EP3292282A1 - Device for pressure regulation in an oil pump - Google Patents

Device for pressure regulation in an oil pump

Info

Publication number
EP3292282A1
EP3292282A1 EP16722786.7A EP16722786A EP3292282A1 EP 3292282 A1 EP3292282 A1 EP 3292282A1 EP 16722786 A EP16722786 A EP 16722786A EP 3292282 A1 EP3292282 A1 EP 3292282A1
Authority
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.)
Granted
Application number
EP16722786.7A
Other languages
German (de)
French (fr)
Other versions
EP3292282B1 (en
Inventor
Timm BRÖCKER
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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 Volkswagen AG filed Critical Volkswagen AG
Publication of EP3292282A1 publication Critical patent/EP3292282A1/en
Application granted granted Critical
Publication of EP3292282B1 publication Critical patent/EP3292282B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • 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
    • 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
    • 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 is obvious and closable, 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.
  • CONFIRMATION COPY 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 exceeding a switching speed of for example 2500 revolutions per minute, the control piston is displaced 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.
  • This generic 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.
  • 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 takes place in that by means of the control piston a bypass apparently and closable, wherein the bypass connects a pressure side of the oil pump with a suction side of the oil pump.
  • the oil pump is preferably 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 creates 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.
  • 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.
  • the at least one piston cooling nozzle is activated, and in a low-pressure stage, the at least one piston cooling nozzle is deactivated.
  • On a first effective area of the control piston acts an oil pressure, namely in particular a so-called gallery pressure.
  • gallery pressure With the help of the control valve, a control channel is obvious and closable, 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 in a schematic representation of a device for pressure control of a
  • FIG. 2 is a schematic, partially sectioned view of a housing arranged in an oil pump
  • Fig. 3 in a schematic, partially sectioned detail of the housing
  • Fig. 4 in a schematic representation of the oil pump and a part of the housing.
  • a device 1 for pressure control of an oil pump 2 is shown schematically.
  • 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 at one of the ports of the Chamber 12 and an associated oil line 1 1 at.
  • 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 effective surface 7 with the oil pressure is obvious and closable.
  • 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 port P is open to port A of the control valve 5, d. H. the control channel 13 is opened, so that the chamber 14 and thus the second active surface 7 is acted upon by the oil pressure. Regardless of the control of the control valve 5, the chamber 10 is acted upon by the first effective surface 6 with oil pressure from the oil pressure line 9.
  • 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, for example, an oil pressure of 1, 8 bar and the second pressure stage can, for example. Adjust 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).
  • bypass 18 is apparent and closable, 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 is apparent and closable 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 When the control valve 5 is de-energized, the control channel 13 is locked. The second active surface 7 is not acted upon by the oil pressure, but the chamber 14 is connected via the control valve 5 with a line 21 to the oil pan 3. Since a higher oil pressure is now required to open the bypass 18, a corresponding higher pump outlet pressure is established at the pump outlet. It is realized a high-pressure stage. During cold start only the pump outlet pressure acts on the third active surface 8, whereby a maximum pressure is limited. In operation, the sum of the forces acting on the active surfaces 6 to 8 regulates the two pressure levels.
  • the control valve 5 is preferably arranged on a housing of the oil pump 2.
  • the oil line 1 1, 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

Device (1) for pressure regulation in an oil pump (2), having a regulating piston (4) and having a control valve (5), wherein at least two pressure levels can be regulated by means of the regulating piston (4), 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) it is possible to open and close a control duct in order to make the oil pressure act on the second active face (7). By means of the regulating piston (4), it is possible to open and close a bypass (18), wherein the bypass (18) connects a pressure side (19) of the oil pump (2) to a suction side (20) of the oil pump (2).

