EP3292282B1 - Device for pressure regulation in an oil pump - Google Patents
Device for pressure regulation in an oil pump Download PDFInfo
- Publication number
- EP3292282B1 EP3292282B1 EP16722786.7A EP16722786A EP3292282B1 EP 3292282 B1 EP3292282 B1 EP 3292282B1 EP 16722786 A EP16722786 A EP 16722786A EP 3292282 B1 EP3292282 B1 EP 3292282B1
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- EP
- European Patent Office
- Prior art keywords
- pressure
- oil
- control
- piston
- pump
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/18—Pressure
- F04C2270/185—Controlled or regulated
Definitions
- the invention relates to a device for pressure control of an oil pump, having the features of the preamble of claim 1.
- the device for pressure control serves to adapt the delivery rate of the oil pump and / or the oil pressure of the oil pump provided to the changing needs of the lubrication system of the internal combustion engine. It is preferable to avoid unnecessarily high oil pressures to keep the drive power required to drive the oil pump low.
- the oil pump has a drive gear fixed on a drive shaft and a shift gear meshing with the drive gear.
- the sliding gear is moved axially, so that by changing the meshing width, the oil flow rate is changed.
- the sliding gear is mounted on a non-rotating bolt which carries a sliding piston and a spring piston. This composite forms a displacement unit.
- the displacement unit is constantly applied to the displacement piston with oil pressure, while counteracting the spring piston, a piston spring and an acting in the spring chamber, controllable control pressure make the flow control.
- the control of the control pressure is carried out via a control piston.
- the control piston and the spring chamber are connected to each other via a control bore.
- the control piston is designed as a stepped piston and has three active surfaces.
- the control piston has a first active surface, wherein an oil pressure is constantly applied to the first active surface.
- the second effective surface is additionally acted upon by two control devices with oil pressure or pressure relieved to exert an additional force on the control piston.
- the third active surface is formed by a control pin, wherein by means of the third active surface or by means of the control pin, the control bore can be opened and closed, whereby the control pressure is controlled.
- the oil pressure can be adjusted in at least two control pressure levels.
- the controllable by the drive devices with a variable force control piston causes the associated adjustment of the flow rate control device.
- a control spring acts on the control piston.
- the first drive device has a first control valve.
- the first control valve is designed as a speed-dependent centrifugal force valve with a control piston and a switching piston spring.
- the switching piston and the switching piston spring are arranged within a conveyor gear.
- the switching piston has in its axis an angular offset to the radial centrifugal force direction.
- the oil pressure for pressurizing the active surfaces of the control piston is branched off behind an oil filter. After crossing a switching speed of, for example, 2500 revolutions per minute, the switching piston is moved by centrifugal force against the switching piston spring in an outer end position. At these high speeds, the oil pressure is increased to an oil pressure level of, for example, 5.0 bar, wherein a pressure relief of the second effective area of the control piston takes place.
- a second drive device is provided.
- This second drive device has a second control valve in the form of an electrovalve.
- a control channel is released for oil pressure reduction, whereby a pressure load with the oil pressure of the second effective surface is caused.
- both active surfaces are oil pressure loaded, so that the control piston already at 2.5 bar oil pressure - the first control pressure stage - exerts its control function and provides the appropriate control pressure for flow control. If the solenoid valve is de-energized, the oil pressure supply to the control channel and thus to the second effective area is interrupted and via a discharge port on the solenoid valve, a pressure relief of the second effective area is caused.
- This device for pressure control of the oil pump is not yet optimally formed.
- the set control pressure level depends on the centrifugal force and thus depends on the speed of the drive gear. At high speeds of the drive gear, the higher control pressure level is selected.
- the structure of the drive gear with the arranged in the drive gear shift piston is complex to manufacture and assemble. Furthermore, the structure of the displacement unit is complicated.
- a device and a method for controlling a lubricating oil pressure of an internal combustion engine with an oil pump and with a control valve or two control valves or Abêtventilen and with a control valve is known.
- Either two parallel shut-off valves are provided, one of which is designed for a high pressure level and one for a low pressure level.
- the shut-off valve device comprises exactly one shut-off valve whose working piston has two active surfaces.
- the shut-off valve preferably has a first input for a first control line and a second input for a second control line, which can be acted upon by a control pressure depending on the pressure level to be set.
- bypass in Ab horrventil between an input and an output for pumped by the oil pump lubricating oil in Essentially arranged perpendicular to a displacement device of the working piston.
- the bypass connects the pressure side, ie the outlet, with the oil sump, which in turn feeds the inlet or the suction side of the oil pump.
- a bypass by means of the corresponding control piston can be opened and closed, wherein the bypass connects a pressure side of the oil pump with a suction side of the oil pump.
- Out DE 101 41 786 A1 is another device for controlling the lubricating oil pressure of an internal combustion engine with an oil pump known.
- An oil pressure valve associated with the oil pump opens and closes depending on the oil pressure a bypass between the pressure side and the suction side of the oil pump.
- variable displacement oil pump used has an inlet, an outlet and a first control chamber and a second control chamber.
- the supplied oil pressure is now adjusted by a displacement unit of the oil pump in response to the pressure in the first and second control chamber. It is described the use of piston cooling nozzles.
- the invention is therefore based on the object, the generic type device for pressure control of the oil pump in such a way and further, so that the structure of the device is simplified.
