truck & Bus AG Einstellvorrichtung, insbesondere für Kraftfahrzeuge

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102758767A (zh) * 2012-07-20 2012-10-31 安徽江淮汽车股份有限公司 柴油马鞍型油箱的油路控制***

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5339776A (en) * 1993-08-30 1994-08-23 Chrysler Corporation Lubrication system with an oil bypass valve
JPH0893430A (ja) * 1994-09-27 1996-04-09 Nissan Motor Co Ltd 内燃機関の潤滑システム
JPH0988533A (ja) * 1995-09-26 1997-03-31 Tokyo Buhin Kogyo Kk エンジン潤滑油供給装置
US20020172604A1 (en) * 2001-05-17 2002-11-21 Berger Alvin Henry Variable pressure oil pump
JP2004108157A (ja) 2002-09-13 2004-04-08 Kubota Corp エンジンの強制潤滑装置の油圧調整装置
DE102006019086A1 (de) * 2006-04-23 2007-10-31 Att Automotivethermotech Gmbh Verfahren und Vorrichtung zur aktiven Öltemperierung bei Kraftfahrzeugen mit Verbrennungskraftmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5339776A (en) * 1993-08-30 1994-08-23 Chrysler Corporation Lubrication system with an oil bypass valve
JPH0893430A (ja) * 1994-09-27 1996-04-09 Nissan Motor Co Ltd 内燃機関の潤滑システム
JPH0988533A (ja) * 1995-09-26 1997-03-31 Tokyo Buhin Kogyo Kk エンジン潤滑油供給装置
US20020172604A1 (en) * 2001-05-17 2002-11-21 Berger Alvin Henry Variable pressure oil pump
JP2004108157A (ja) 2002-09-13 2004-04-08 Kubota Corp エンジンの強制潤滑装置の油圧調整装置
DE102006019086A1 (de) * 2006-04-23 2007-10-31 Att Automotivethermotech Gmbh Verfahren und Vorrichtung zur aktiven Öltemperierung bei Kraftfahrzeugen mit Verbrennungskraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2602485A1 (de) * 2011-12-05 2013-06-12 MAN Truck & Bus AG Einstellvorrichtung, insbesondere für Kraftfahrzeuge

Also Published As

Publication number Publication date
FR2927358A1 (fr) 2009-08-14
FR2927358B1 (fr) 2010-02-12

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