Description

Vorrichtung zur Druckregelung einer Ölpumpe  Device for pressure control of an oil pump
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 claim 1.
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 gattungsbildenden DE 102 37 801 A1 ist eine Vorrichtung zur Druckregelung einer Ölpumpe bekannt. Die Ölpumpe weist ein auf einer Antriebswelle fixiertes Antriebszahnrad und ein mit dem Antriebszahnrad kämmendes Verschiebezahnrad auf. Bei einer Fördermengenregelung wird das Verschiebezahnrad axial verschoben, so dass durch eine veränderte Zahneingriffsbreite die Ölfördermenge verändert wird. Das Verschiebezahnrad ist auf einem nicht rotierenden Bolzen gelagert, der einen Verschiebekolben und einen Federkolben trägt. Dieser Verbund bildet eine Verschiebeeinheit. Die Verschiebeeinheit ist am Verschiebekolben ständig mit Öldruck beaufschlagt, während hierzu entgegenwirkend am Federkolben eine Kolbenfeder und ein in der Federkammer wirkender, regelbarer Steuerdruck die Fördermengenregelung vornehmen. Die Regelung des Steuerdrucks wird über einen Regelkolben vorgenommen. Der Regelkolben und die Federkammer sind über eine Steuerbohrung miteinander verbunden. Der Regelkolben ist als Stufenkolben ausgebildet und weist drei Wirkflächen auf. Der Regelkolben weist eine erste Wirkfläche auf, wobei an der ersten Wirkfläche ständig ein Öldruck anliegt. Die zweite Wirkfläche ist durch zwei Ansteuereinrichtungen zusätzlich mit Öldruck beaufschlagbar oder druckentlastbar, um eine Zusatzkraft auf den Regelkolben auszuüben. Die dritte Wirkfläche ist durch einen Regelzapfen gebildet, wobei mittels der dritten Wirkfläche bzw. mittels des Regelzapfen die Steuerbohrung offenbar und verschließbar ist, wodurch der Steuerdruck geregelt wird. Der Öldruck kann in zumindest zwei Regeldruckstufen eingestellt werden. Der von den Ansteuervorrichtungen mit einer veränderlichen Kraft beaufschlagbare Regelkolben bewirkt die zugehörige Einstellung der Fördermengenregeleinrichtung. Als Gegenkraft zum Steuerdruck wirkt eine Regelfeder auf den Regelkolben. Die erste Ansteuereinrichtung weist ein erstes Stellventil auf. Das erste Stellventil ist als drehzahlabhängiges Fliehkraftventil mit einem Schaltkolben und einer Schaltkolbenfeder ausgebildet. Der Schaltkolben und die From the generic DE 102 37 801 A1 a device for pressure control of an oil pump is known. The oil pump has a drive gear fixed on a drive shaft and a shift gear meshing with the drive gear. In a flow control, 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 is obvious and closable, 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. As a counter force to the control pressure, 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 control piston and the
BESTÄTIGUNGSKOPIE Schaltkolbenfeder sind innerhalb eines Förderzahnrades angeordnet. Der Schaltkolben weist in seiner Achse einen Winkelversatz zur radialen Fliehkraftrichtung auf. Der Öldruck zur Druckbeaufschlagung der Wirkflächen des Regelkolbens wird hinter einem Ölfilter abgezweigt. Nach Überschreiten einer Umschaltdrehzahl von beispielsweise 2500 Umdrehungen pro Minute wird der Schaltkolben fliehkraftbedingt gegen die Schaltkolbenfeder in eine äußere Endposition verschoben. Bei diesen hohen Drehzahlen wird der Öldruck auf ein Öldruckniveau von beispielsweise 5,0 bar erhöht, wobei eine Druckentlastung der zweiten Wirkfläche des Regelkolbens erfolgt. Ferner ist eine zweite Ansteuereinrichtung vorgesehen. Diese zweite Ansteuervorrichtung weist ein zweites Stellventil in Form eines Elektroventils auf. Bei einer Aktivierung des Elektroventils wird zur Öldruckabsenkung ein Steuerkanal freigeschaltet, wodurch eine Druckbelastung mit dem Öldruck der zweiten Wirkfläche hervorgerufen wird. Damit sind beide Wirkflächen öldruckbelastet, so dass der Regelkolben bereits bei 2,5 bar Öldruck - der ersten Regeldruckstufe - seine Regelfunktion ausübt und den entsprechenden Steuerdruck zur Fördermengenregelung bereitstellt. Wenn das Elektroventil unbestromt ist, wird die Öldruckzufuhr zum Steuerkanal und somit zur zweiten Wirkfläche unterbrochen und über einen Entlastungsstutzen am Elektroventil wird eine Druckentlastung der zweiten Wirkfläche hervorgerufen. Der nun nur noch an der ersten Wirkfläche anliegende Öldruck verlagert den Regelbeginn dann auf beispielsweise 5 bar, wodurch die zweite, höhere Regeldruckstufe gebildet ist. Diese zweite Regeldruckstufe ist bei einer defektbedingten Unterbrechung der elektrischen Anschlüsse des Elektroventils als Sicherheitsöldruck für alle Betriebsbedingungen des Verbrennungsmotors gewährleistet. CONFIRMATION COPY 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 exceeding a switching speed of for example 2500 revolutions per minute, the control piston is displaced 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. Furthermore, a second drive