- This object of the invention is based is achieved by a device for pressure control of the oil pump, with the features of claim 1.
- the control of the oil pump is effected in that by means of the control piston, a bypass can be opened and closed, wherein the bypass connects a pressure side of the oil pump with a suction side of the oil pump.
- the oil pump is designed as an internal gear pump or as a gerotor pump. Through the bypass is easily a pressure control of the internal gear pump or the gerotor pump with at least two pressure levels possible.
- the toothed ring pump preferably has a trochoid toothing, wherein a centrally mounted drive gear drives an outer eccentrically mounted toothed ring. This results in the pump shrinking and enlarging spaces that produce the suction and conveying effect.
- the drive gear is drivingly coupled to the crankshaft.
- the bypass is closed or opened.
- the pump outlet pressure is applied to the third effective area.
- On the first active surface and the second effective surface acts a dependent on the oil pressure force.
- the control piston is spring loaded. The forces acting on the active surfaces are opposite to the spring force.
- the control piston is designed as a sum piston.
- When the bypass is open the pump outlet pressure is lowered. From a certain piston position, oil flows back internally via the bypass from the pressure side to the suction side of the oil pump. The pump outlet pressure or the oil pressure is reduced as needed. This results in a control of the control piston.
- only the pump outlet pressure acts on the third effective area, which limits the maximum pressure. In operation, the sum of both pressures on the first and second effective area regulates a fixed oil pressure.
- the energy requirement for the oil supply can be reduced as needed and, on the other hand, at least one piston cooling nozzle can be actively switched via the oil pressure.
- several piston cooling nozzles are switched as a function of the switching position of the control valve and thus in dependence on the selected pressure level. In a high-pressure stage, the at least one piston cooling nozzle is activated, and in a low-pressure stage, the at least one piston cooling nozzle is deactivated.
- a first effective area of the control piston acts an oil pressure, namely in particular a so-called gallery pressure.
- a control channel can be opened and closed, which releases a second effective area of the control piston.
- the oil pressure acting on the first effective area is in particular lower than the pump outlet pressure.
- the oil pressure or gallery pressure for acting on the first and second active surfaces is preferably branched off behind an oil filter and behind an oil cooler. This oil pressure can be referred to as gallery printing.
- the control valve is preferably designed as an electromagnetically actuated control valve.
- the control valve is formed by an on / off valve. This makes it possible to choose the different pressure levels regardless of the input speed of the oil pump.
- the electromagnetic control valve is preferably disposed on a housing of the oil pump, wherein the control channel extends within the housing.
- the control valve is arranged externally accessible on the housing of the oil pump.
- the control piston is arranged within the housing of the oil pump.
- a high pressure stage is realized when the control valve is de-energized.
- the control channel is blocked.
- the control channel is connected via the control valve with a line to the oil sump, whereby the second effective area is depressurized.
- the second active surface is not acted upon by the oil pressure.
- the oil flows only to the first effective area.
- On the first effective surface acts a dependent of the oil pressure force, which can move the piston against the spring force when the oil pressure increases. From a certain piston position, oil flows back through the bypass from the pressure side to the suction side of the oil pump, which limits the pump output pressure and, in the case of a cold start, the maximum oil pressure.
- a low pressure stage is realized when the control valve is energized, wherein the control valve is open to the control channel and thus to the second effective area.
- the oil flows through the control channel to the second effective surface.
- the control channel is open.
- the first and the second active surface are acted upon by the oil pressure against the force acting on the control piston spring force.
- control piston has further active surfaces, which can be activated or acted upon via further channels or control channels.
- FIG. 1 schematically a device 1 for pressure control of an oil pump 2 is shown.
- Fig. 2 to 4 show a corresponding oil pump and a part of the device 1.
- the oil pump 2 delivers oil from an oil pan 3.
- the oil pan 3 forms an oil sump.
- the device 1 now has a control piston 4 and a control valve 5.
- the control piston 4 By means of the control piston 4 at least two pressure levels can be controlled, namely a low pressure stage and a high pressure stage.
- the control piston 4 has for this purpose a first active surface 6, a second active surface 7 and in particular a third active surface 8.
- At the first active surface 6 is an oil pressure, which is provided by an oil pressure line 9.
- the oil pressure line 9 opens into a chamber 10, wherein the chamber 10 is bounded on the one hand by the active surface 6 of the control piston.
- the oil pump 2 delivers the oil from the oil pan 3 through a chamber 12 and provides a pump outlet pressure.
- the pump outlet pressure is applied to a port of the chamber 12 and an oil line 11 connected thereto.
- This oil line 11 may extend in particular in the housing of the oil pump 2.
- This flow of the oil pump 2 is supplied via the oil line 11 an oil filter ⁇ F and an oil cooler ⁇ K. Behind the oil cooler ⁇ K the oil pressure is branched off at an oil pressure line 16. This oil pressure can also be called gallerietik.
- the oil pressure is lower than the pump outlet pressure due to pressure losses via the oil filter ⁇ F and the oil cooler ⁇ K.
- a control channel 13 for acting on the second active surface 7 with the oil pressure can be opened and closed.
- the control channel 13 connects the port A of the control valve 5 to the chamber 14 of the control piston 4.
- a further oil pressure line 15 is connected to a port P of the control valve 5.
