EP1942277A2 - Dynamic pressure control for hydraulic pumps - Google Patents
Dynamic pressure control for hydraulic pumps Download PDFInfo
- Publication number
- EP1942277A2 EP1942277A2 EP20070122222 EP07122222A EP1942277A2 EP 1942277 A2 EP1942277 A2 EP 1942277A2 EP 20070122222 EP20070122222 EP 20070122222 EP 07122222 A EP07122222 A EP 07122222A EP 1942277 A2 EP1942277 A2 EP 1942277A2
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- EP
- European Patent Office
- Prior art keywords
- pressure
- control
- oil
- piston
- chamber
- 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
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
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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
- 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
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0238—Rotary pumps
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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
- F04C2270/04—Force
- F04C2270/042—Force radial
- F04C2270/0422—Force radial centrifugal
Definitions
- the invention relates to hydraulic pumps with adjustable delivery rates and delivery pressures, in particular so-called.
- Regular oil pumps for lubricating oil supply of internal combustion engines By controlling the flow rate and in particular the resulting controllable discharge pressure, a reduction of the drive power of hydraulic pumps is effected, which advantages for fuel economy and thus in the CO 2 exhaust gas emissions are achieved for internal combustion engines.
- the change in the additional force acting on the control piston is effected either by an electrical control of a control unit or speed dependent hydraulic, by a centrifugal switching valve or a variable speed control pressure generated so-called. Spiralnut on a journal of a conveyor gear.
- German patent application DE 102004007323 A1 describes a further control oil pump whose oil pressure is controlled hydraulically substantially dependent on the operating speed.
- a so-called. Fliehdruck is used, which is generated from the speed-dependent variable centrifugal force of oil in radially arranged oil holes of a conveyor gear.
- the centrifugal pressure acts on a differential pressure piston, the piston force transmits via a spring as an additional force to a control piston performing the oil pressure control.
- German patent application DE102006051575A1 describes for control oil pumps a solution for improving the control function, in which the pressure acting on the pressure side of the control oil pump discharge pressure is used for adjusting the flow rate to overcome the adjustment counteracting frictional forces.
- the exclusively hydraulic control of DE10237801 B4 by the speed-dependent variably generated control pressure of the spiral groove has the disadvantage that the control pressure generated in the relatively flat and long spiral groove of the correspondingly formed journal depends not only on the speed of the journal, but also substantially on the temperature-dependent oil viscosity. In this way, although the control piston acted upon by the control pressure obtains a speed-dependent control function which, however, is also influenced by temperature and therefore effects a desired regulation only in certain temperature ranges.
- centrifugal pressure control uses centrifugal effects for the pressure control of a control oil pump and thus operates largely independent of the temperature-dependent variable Oil viscosity.
- the centrifugal pressure is generated in radial oil holes of a conveyor gear, however, which are relatively expensive to manufacture and cause corresponding cost disadvantages.
- the invention has for its object to provide for control oil pumps a hydraulic control that performs largely independent of variable oil viscosities a variable-speed oil pressure control according to the oil pressure demand, for example, to be supplied with lubricating oil combustion engine, which is simple and inexpensive executable and has high reliability.
- This object is achieved according to the invention for control oil pumps according to claim 1 in a simple manner by the shear force of a rotating conveyor wheel is used on the located in a the oil wheel oil bag facing the pump for the pump control.
- the dynamic pressure acts according to the invention via two connections to a differential pressure piston, which transfers its force generated by the back pressure as an additional force to the control piston of the delivery amount, so that a substantially speed-dependent variable oil pressure control is achieved.
- the Fig. 1 shows an embodiment of an external gear control oil pump with inventive back pressure control.
- the pump housing 1 has a drive shaft 2 with a first feed wheel 3.
- the feed wheel 3 is in meshing engagement with a second feed wheel 4, which is part of a multi-part displacement unit 5.