device is provided. This second drive device has a second control valve in the form of an electrovalve. Upon activation of the solenoid valve, a control channel is released for oil pressure reduction, whereby a pressure load with the oil pressure of the second effective surface is caused. Thus, 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. The now only applied to the first effective surface oil pressure then shifts the start of control then, for example, 5 bar, whereby the second, higher control pressure level is formed. This second control pressure level is ensured at a defect-related interruption of the electrical connections of the solenoid valve as a safety oil pressure for all operating conditions of the internal combustion engine.
Diese gattungsbildende 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 generic 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.
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 offenbar 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 claim 1. The control of the oil pump takes place in that by means of the control piston a bypass apparently and closable, wherein the bypass connects a pressure side of the oil pump with a suction side of the oil pump. This has the advantage that the structure of the oil pump and thus the structure of the entire device can be simplified. The oil pump requires no sliding gear and no displacement unit for such a gear. As a result, a more cost-effective simpler structure is achieved,
Die Ölpumpe ist vorzugsweise 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 preferably 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 creates 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 vorzugsweise 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. Auf eine erste Wirkfläche des Regelkolbens wirkt ein Öldruck, nämlich insbesondere ein sogenannter Galeriedruck. Mit Hilfe des Stellventils ist ein Steuerkanal offenbar 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. By controlling at least two pressure levels, the energy requirement for the oil supply can be reduced as needed and, on the other hand, preferably 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. 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 is obvious and closable, 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. Die eingangs genannten Nachteile sind hierdurch vermieden und entsprechend Vorteile sind erzielt. It is conceivable that the control piston has further active surfaces, which can be activated or acted upon via further channels or control channels. 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: In the drawing shows:
Fig. 1 in einer schematischen Darstellung eine Vorrichtung zur Druckregelung einer Fig. 1 in a schematic representation of a device for pressure control of a
Ölpumpe,  Oil pump,
Fig. 2 in einer schematischen, teilgeschnittenen Darstellung eine in einem Gehäuse angeordnete Ölpumpe, 2 is a schematic, partially sectioned view of a housing arranged in an oil pump,
Fig. 3 in einer schematischen, teilgeschnittenen Detaildarstellung des Gehäuses, und Fig. 3 in a schematic, partially sectioned detail of the housing, and
Fig. 4 in einer schematischen Darstellung die Ölpumpe und ein Teil des Gehäuses. Fig. 4 in a schematic representation of the oil pump and a part of the housing.
In Fig. 1 ist schematisch eine Vorrichtung 1 zur Druckregelung einer Ölpumpe 2 dargestellt. Fig. 2 bis 4 zeigen eine entsprechende Ölpumpe und einen Teil der Vorrichtung 1. Die Ölpumpe 2 fördert Öl aus einer Ölwanne 3. Die Ölwanne 3 bildet einen Ölsumpf. In Fig. 1, a device 1 for pressure control of an oil pump 2 is shown schematically. 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.
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 device 1 now has a control piston 4 and a control valve 5. 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.
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 1 1 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 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 at one of the ports of the Chamber 12 and an associated oil line 1 1 at. 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 ÖF and an oil cooler ÖK. Behind the oil cooler ÖK the oil pressure is branched off at an oil pressure line 16. This oil pressure can also be called galleriedruck. The oil pressure is lower than the pump outlet pressure due to pressure losses via the oil filter ÖF and the oil cooler ÖK.
Mittels des Stellventils 5 ist ein Steuerkanal 13 zur Beaufschlagung der zweiten Wirkfläche 7 mit dem Öldruck offenbar 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 control valve 5, a control channel 13 for acting on the second effective surface 7 with the oil pressure is obvious and closable. 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.