- the oil pressure lines 9 and 15 are fed by the common oil pressure line 16.
- the oil pressure line 16 is at least partially formed in a crankcase 17.
- the control valve 5 is preferably designed as an electromagnetic control valve 5. This has the advantage that the two pressure stages can be selected as a function of the energization state of the control valve 5.
- the first pressure stage can control an oil pressure of 1.8 bar and the second pressure stage can control an oil pressure of 3.3 bar. Since the pressure stages can be switched independently of the drive speed of the oil pump 2, a power saving is possible.
- the pressure stages are switched by means of the control valve 5 such that at least one piston cooling nozzle (not shown) can be actively switched via the oil pressure.
- piston cooling nozzles are present.
- the piston cooling nozzles have an opening pressure which is between the pressure of the low pressure stage and the pressure of the high pressure stage.
- the underside of the pistons is sprayed with oil from below via the piston cooling nozzle connected to the oil circuit in order to cool the piston and thus also a part of the combustion chamber. This allows the piston temperature to lower.
- the piston cooling nozzles can be switched by means of the control valve 5.
- the piston cooling nozzles open when the applied oil pressure is above an opening pressure.
- each piston is preferably associated with a piston cooling nozzle.
- the piston cooling nozzles are fed by branches from the oil pressure line 16 (not shown).
- a bypass 18 can be opened and closed, wherein the bypass 18 connects a pressure side 19 of the oil pump 2 with a suction side 20 of the oil pump 2.
- the bypass 18 can be opened and closed by the third active surface 8 is shifted so that the pressure side 19 of the oil pump 2 is fluidly connected via the chamber 12 to the bypass 18.
- the bypass 18 may also be referred to as a bypass line.
- the oil pump 2 is preferably designed as a rotor pump.
- the oil pump 2 can be driven by the crankshaft.
- the oil pump 2 is preferably designed as a toothed ring pump.
- the gerotor pump has a centrally arranged drive gear and an outer eccentrically arranged toothed ring.
- the toothed ring is drivable by means of the drive gear.
- the toothed ring has one tooth more than the drive gear.
- the control piston 4 is spring loaded. On the first active surface 6 of the oil pressure acts. The oil pressure can act on the second active surface 7 as a function of the switching position of the control valve 5.
- the pump outlet pressure acts on the third effective surface 8.
- On the three active surfaces 6, 7 and 8 each act on the oil pressure and the pump output pressure dependent forces which move the piston against the spring force. From a certain piston position, the oil flows from the chamber 12 via the bypass 18 to the suction side 20 of the oil pump 2 back. Now, when the control channel 13 is opened by the control valve 5, a lower oil pressure and a lower pump outlet pressure is sufficient to open the bypass line 18 and to connect to the chamber 12. This preferably corresponds to the energized position of the control valve. 5
- the control valve 5 is preferably arranged on a housing of the oil pump 2.
- the oil line 11, the oil pressure line 9, the control channel 13 and the oil pressure line 15 may be formed at least partially within the housing.
- control piston 4 further active surfaces (not shown), said further active surfaces (not shown) via further control valves can be acted upon in accordance with the oil pressure to realize further pressure levels.
Description
Die Erfindung betrifft eine Vorrichtung zur Druckregelung einer Ölpumpe, mit den Merkmalen des Oberbegriffes des Patentanspruches 1.The invention relates to a device for pressure control of an oil pump, having the features of the preamble of
Die Vorrichtung zur Druckregelung dient dazu, die Förderleistung der Ölpumpe und/oder den bereitgestellten Öldruck der Ölpumpe an den wechselnden Bedarf des Schmiersystems des Verbrennungsmotors anzupassen. Es werden vorzugsweise unnötig hohe Öldrucke vermieden, um die zum Antrieb der Ölpumpe erforderliche Antriebsleistung gering zu halten.The device for pressure control serves to adapt the delivery rate of the oil pump and / or the oil pressure of the oil pump provided to the changing needs of the lubrication system of the internal combustion engine. It is preferable to avoid unnecessarily high oil pressures to keep the drive power required to drive the oil pump low.
Aus der
Diese Vorrichtung zur Druckregelung der Ölpumpe ist noch nicht optimal ausgebildet. Die eingestellte Regeldruckstufe ist abhängig von der Fliehkraft und damit abhängig von der Drehzahl des Antriebszahnrades. Bei hohen Drehzahlen des Antriebszahnrades wird die höhere Regeldruckstufe gewählt. Der Aufbau des Antriebszahnrades mit dem im Antriebszahnrad angeordneten Schaltkolben ist aufwändig herzustellen und zu montieren. Ferner ist der Aufbau der Verschiebeeinheit aufwendig.This device for pressure control of the oil pump is not yet optimally formed. The set control pressure level depends on the centrifugal force and thus depends on the speed of the drive gear. At high speeds of the drive gear, the higher control pressure level is selected. The structure of the drive gear with the arranged in the drive gear shift piston is complex to manufacture and assemble. Furthermore, the structure of the displacement unit is complicated.
Aus der gattungsbildenden
Aus
Aus der
Der Erfindung liegt daher die Aufgabe zugrunde, die gattungsbildende Vorrichtung zur Druckregelung der Ölpumpe derart auszugestalten und weiterzubilden, so dass der Aufbau der Vorrichtung vereinfacht ist.The invention is therefore based on the object, the generic type device for pressure control of the oil pump in such a way and further, so that the structure of the device is simplified.