- the displacement unit 5 is axially movably guided in the pump housing 1, so that depending on the axial overlap of the tooth engagement of the two conveyor gears 3 and 4, the flow rate of the control oil pump can be adjusted in a known manner, in Fig. 1 the delivery rate is approx. 65%.
- the displacement unit 5 has for storage of conveying wheel 4 on a journal 6, whose left end with a correspondingly large diameter 7, the displacement unit 5 in the pump housing 1 leads. At its right-hand end of the journal 6 is guided by a piston 8 mounted on it in the pump housing 1.
- the axial positioning of the displacement unit 5 is effected by forces acting on both sides of them.
- right-hand chamber 9 is constantly acting on a pressure line 10 to be controlled by the control oil pump oil pressure on the displacement unit 5, while from a left-side chamber 11 a prevailing in her control pressure as well as a spring 12 acting on the displacement unit 5.
- An arranged in the journal 6 control piston 13 which is constantly acted upon from the chamber 9 end face with oil pressure generated in cooperation with an associated control spring 14 in a known manner the control pressure in the chamber 11.
- the control piston 13 is this depending on the axial position of its groove 15th more or less both via a pressure bore 16, a groove 17 and a bore 18 with the acted upon by the oil pressure chamber 9 as well as a discharge hole 19, a bore 20 and an oil pocket 21 of the piston 8 with the unpressurized suction side of the control oil pump in variable pressure connection.
- the in the groove 15 in a known manner generated control pressure passes through a step tube 22 into the chamber 11 and controls the axial displacement of the displacement unit 5, the resulting flow rate of the conveyor gears 3 and 4 such that, for example, the demand oil pressure of an internal combustion engine in the chamber. 9 established.
- control piston 13 is further acted upon by a differential pressure piston 23 via a spring 24 with a variable additional force in order to influence the control pressure in the chamber 11 variable.
- the arranged in the large diameter 7 of the journal 6 differential pressure piston 23 is on the one hand with a first chamber 25 via a first conduit consisting of a bore 26 and a groove 27, and on the other hand with a second chamber 28 via a second line, consisting of a further bore 29, in pressure communication with a standing under pressure oil pocket 30.
- the bore 29 is opposite to the direction of rotation of the feed wheel 4 offset from the groove 27, which is in Fig. 1 is expressed by the other hatching of the vicinity of hole 29.
- the bores 26 and 29 are limited in terms of an advantageous throttling of the differential pressure piston 23 in their diameters and may have a bevel, for example, the chamfer 31 of the bore 29 for the purpose of asymmetric throttle action at one end.
- the depth of the oil pocket 30 is defined by the distance of its bottom 32 to the opposite feed wheel 4.
- a bypass bore 33 arranged in the piston 8 serves to limit the delivery pressure with axially minimal overlap of the meshing engagement of the conveyor gears 3 and 4.
- the Fig. 1 further shows a belonging to the control oil pump pressure line system, with a not visible behind the control oil pump connection port on the pump housing 1, via which the control oil pump feed oil, for example, to be supplied with lubricating oil combustion engine.
- the delivery oil under delivery pressure flows via a pressure line 34 through a filter 35, which may alternatively be designed as a filter-cooler module, and via a subsequent pressure line 36 to the engine.
- the pressure line 34 has a pressure relief valve 37 whose opening pressure is above the normal operating pressure of the delivery pressure in the pressure line 34.
- the pressure prevailing in the pressure line 36 oil pressure to the chamber 9 of the pump housing 1 is returned to the pump control.
- the pressure line 10 may have an electrically switchable solenoid valve 38 that depressurizes the pressure line 10 via its connection piece 39, for example when the oil pressure requirement of piston injection nozzles of an internal combustion engine increases temporarily.
- the control oil pump adjusted to maximum flow and then works temporarily as a conventional constant displacement pump with bypass control by deriving a partial flow through the pressure relief valve 37th
- Fig. 2 is the displacement unit 5 of the control oil pump in a cross section through the feed wheel 4 according to the in Fig. 1 indicated section AA shown. It communicates with the differential pressure piston 23 on the one hand via the groove 27 and the bore 26 and on the other hand over the offset in this embodiment, the groove 27 by 90 ° arranged bore 29 in pressure communication.