In der in Fig. 1 dargestellten Stellung des Stellventils 5 ist der Anschluss P zum Anschluss A des Stellventils 5 geöffnet, d. h. der Steuerkanal 13 ist geöffnet, so dass die Kammer 14 und somit die zweite Wirkfläche 7 mit dem Öldruck beaufschlagt wird. Unabhängig von der Ansteuerung des Stellventils 5 wird die Kammer 10 mit der ersten Wirkfläche 6 mit Öldruck aus der Öldruckleitung 9 beaufschlagt. In the position of the control valve 5 shown in FIG. 1, the port P is open to port A of the control valve 5, d. H. the control channel 13 is opened, so that the chamber 14 and thus the second active surface 7 is acted upon by the oil pressure. Regardless of the control of the control valve 5, the chamber 10 is acted upon by the first effective surface 6 with oil pressure from the oil pressure line 9.
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 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, for example, an oil pressure of 1, 8 bar and the second pressure stage can, for example. Adjust 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.
In besonders bevorzugter Ausgestaltung 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 den Kolbenunterseite gespritzt. Jedem Kolben ist vorzugsweise eine Kolbenkühldüse zugeordnet. Die Kolbenkühldüsen werden von Abzweigen von der Öldruckleitung 16 gespeist (nicht dargestellt). In a particularly preferred embodiment, 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. In particular, several 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. In this case, 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. If the oil pressure below the opening pressure, so is the Piston cooling nozzle deactivated and no oil is sprayed on the underside of the piston. 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).
Die eingangs genannten Nachteile sind nun dadurch vermieden, dass mittels des Regelkolbens 4 ein Bypass 18 offenbar und schließbar ist, 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 offenbar 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. The disadvantages mentioned above are now avoided by means of the control piston 4, a bypass 18 is apparent and closable, wherein the bypass 18 connects a pressure side 19 of the oil pump 2 with a suction side 20 of the oil pump 2. By means of the third active surface of the control piston 4, the bypass 18 is apparent and closable 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.
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 oil pump 2 and thus the structure of the entire device 1 can be simplified. 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.
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 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
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. 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 1 1 , die Öldruckleitung 9, der Steuerkanal 13 und die Öldruckleitung 15 können zumindest teilweise innerhalb des Gehäuses ausgebildet sein. When the control valve 5 is de-energized, the control channel 13 is locked. The second active surface 7 is not acted upon by the oil pressure, but the chamber 14 is connected via the control valve 5 with a line 21 to the oil pan 3. Since a higher oil pressure is now required to open the bypass 18, a corresponding higher pump outlet pressure is established at the pump outlet. It is realized a high-pressure stage. During cold start only the pump outlet pressure acts on the third active surface 8, whereby a maximum pressure is limited. In operation, the sum of the forces acting on the active surfaces 6 to 8 regulates the two pressure levels. The control valve 5 is preferably arranged on a housing of the oil pump 2. The oil line 1 1, the oil pressure line 9, the control channel 13 and the oil pressure line 15 may be formed at least partially within the housing.
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 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.
BEZUGSZEICHENLISTE LIST OF REFERENCE NUMBERS
1 Vorrichtung 1 device
2 Ölpumpe  2 oil pump
3 Ölwanne  3 oil pan
4 Regelkolben  4 control pistons
5 Stellventil  5 control valve
6 erste Wirkfläche  6 first effective area
7 zweite Wirkfläche  7 second effective area
8 dritte Wirkfläche  8 third effective area
9 Öldruckleitung  9 oil pressure line
10 Kammer  10 chamber
11 Ölleitung  11 oil line
12 Kammer  12 chamber
13 Steuerkanal  13 control channel
14 Kammer  14 chamber
15 Öldruckleitung  15 oil pressure line
16 Öldruckleitung  16 oil pressure line
17 Kurbelgehäuse  17 crankcase
18 Bypass  18 bypass
19 Druckseite  19 print page
20 Saugseite  20 suction side
21 Leitung  21 line
ÖF Ölfilter  ÖF oil filter
ÖK Ölkühler  ÖK oil cooler
P Anschluss des Stellventils  P Connection of the control valve
A Anschluss des Stellventils  A Connection of the control valve
T Anschluss des Stellventils  T Connection of the control valve