Diese der Erfindung zugrunde liegende Aufgabe wird nun durch eine Vorrichtung zur Druckregelung der Ölpumpe, mit den Merkmalen des Patentanspruches 1 gelöst. Die Regelung der Ölpumpe erfolgt dadurch, dass mittels des Regelkolbens ein Bypass öffenbar und schließbar ist, wobei der Bypass eine Druckseite der Ölpumpe mit einer Saugseite der Ölpumpe verbindet. Dies hat den Vorteil, dass der Aufbau der Ölpumpe und damit der Aufbau der gesamten Vorrichtung vereinfacht werden kann. Die Ölpumpe benötigt kein Verschiebezahnrad und keine Verschiebeeinheit für ein solches Zahnrad. Hierdurch ist ein kostengünstiger einfacherer Aufbau erzielt.This object of the invention is based is achieved by a device for pressure control of the oil pump, with the features of
Die Ölpumpe ist als Innenzahnradpumpe oder als Zahnringpumpe ausgebildet. Durch den Bypass ist auf einfache Weise eine Druckregelung der Innenzahnradpumpe oder der Zahnringpumpe mit mindestens zwei Druckstufen ermöglicht. Die Zahnringpumpe weist vorzugsweise eine Trochoidenverzahnung auf, wobei ein mittig gelagertes Antriebszahnrad einen äußeren exzentrisch gelagerten Zahnring antreibt. Hierdurch entstehen in der Pumpe sich verkleinernde und vergrößernde Räume, die die Saug- und Förderwirkung erzeugen. Das Antriebszahnrad ist antriebstechnisch mit der Kurbelwelle gekoppelt.The oil pump is designed as an internal gear pump or as a gerotor pump. Through the bypass is easily a pressure control of the internal gear pump or the gerotor pump with at least two pressure levels possible. The toothed ring pump preferably has a trochoid toothing, wherein a centrally mounted drive gear drives an outer eccentrically mounted toothed ring. This results in the pump shrinking and enlarging spaces that produce the suction and conveying effect. The drive gear is drivingly coupled to the crankshaft.
Je nach Stellung des Regelkolbens ist der Bypass verschlossen oder geöffnet. Der Pumpenausgangsdruck liegt an der dritten Wirkfläche an. Auf die erste Wirkfläche und die zweite Wirkfläche wirkt eine vom Öldruck abhängige Kraft. Der Regelkolben ist federbelastet. Die auf die Wirkflächen wirkenden Kräfte sind der Federkraft entgegengesetzt. Der Regelkolben ist als Summenkolben ausgebildet. Wenn der Bypass geöffnet ist, wird der Pumpenausgangsdruck abgesenkt. Ab einer bestimmten Kolbenstellung strömt Öl intern über den Bypass von der Druck- auf die Saugseite der Ölpumpe zurück. Der Pumpenausgangsdruck beziehungsweise der Öldruck wird bedarfsgerecht reduziert. Hierdurch erfolgt eine Regelung des Regelkolbens. Beim Kaltstart wirkt nur der Pumpenausgangsdruck auf die dritte Wirkfläche, wodurch der Maximaldruck begrenzt wird. Im Betrieb regelt die Summe beider Drücke auf die erste und zweite Wirkfläche einen festen Öldruck ein.Depending on the position of the control piston, the bypass is closed or opened. The pump outlet pressure is applied to the third effective area. On the first active surface and the second effective surface acts a dependent on the oil pressure force. The control piston is spring loaded. The forces acting on the active surfaces are opposite to the spring force. The control piston is designed as a sum piston. When the bypass is open, the pump outlet pressure is lowered. From a certain piston position, oil flows back internally via the bypass from the pressure side to the suction side of the oil pump. The pump outlet pressure or the oil pressure is reduced as needed. This results in a control of the control piston. During cold start, only the pump outlet pressure acts on the third effective area, which limits the maximum pressure. In operation, the sum of both pressures on the first and second effective area regulates a fixed oil pressure.
Durch Regelung von mindestens zwei Druckstufen kann so zum einen der Energiebedarf zur Ölversorgung bedarfsgerecht reduziert werden und zum anderen mindestens eine Kolbenkühldüse aktiv über den Öldruck geschaltet werden. Insbesondere werden mehrere Kolbenkühldüsen in Abhängigkeit der Schaltstellung des Stellventils und somit in Abhängigkeit von der gewählten Druckstufe geschaltet. In einer Hochdruckstufe ist die mindestens eine Kolbenkühldüse aktiviert und in einer Niederdruckstufe ist die mindestens eine Kolbenkühldüse deaktiviert.By controlling at least two pressure levels, on the one hand, the energy requirement for the oil supply can be reduced as needed and, on the other hand, at least one piston cooling nozzle can be actively switched via the oil pressure. In particular, several piston cooling nozzles are switched as a function of the switching position of the control valve and thus in dependence on the selected pressure level. In a high-pressure stage, the at least one piston cooling nozzle is activated, and in a low-pressure stage, the at least one piston cooling nozzle is deactivated.