- An intake passage 40 and an opposite pressure channel 41 guide the flowing oil through the pump housing. 1
- the rotating feed wheel 4 transmits in the direction of rotation to the oil contained in the oil bag 30 a speed-dependent variable shear force, which causes a pressure drop in the oil bag 30, the so-called. Dynamic pressure.
- This back pressure acts as a pressure difference on the differential pressure piston 23, the bias increases its spring 24 on the control piston 13 with increasing back pressure and causes in a known manner an increase in the flow rate and the oil pressure of the control oil pump.
- the height of the oil pressure control used by the control oil pump Back pressure can be influenced essentially by the size of the angle between the groove 27 and the bore 29, in this embodiment 90 °, but also by the choice of the depth of the oil bag 30, the in Fig. 1 can be seen by appropriate distance of their bottom 32 to the opposite feed wheel 4.
- the influence of the oil viscosity can be reduced to the oil pressure control and predominantly a desired speed-dependent control of the flow rate and the delivery pressure can be achieved.
- the two bores 26 and 29 can each act as throttles with correspondingly small diameters selected and thus produce an advantageous for the control of the delivery pressure of the control oil pump damping of the differential pressure piston 23.
- Fig. 3 is the standard oil pump of Fig. 1 shown in a side view of the intake passage 40.
- the two visible in the intake passage 40 feed gears 3 and 4 are by a maximum adjustment of the displacement unit 5 with left-side stop position on the pump housing 1 in the lowest axial overlap for a minimum flow.
- the right side of the conveyor wheel 4 adjacent piston 8 is in this case in a position in which his standing under pressure bypass bore 33 is in register with the intake passage 40, whereby a return flow of feed oil into the intake passage 40 takes place.
- This backflow of production oil through the bypass bore 33 avoids unacceptably high oil pressure in extreme operating conditions in which the minimum flow is still too high.
- the Fig. 4 shows the control oil pump of Fig. 3 In a sectional view through the bypass bore 33. It connects with minimal axial overlap of the meshing engagement of the conveyor gears 3 and 4, the pressure channel 41 with the intake passage 40, so that a portion of the conveying oil flows back to the intake passage 40 and correspondingly too high a delivery pressure is avoided.
- the piston 8 has a conveying wheel 3 enclosing, arcuate recess 42 which limits the diameter of the bypass bore 33 with its closest distance to the journal 6.
- its end located at the pressure channel 41 may, for example, have a conical extension 43.
- the Fig. 5 shows the control oil pump in an angled sectional view corresponding to section CC of Fig. 4 by the displacement unit 5.
- the control piston 13 generates accordingly Fig. 1 from the voltage applied in the chamber 9 oil pressure and the pressure prevailing in the suction bag 21 suction pressure acting in the chamber 11 control pressure, the control is supplied in normal operation with filtered oil from the chamber 9.
- control pressure in the chamber 11 can be increased in the normal control operation of the control piston 13 to a maximum of the pressure level of the oil pressure of the chamber 9, wherein the spring 12 from a certain friction of the displacement unit 5, a readjustment in terms of increased flow then can no longer perform and Oil pressure drop results.
- the piston 8 in its upper section on a high discharge pressure pressure pocket 50 which supplies the delivery pressure via a bore 51 with a filter element 52 a bore 53 of the journal 6, the at normal control operation of the control piston 13 in Fig. 5 still kept closed.
- the Fig. 6 shows in contrast to Fig. 5 the control piston 13 in a shifted to the right position, which is set at a low in the chamber 9 oil pressure.
- the control piston 13 closes in this position, the bore 18 as well as the bore 19 of the journal 6, so that the pressure connections of its groove 15 to the chamber 9 and also to the suction bag 21 are interrupted.
- the groove 15 is now via the bore 53 and the bore 51 in pressure communication with the pressure pocket 50, the high delivery pressure of the control piston 13 fed as a control pressure in the chamber 11 and adjusted according to the displacement unit 5 to the right in terms of a flow rate and oil pressure increase.