Claims

P A T E N TA N S P R Ü C H E PATEN TA NSPR CHE
1. Vorrichtung (1 ) zur Druckregelung einer Ölpumpe (2), mit einem Regelkolben (4) und mit einem Stellventil (5), wobei mittels des Regelkolbens (4) mindestens zwei Druckstufen regelbar sind, wobei der Regelkolben (4) eine erste Wirkfläche (6) und eine zweite Wirkfläche (7) aufweist, wobei an der ersten Wirkfläche (6) ein Öldruck anliegt, wobei mittels des Stellventils (5) ein Steuerkanal zur Beaufschlagung der zweiten Wirkfläche (7) mit dem Öldruck offenbar und schließbar ist, dadurch gekennzeichnet, dass mittels des Regelkolbens (4) ein Bypass (18) offenbar und schließbar ist, wobei der Bypass (18) eine Druckseite (19) der Ölpumpe (2) mit einer Saugseite (20) der Ölpumpe (2) verbindet. 1. Device (1) for pressure control of an oil pump (2), with a control piston (4) and with a control valve (5), wherein by means of the control piston (4) at least two pressure levels are adjustable, wherein the control piston (4) has a first effective area (6) and a second active surface (7), wherein on the first active surface (6) bears an oil pressure, by means of the control valve (5) a control channel for acting on the second effective surface (7) with the oil pressure is apparent and closable, characterized characterized in that by means of the control piston (4) a bypass (18) is apparent and closable, wherein the bypass (18) connects a pressure side (19) of the oil pump (2) with a suction side (20) of the oil pump (2).
2. Vorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass mindestens eine Kolbenkühldüse in Abhängigkeit der Schaltstellung des Stellventils (5) und somit in Abhängigkeit von der gewählten Druckstufe schaltbar ist, wobei in einer Hochdruckstufe die mindestens eine Kolbenkühldüse aktiviert ist, wobei in einer Niederdruckstufe die mindestens eine Kolbenkühldüse deaktiviert ist, wobei die mindestens eine Kolbenkühldüse einen Öffnungsdruck aufweist und der Öffnungsdruck zwischen dem Druck der Niederdruckstufe und dem Druck der Hochdruckstufe liegt. 2. Apparatus according to claim 1, characterized in that at least one piston cooling nozzle in response to the switching position of the control valve (5) and thus in response to the selected pressure level is switchable, wherein in a high-pressure stage, the at least one Kolbenkühldüse is activated, wherein in a low-pressure stage at least one piston cooling nozzle is deactivated, wherein the at least one piston cooling nozzle has an opening pressure and the opening pressure between the pressure of the low pressure stage and the pressure of the high-pressure stage is located.
3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Ölpumpe (2) als Innenzahnradpumpe oder als Zahnringpumpe ausgebildet ist. 3. Device according to claim 1 or 2, characterized in that the oil pump (2) is designed as an internal gear pump or as a gerotor pump.
4. Vorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass eine Hochdruckstufe dadurch realisiert ist, dass das Stellventil (5) stromlos gestaltet ist, wobei in der Hochdruckstufe der Steuerkanal (13) gesperrt ist und der Steuerkanal (13) über das Stellventil (5) mit einer Leitung (21 ) zur Ölwanne (3) verbunden ist und somit die zweite Wirkfläche druckentlastet ist, wobei in einer Niederdruckstufe das Stellventil (5) bestromt ist, wobei in der Niederdruckstufe der Steuerkanal (13) geöffnet ist und somit die zweite Wirkfläche (7) und die erste Wirkfläche (6) mit dem Öldruck entgegen einer auf den Regelkolben (4) drückenden Federkraft beaufschlagt ist. 4. Device according to one of the preceding claims, characterized in that a high-pressure stage is realized in that the control valve (5) is designed to be de-energized, wherein in the high-pressure stage of the control channel (13) is locked and the control channel (13) via the control valve (13). 5) is connected to a line (21) to the oil pan (3) and thus the second effective area is depressurized, wherein in a low pressure stage, the control valve (5) is energized, wherein in the low pressure stage of the control channel (13) is open and thus the second Working surface (7) and the first active surface (6) is acted upon by the oil pressure against a force acting on the control piston (4) spring force.
5. Vorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass an der dritten Fläche ein Pumpenausgangsdruck anliegt, wobei der Öldruck hinter einem Ölfilter (ÖF) und hinter einem Ölkühler (ÖK) abgezweigt ist, wobei der Öldruck niedriger als der Pumpenausgangsdruck ist. 5. Device according to one of the preceding claims, characterized in that on the third surface a pump outlet pressure is applied, wherein the oil pressure is branched off behind an oil filter (ÖF) and behind an oil cooler (ÖK), wherein the oil pressure is lower than the pump outlet pressure.
EP16722786.7A 2015-05-06 2016-05-04 Device for pressure regulation in an oil pump Active EP3292282B1 (en)

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

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EP3292282A1 true EP3292282A1 (en) 2018-03-14
EP3292282B1 EP3292282B1 (en) 2019-11-20

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DE (1) DE102015005682A1 (en)
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Publication number Priority date Publication date Assignee Title
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
CN112315036A (en) * 2020-11-27 2021-02-05 常州威图流体科技有限公司 Electronic cigarette active oil supply atomization system and electronic cigarette thereof

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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

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EP3292282B1 (en) 2019-11-20
WO2016177468A1 (en) 2016-11-10

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