Auf eine erste Wirkfläche des Regelkolbens wirkt ein Öldruck, nämlich insbesondere ein sogenannter Galeriedruck. Mit Hilfe des Stellventils ist ein Steuerkanal öffenbar und schließbar, der eine zweite Wirkfläche des Regelkolbens freigibt. Der auf die erste Wirkfläche wirkende Öldruck ist insbesondere geringer als der Pumpenausgangsdruck. Der Öldruck beziehungsweise Galeriedruck zur Beaufschlagung der ersten und zweiten Wirkfläche wird vorzugsweise hinter einem Ölfilter und hinter einem Ölkühler abgezweigt. Dieser Öldruck kann als Galeriedruck bezeichnet werden.On a first effective area of the control piston acts an oil pressure, namely in particular a so-called gallery pressure. With the help of the control valve a control channel can be opened and closed, which releases a second effective area of the control piston. The oil pressure acting on the first effective area is in particular lower than the pump outlet pressure. The oil pressure or gallery pressure for acting on the first and second active surfaces is preferably branched off behind an oil filter and behind an oil cooler. This oil pressure can be referred to as gallery printing.
Das Stellventil ist vorzugsweise als elektromagnetisch betätigtes Stellventil ausgebildet. Das Stellventil ist durch ein on-/off-Ventil gebildet. Hierdurch ist es möglich, die unterschiedlichen Druckstufen unabhängig von der Eingangsdrehzahl der Ölpumpe zu wählen. Das elektromagnetische Stellventil ist vorzugsweise an einem Gehäuse der Ölpumpe angeordnet, wobei der Steuerkanal sich innerhalb des Gehäuses erstreckt. Das Stellventil ist von außen zugänglich am Gehäuse der Ölpumpe angeordnet. Der Regelkolben ist innerhalb des Gehäuses der Ölpumpe angeordnet.The control valve is preferably designed as an electromagnetically actuated control valve. The control valve is formed by an on / off valve. This makes it possible to choose the different pressure levels regardless of the input speed of the oil pump. The electromagnetic control valve is preferably disposed on a housing of the oil pump, wherein the control channel extends within the housing. The control valve is arranged externally accessible on the housing of the oil pump. The control piston is arranged within the housing of the oil pump.
Eine Hochdruckstufe ist realisiert, wenn das Stellventil stromlos geschaltet ist. In der Hochdruckstufe ist der Steuerkanal gesperrt. Der Steuerkanal ist über das Stellventil mit einer Leitung zum Ölsumpf verbunden, wodurch die zweite Wirkfläche druckentlastet ist. Die zweite Wirkfläche ist hierbei nicht von dem Öldruck beaufschlagt. Das Öl strömt lediglich zur ersten Wirkfläche. Auf die erste Wirkfläche wirkt eine vom Öldruck abhängige Kraft, welche den Kolben entgegen der Federkraft verschieben kann, wenn der Öldruck steigt. Ab einer bestimmten Kolbenstellung strömt Öl über den Bypass von der Druckseite auf die Saugseite der Ölpumpe zurück, wodurch der Pumpenausgangsdruck und im Falle des Kaltstarts der maximale Öldruck begrenzt wird.A high pressure stage is realized when the control valve is de-energized. In the high-pressure stage, the control channel is blocked. The control channel is connected via the control valve with a line to the oil sump, whereby the second effective area is depressurized. The second active surface is not acted upon by the oil pressure. The oil flows only to the first effective area. On the first effective surface acts a dependent of the oil pressure force, which can move the piston against the spring force when the oil pressure increases. From a certain piston position, oil flows back through the bypass from the pressure side to the suction side of the oil pump, which limits the pump output pressure and, in the case of a cold start, the maximum oil pressure.
Eine Niederdruckstufe ist realisiert, wenn das Stellventil bestromt ist, wobei das Stellventil zum Steuerkanal und somit zu der zweiten Wirkfläche geöffnet ist. Das Öl strömt durch den Steuerkanal zu der zweiten Wirkfläche. In der Niederdruckstufe ist der Steuerkanal geöffnet. Die erste und die zweite Wirkfläche sind mit dem Öldruck entgegen der auf den Regelkolben wirkenden Federkraft beaufschlagt. Durch die Summierung der ersten und der zweiten Wirkfläche und somit der Kräfte auf die erste und zweite Wirkfläche wird für die gleiche Verstellung des Regelkolbens ein geringerer Öldruck benötigt. Der Regelbeginn beginnt früher und der Bypass wird früher geöffnet.A low pressure stage is realized when the control valve is energized, wherein the control valve is open to the control channel and thus to the second effective area. The oil flows through the control channel to the second effective surface. In the low pressure stage, the control channel is open. The first and the second active surface are acted upon by the oil pressure against the force acting on the control piston spring force. By summing the first and the second effective area and thus the forces on the first and second active area a lower oil pressure is required for the same adjustment of the control piston. The beginning of the rule starts earlier and the bypass opens earlier.
Es ist denkbar, dass der Regelkolben weitere Wirkflächen aufweist, die über weitere Kanäle beziehungsweise Steuerkanäle freischaltbar beziehungsweise beaufschlagbar sind.It is conceivable that the control piston has further active surfaces, which can be activated or acted upon via further channels or control channels.
Die eingangs genannten Nachteile sind hierdurch vermieden und entsprechend Vorteile sind erzielt.The aforementioned disadvantages are thereby avoided and corresponding advantages are achieved.