- the control piston 13 moves back to the left in its original control position accordingly Fig. 5 ,
- control oil pump with a dynamic pressure control allows in a simple manner increasing with the speed of oil pressure, for example, approximately according to the oil pressure demand of a to be supplied with lubricating oil combustion engine.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
Die Erfindung betrifft Hydraulikpumpen mit verstellbaren Fördermengen und Förderdrücken, insbesondere sog. Regelölpumpen für die Schmierölversorgung von Verbrennungsmotoren. Durch eine Regelung der Fördermenge und insbesondere auch des dadurch regelbaren Förderdruckes wird eine Reduzierung der Antriebsleistung von Hydraulikpumpen bewirkt, wodurch für Verbrennungsmotoren Vorteile im Kraftstoffverbrauch und entsprechend in der CO2-Abgasemission erzielt werden.The invention relates to hydraulic pumps with adjustable delivery rates and delivery pressures, in particular so-called. Regular oil pumps for lubricating oil supply of internal combustion engines. By controlling the flow rate and in particular the resulting controllable discharge pressure, a reduction of the drive power of hydraulic pumps is effected, which advantages for fuel economy and thus in the CO 2 exhaust gas emissions are achieved for internal combustion engines.
Aus der deutschen Patentschrift
Die deutsche Patentanmeldung
Die deutschen Patentanmeldung
Weiterhin ist aus der deutschen Patentanmeldung
Die Regelungen der bekannten Regelölpumpen stellen einen gewissen Zusatzaufwand dar und sind insbesondere bei elektrischer Ansteuerung mit entsprechenden Mehrkosten verbunden.The regulations of the known control oil pumps represent a certain additional effort and are particularly associated with electrical control with corresponding additional costs.
Die ausschließlich hydraulische Regelung der
Die Öldruckumschaltung durch das in einem Förderzahnrad angeordnete Fliehkraft-Schaltventil der
Die aus der
Der Erfindung liegt die Aufgabe zugrunde, für Regelölpumpen eine hydraulische Regelung zu schaffen, die weitgehend unabhängig von veränderlichen Ölviskositäten eine drehzahlvariable Öldruckregelung entsprechend dem Öldruckbedarf beispielsweise eines mit Schmieröl zu versorgenden Verbrennungsmotors durchführt, die einfach und kostengünstig ausführbar ist und eine hohe Betriebssicherheit aufweist.The invention has for its object to provide for control oil pumps a hydraulic control that performs largely independent of variable oil viscosities a variable-speed oil pressure control according to the oil pressure demand, for example, to be supplied with lubricating oil combustion engine, which is simple and inexpensive executable and has high reliability.
Diese Aufgabe wird für Regelölpumpen erfindungsgemäß entsprechend Anspruch 1 in einfacher Weise dadurch gelöst, indem für die Pumpenregelung die Scherkraftwirkung eines rotierenden Förderrades auf das in einer dem Förderrad zugewandten Öltasche befindliche Öl genutzt wird. Die im Wesentlichen drehzahlabhängige Scherkraft erzeugt in Bewegungsrichtung des Förderrades über der Länge der Öltasche einen Druckanstieg, der hier als Staudruck bezeichnet wird. Der Staudruck wirkt erfindungsgemäß über zwei Verbindungen an einem Differenzdruckkolben, der seine vom Staudruck erzeugte Kraft als Zusatzkraft auf den Regelkolben der Fördermengenverstelleinrichtung überträgt, so dass eine im Wesentlichen drehzahlabhängig veränderliche Öldruckregelung erzielt wird.This object is achieved according to the invention for control oil pumps according to
Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung von in Zeichnungen schematisch dargestellten Ausführungsbeispielen. Es zeigen:
-
Fig. 1 : eine Außenzahnrad-Regelölpumpe mit Staudruck-Regelung bei reduzierter Fördermenge in Schnittansicht; -
Fig. 2 : eine Schnittansicht der Außenzahnrad-Regelölpumpe entsprechend Schnitt A-A vonFig. 1 ; -
Fig. 3 : eine Seitenansicht der Regelölpumpe vonFig. 1 bei minimaler Fördermenge; -
Fig. 4 : eine Schnittansicht entsprechend Schnitt B-B vonFig. 3 durch die Bypassbohrung; -
Fig. 5 : eine Schnittansicht der Regelölpumpe entsprechend Schnitt C-C vonFig. 4 ; -
Fig. 6 : die Schnittansicht vonFig. 5 mit anderer Position des Regelkolbens;
-
Fig. 1 : an external gear oil pump with back pressure control at reduced flow rate in sectional view; -
Fig. 2 : A sectional view of the external gear oil pump according to section AA ofFig. 1 ; -
Fig. 3 : a side view of the control oil pump ofFig. 1 at minimum flow rate; -
Fig. 4 : a sectional view corresponding to section BB ofFig. 3 through the bypass hole; -
Fig. 5 : A sectional view of the control oil pump according to section CC fromFig. 4 ; -
Fig. 6 : the sectional view ofFig. 5 with another position of the control piston;
Die
Die Verschiebeeinheit 5 weist zur Lagerung von Förderrad 4 einen Laufzapfen 6 auf, dessen linkes Ende mit einem entsprechend großen Durchmesser 7 die Verschiebeeinheit 5 im Pumpengehäuse 1 führt. Am seinem rechtsseitigen Ende ist der Laufzapfen 6 von einem auf ihm befestigten Kolben 8 im Pumpengehäuse 1 geführt.The
Die axiale Positionierung der Verschiebeeinheit 5 erfolgt durch beidseitig auf sie einwirkende Kräfte. In einer im Pumpengehäuse 1 rechtsseitigen Kammer 9 wirkt ständig über eine Druckleitung 10 ein von der Regelölpumpe zu regelnder Öldruck auf die Verschiebeeinheit 5, während von einer linksseitigen Kammer 11 ein in ihr herrschender Regeldruck wie auch eine Feder 12 auf die Verschiebeeinheit 5 einwirken. Ein im Laufzapfen 6 angeordneter Regelkolben 13, der aus der Kammer 9 ständig stirnseitig mit Öldruck beaufschlagt ist, erzeugt im Zusammenwirken mit einer zugehöriger Regelfeder 14 in bekannter Weise den Regeldruck in der Kammer 11. Der Regelkolben 13 steht hierzu je nach axialen Position seiner Nut 15 mehr oder weniger sowohl über eine Druckbohrung 16, eine Nut 17 und eine Bohrung 18 mit der vom Öldruck beaufschlagten Kammer 9 wie auch über eine Entlastungsbohrung 19, eine Bohrung 20 und eine Öltasche 21 des Kolbens 8 mit der drucklosen Ansaugseite der Regelölpumpe in veränderlicher Druckverbindung. Der in der Nut 15 in bekannter Weise erzeugte Regeldruck gelangt über ein Stufenrohr 22 in die Kammer 11 und regelt über die axiale Position der Verschiebeeinheit 5 die resultierende Fördermenge der Förderzahnräder 3 und 4 derart ein, das sich beispielsweise der Bedarfs-Öldruck eines Verbrennungsmotors in der Kammer 9 einstellt.The axial positioning of the
Der Regelkolben 13 ist weiterhin von einem Differenzdruckkolben 23 über eine Feder 24 mit einer variablen Zusatzkraft beaufschlagt, um den Regeldruck in der Kammer 11 veränderlich zu beeinflussen.The