Es gibt nun eine Vielzahl von Möglichkeiten, die erfindungsgemäße Vorrichtung zur Druckregelung der Ölpumpe auszugestalten und weiterzubilden. Hierfür darf zunächst auf die dem Patentanspruch 1 nachgeordneten Patentansprüche verwiesen werden. Im Folgenden wird eine bevorzugte Ausgestaltung der Erfindung anhand der Zeichnung und der dazugehörigen Beschreibung näher erläutert.There are now a variety of ways to design and further develop the inventive device for pressure control of the oil pump. For this purpose, reference may first be made to the claims subordinate to claim 1. In the following, a preferred embodiment of the invention will be explained in more detail with reference to the drawing and the associated description.
In der Zeichnung zeigt:
- Fig. 1
- in einer schematischen Darstellung eine Vorrichtung zur Druckregelung einer Ölpumpe,
- Fig. 2
- in einer schematischen, teilgeschnittenen Darstellung eine in einem Gehäuse angeordnete Ölpumpe,
- Fig. 3
- in einer schematischen, teilgeschnittenen Detaildarstellung des Gehäuses, und
- Fig. 4
- in einer schematischen Darstellung die Ölpumpe und ein Teil des Gehäuses.
- Fig. 1
- in a schematic representation of a device for pressure control of an oil pump,
- Fig. 2
- in a schematic, partially sectional view of an oil pump arranged in a housing,
- Fig. 3
- in a schematic, partially sectioned detail of the housing, and
- Fig. 4
- in a schematic representation of the oil pump and a part of the housing.
In
Die Vorrichtung 1 weist nun einen Regelkolben 4 und ein Stellventil 5 auf. Mittels des Regelkolbens 4 sind mindestens zwei Druckstufen regelbar, nämlich eine Niederdruckstufe und eine Hochdruckstufe. Der Regelkolben 4 weist dazu eine erste Wirkfläche 6, eine zweite Wirkfläche 7 und insbesondere eine dritte Wirkfläche 8 auf. An der ersten Wirkfläche 6 liegt ein Öldruck an, der durch eine Öldruckleitung 9 bereitgestellt ist. Die Öldruckleitung 9 mündet in eine Kammer 10, wobei die Kammer 10 einerseits von der Wirkfläche 6 des Regelkolbens begrenzt wird.The
Die Ölpumpe 2 fördert das Öl aus der Ölwanne 3 durch eine Kammer 12 und stellt einen Pumpenausgangsdruck bereit. Der Pumpenausgangsdruck liegt an einem Anschluss der Kammer 12 und einer hiermit verbundenen Ölleitung 11 an. Diese Ölleitung 11 kann sich insbesondere im Gehäuse der Ölpumpe 2 erstrecken. Dieser Förderstrom der Ölpumpe 2 wird über die Ölleitung 11 einem Ölfilter ÖF und einem Ölkühler ÖK zugeführt. Hinter dem Ölkühler ÖK wird der Öldruck an einer Öldruckleitung 16 abgezweigt. Dieser Öldruck kann auch als Galleriedruck bezeichnet werden. Der Öldruck ist infolge von Druckverlusten über den Ölfilter ÖF und den Ölkühler ÖK kleiner als der Pumpenausgangsdruck.The
Mittels des Stellventils 5 ist ein Steuerkanal 13 zur Beaufschlagung der zweiten Wirkfläche 7 mit dem Öldruck öffenbar und schließbar. Der Steuerkanal 13 verbindet den Anschluss A des Stellventils 5 mit der Kammer 14 des Regelkolbens 4. Eine weitere Öldruckleitung 15 ist mit einem Anschluss P des Stellventils 5 verbunden. Die Öldruckleitungen 9 und 15 werden von der gemeinsamen Öldruckleitung 16 gespeist. Die Öldruckleitung 16 ist zumindest teilweise in einem Kurbelgehäuse 17 ausgebildet.By means of the
In der in
Das Stellventil 5 ist vorzugsweise als elektromagnetisches Stellventil 5 ausgebildet. Dies hat den Vorteil, dass die zwei Druckstufen in Abhängigkeit von dem Bestromungszustand des Stellventils 5 gewählt werden können. Die erste Druckstufe kann bspw. einen Öldruck von 1,8 bar und die zweite Druckstufe kann bspw. einen Öldruck von 3,3 bar einregeln. Da die Druckstufen unabhängig von der Antriebsdrehzahl der Ölpumpe 2 geschaltet werden können, ist eine Leistungseinsparung möglich.The
Erfindungsgemäß werden die Druckstufen mittels des Stellventils 5 derart geschaltet, dass mindestens eine Kolbenkühldüse (nicht dargestellt) aktiv über den Öldruck geschaltet werden kann. Insbesondere sind mehrere Kolbenkühldüsen vorhanden. Die Kolbenkühldüsen weisen einen Öffnungsdruck auf, der zwischen dem Druck der Niederdruckstufe und dem Druck der Hochdruckstufe liegt. Hierbei wird die Unterseite der Kolben über die mit dem Ölkreislauf verbundenen Kolbenkühldüse von unten mit Öl bespritzt, um den Kolben und damit auch zu einem Teil den Brennraum zu kühlen. Hierdurch lässt sich die Kolbentemperatur absenken. Die Kolbenkühldüsen sind mittels des Stellventils 5 schaltbar. Die Kolbenkühldüsen öffnen dabei, wenn der anliegende Öldruck oberhalb eines Öffnungsdruckes liegt. Liegt der Öldruck unterhalb des Öffnungsdrucks, so ist die Kolbenkühldüse deaktiviert und es wird kein Öl auf die Kolbenunterseite gespritzt. Jedem Kolben ist vorzugsweise eine Kolbenkühldüse zugeordnet. Die Kolbenkühldüsen werden von Abzweigen von der Öldruckleitung 16 gespeist (nicht dargestellt).According to the invention, the pressure stages are switched by means of the
Mittels des Regelkolbens 4 ist ein Bypass 18 öffenbar und schließbar, wobei der Bypass 18 eine Druckseite 19 der Ölpumpe 2 mit einer Saugseite 20 der Ölpumpe 2 verbindet. Mittels der dritten Wirkfläche des Regelkolbens 4 ist der Bypass 18 öffenbar und verschließbar, indem die dritte Wirkfläche 8 derart verschoben ist, so dass die Druckseite 19 der Ölpumpe 2 über die Kammer 12 mit dem Bypass 18 fluidtechnisch verbunden ist. Der Bypass 18 kann auch als Umgehungsleitung bezeichnet werden.By means of the
Dies hat den Vorteil, dass der Aufbau der Ölpumpe 2 und damit der Aufbau der gesamten Vorrichtung 1 vereinfacht werden kann. Die Ölpumpe 2 ist vorzugsweise als Rotorpumpe ausgebildet. Die Ölpumpe 2 ist von der Kurbelwelle antreibbar. Die Ölpumpe 2 ist vorzugsweise als Zahnringpumpe ausgebildet ist. Die Zahnringpumpe weist ein mittig angeordnetes Antriebszahnrad und einen äußeren exzentrisch angeordneten Zahnring auf. Der Zahnring ist mittels des Antriebszahnrads antreibbar. Der Zahnring weist einen Zahn mehr als das Antriebszahnrad auf.This has the advantage that the structure of the
Der Regelkolben 4 ist federbelastet. Auf die erste Wirkfläche 6 wirkt der Öldruck. Auf die zweite Wirkfläche 7 kann der Öldruck wirken in Abhängigkeit der Schaltstellung des Stellventils 5. Auf die dritte Wirkfläche 8 wirkt der Pumpenausgangsdruck. Auf die drei Wirkflächen 6, 7 und 8 wirken jeweils vom Öldruck und vom Pumpenausgangsdruck abhängige Kräfte, welche den Kolben entgegen der Federkraft verschieben. Ab einer bestimmten Kolbenstellung strömt das Öl aus der Kammer 12 über den Bypass 18 zur Saugseite 20 der Ölpumpe 2 zurück. Wenn nun der Steuerkanal 13 durch das Stellventil 5 geöffnet ist, ist ein geringerer Öldruck und ein geringerer Pumpenausgangsdruck hinreichend, um die Bypassleitung 18 zu öffnen bzw. mit der Kammer 12 zu verbinden. Dies entspricht vorzugsweise der bestromten Stellung des Stellventils 5.The
Wenn das Stellventil 5 stromlos geschaltet ist, ist der Steuerkanal 13 gesperrt. Die zweite Wirkfläche 7 ist nicht mit dem Öldruck beaufschlagt, sondern die Kammer 14 ist über das Stellventil 5 mit einer Leitung 21 zur Ölwanne 3 verbunden. Da nun zum Öffnen des Bypass 18 ein höherer Öldruck erforderlich ist, stellt sich am Pumpenausgang ein entsprechender höherer Pumpenausgangsdruck ein. Es ist eine Hochdruckstufe realisiert.When the
Beim Kaltstart wirkt nur der Pumpenausgangsdruck auf die dritte Wirkfläche 8, wodurch ein Maximaldruck begrenzt wird. Im Betrieb regelt die Summe der auf die Wirkflächen 6 bis 8 wirkenden Kräfte die beiden Druckstufen ein. Das Stellventil 5 ist vorzugsweise an einem Gehäuse der Ölpumpe 2 angeordnet. Die Ölleitung 11, die Öldruckleitung 9, der Steuerkanal 13 und die Öldruckleitung 15 können zumindest teilweise innerhalb des Gehäuses ausgebildet sein.During cold start only the pump outlet pressure acts on the third
Es ist denkbar, dass in alternativer Ausgestaltung der Regelkolben 4 weitere Wirkflächen (nicht dargestellt) aufweist, wobei diese weiteren Wirkflächen über weitere Stellventile (nicht dargestellt) entsprechend mit dem Öldruck beaufschlagt werden können, um weitere Druckstufen zu realisieren.It is conceivable that in an alternative embodiment of the
- 11
- Vorrichtungdevice
- 22
- Ölpumpeoil pump
- 33
- Ölwanneoil pan
- 44
- Regelkolbencontrol piston
- 55
- StellventilControl valve
- 66
- erste Wirkflächefirst effective area
- 77
- zweite Wirkflächesecond effective area
- 88th
- dritte Wirkflächethird effective area
- 99
- ÖldruckleitungOil pressure line
- 1010
- Kammerchamber
- 1111
- Ölleitungoil line
- 1212
- Kammerchamber
- 1313
- Steuerkanalcontrol channel
- 1414
- Kammerchamber
- 1515
- ÖldruckleitungOil pressure line
- 1616
- ÖldruckleitungOil pressure line
- 1717
- Kurbelgehäusecrankcase
- 1818
- Bypassbypass
- 1919
- Druckseitepressure side
- 2020
- Saugseitesuction
- 2121
- Leitungmanagement
- ÖFÖF
- Ölfilteroil filter
- ÖKÖK
- Ölkühleroil cooler
- PP
- Anschluss des StellventilsConnection of the control valve
- AA
- Anschluss des StellventilsConnection of the control valve
- TT
- Anschluss des StellventilsConnection of the control valve
Claims (3)
- A device (1) for pressure regulation of an oil pump (2), having at least one piston cooling jet, with a regulating piston (4) and having a control valve (5), wherein by means of the regulating piston (4) at least two pressure levels can be regulated, wherein the regulating piston (4) has a first active face (6) and a second active face (7), wherein an oil pressure acts on the first active face (6), wherein by means of the control valve (5) a control duct can be opened and closed in order to make the oil pressure act on the second active face (7), wherein by means of the regulating piston (4) a bypass (18) can be opened and closed, wherein the bypass (18) connects a pressure side (19) of the oil pump (2) to a suction side (20) of the oil pump (2), characterized in that the at least one piston cooling jet can be switched in dependence on the switch position of the control valve (5) and thus in dependence on the selected pressure level, wherein in a high pressure level the at least one piston cooling jet is activated, wherein in the low pressure level the at least one piston cooling jet is deactivated, wherein the at least one piston cooling jet has an opening pressure and the opening pressure is between the pressure of the low pressure level and the pressure of the high pressure level, wherein the oil pump (2) is designed as an internal gear pump or as a gear ring pump.
- The device according to the preceding claim, characterized in that a high pressure level is realized in that the control valve (5) is designed without current, wherein in the high pressure level the control duct (13) is blocked and the control duct (13) is connected via the control valve (5) to a line (21) to the oil pan (3) and thus the second active face is pressure-relieved, wherein in a low pressure level the control valve (5) is supplied with current, wherein the low pressure level of the control duct (13) is opened and thus the second active face (7) and the first active face (6) are acted upon with oil pressure against a spring force pressing on the regulating piston (4).
- The device according to any one of the preceding claims, characterized in that a pump output pressure acts on the third face, wherein the oil pressure is branched off behind an oil filter (OF) and behind an oil cooler (OK), wherein the oil pressure is lower than the pump output pressure.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015005682.4A DE102015005682A1 (en) | 2015-05-06 | 2015-05-06 | Device for pressure control of an oil pump |
PCT/EP2016/000730 WO2016177468A1 (en) | 2015-05-06 | 2016-05-04 | Device for pressure regulation in an oil pump |
Publications (2)
Publication Number | Publication Date |
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EP3292282A1 EP3292282A1 (en) | 2018-03-14 |
EP3292282B1 true EP3292282B1 (en) | 2019-11-20 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP16722786.7A Active EP3292282B1 (en) | 2015-05-06 | 2016-05-04 | Device for pressure regulation in an oil pump |
Country Status (3)
Country | Link |
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EP (1) | EP3292282B1 (en) |
DE (1) | DE102015005682A1 (en) |
WO (1) | WO2016177468A1 (en) |
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CN109139175A (en) * | 2018-10-22 | 2019-01-04 | 湖南机油泵股份有限公司 | The control pressurer system based on fixed displacement lubricating oil pump that structure simplifies |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DD252413A1 (en) * | 1986-08-26 | 1987-12-16 | Ifa Motorenwerke | DEVICE FOR OIL PRESSURE CONTROL IN INTERNAL COMBUSTION ENGINES |
DE3824398C2 (en) * | 1987-07-23 | 1993-11-18 | Barmag Barmer Maschf | Lubricating oil pump |
DE10141786B4 (en) * | 2001-08-25 | 2008-12-24 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Device for controlling the lubricating oil pressure of an internal combustion engine |
DE10237801C5 (en) | 2002-01-12 | 2010-02-11 | Voigt, Dieter, Dipl.-Ing. | Device for regulating the pressure of hydraulic pumps |
DE102004049029B4 (en) * | 2004-10-08 | 2015-05-21 | Audi Ag | Apparatus and method for controlling a lubricating oil pressure of an internal combustion engine |
DE102006051575A1 (en) * | 2006-11-02 | 2007-09-13 | Voigt, Dieter, Dipl.-Ing. | Regulator for hydraulic pump, has adjusting device adjusting flow rate of regulated oil pump, where regulator produces increased regulated pressure either from oil pressure or from discharge pressure fed over connection |
DE102012002672B4 (en) * | 2011-11-02 | 2014-07-24 | Dieter Voigt | register pump |
GB2502369B (en) * | 2012-05-25 | 2016-03-23 | Gm Global Tech Operations Inc | Lubrication system for an internal combustion engine |
-
2015
- 2015-05-06 DE DE102015005682.4A patent/DE102015005682A1/en not_active Withdrawn
-
2016
- 2016-05-04 WO PCT/EP2016/000730 patent/WO2016177468A1/en active Application Filing
- 2016-05-04 EP EP16722786.7A patent/EP3292282B1/en active Active
Non-Patent Citations (1)
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WO2016177468A1 (en) | 2016-11-10 |
EP3292282A1 (en) | 2018-03-14 |
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