Der im großen Durchmesser 7 des Laufzapfens 6 angeordneter Differenzdruckkolben 23 steht einerseits mit einer ersten Kammer 25 über eine erste Leitung, bestehend aus einer Bohrung 26 und einer Nut 27, und andererseits mit einer zweiten Kammer 28 über eine zweite Leitung, bestehend aus einer weiteren Bohrung 29, in Druckverbindung mit einer unter Förderdruck stehenden Öltasche 30. Die Bohrung 29 ist entgegen der Drehrichtung des Förderrades 4 versetzt zu der Nut 27 angeordnet, was in
Eine im Kolben 8 angeordnete Bypassbohrung 33 dient der Begrenzung des Förderdruckes bei axial minimaler Überdeckung des Zahneingriffes der Förderzahnräder 3 und 4.A
Die
Die Druckleitung 10 kann ein elektrisch schaltbares Magnetventil 38 aufweisen, dass beispielsweise bei temporär erhöhtem Öldruckbedarf von Kolbenspritzdüsen eines Verbrennungsmotors die Druckleitung 10 über ihren Stutzen 39 druckentlastet. Hierdurch verstellt sich die Regelölpumpe auf maximale Fördermenge und arbeitet dann temporär als herkömmliche Konstantpumpe mit Bypassregelung durch Ableitung einer Teilfördermenge über das Überdruckventil 37.The
In
Ein Ansaugkanal 40 und ein ihm gegenüberliegender Druckkanal 41 leiten das strömende Förderöl durch das Pumpengehäuse 1.An
Das rotierende Förderrades 4 überträgt in Drehrichtung auf das in der Öltasche 30 befindliche Förderöl eine drehzahlabhängig veränderliche Scherkraft, die in der Öltasche 30 ein Druckgefälle, den sog. Staudruck hervorruft. Dieser Staudruck wirkt als Druckdifferenz am Differenzdruckkolben 23, der bei steigendem Staudruck die Vorspannung seine Feder 24 auf den Regelkolben 13 erhöht und in bekannter Weise eine Erhöhung der Fördermenge bzw. des Öldruckes der Regelölpumpe bewirkt.The
Die Höhe des für die Öldruckregelung der Regelölpumpe genutzten Staudruckes kann im Wesentlichen durch die Größe des Winkels zwischen der Nut 27 und der Bohrung 29, in diesem Ausführungsbeispiel 90°, beeinflusst werden, weiterhin aber auch durch die Wahl der Tiefe der Öltasche 30, die in
Während eine geringe Tiefe der Öltasche 30, beispielsweise nur 1 mm, einen sehr hohen Staudruck erzeugt, bewirkt eine größere Tiefe einen den Staudruck senkenden Druckausgleich durch gegenüberliegend zum Förderrad 4 am Boden 32 gegen die Drehrichtung rückströmendes Förderöl vom Ende zum Anfang der Öltasche 30. Hierdurch kann beispielsweise der Einfluss der Ölviskosität auf die Öldruckregelung reduziert und überwiegend eine gewünscht drehzahlabhängige Regelung der Fördermenge bzw. des Förderdruckes erzielt werden.While a small depth of the
Die beiden Bohrungen 26 und 29 können jeweils bei entsprechend klein gewählten Durchmessern als Drosseln wirken und damit eine für die Regelung des Förderdruckes der Regelölpumpe vorteilhafte Bedämpfung des Differenzdruckkolbens 23 hervorrufen.The two bores 26 and 29 can each act as throttles with correspondingly small diameters selected and thus produce an advantageous for the control of the delivery pressure of the control oil pump damping of the
In
Die
Der Kolben 8 weist eine das Förderrad 3 umschließende, bogenförmige Ausnehmung 42 auf, die mit ihrem engsten Abstand zum Laufzapfen 6 den Durchmesser der Bypassbohrung 33 begrenzt. Im Sinne einer Entdrosselung der Bypassbohrung 33 kann ihr am Druckkanal 41 befindliches Ende beispielsweise eine konusähnliche Erweiterung 43 aufweisen.The
Die
Im Falle einer der Verstellung der Verschiebeeinheit 5 entgegenwirkenden, erhöhten Reibung zwischen der Verschiebeeinheit 5 und dem sie führenden Pumpengehäuse 1, beispielsweise bei erhöhtem, quer auf die Verschiebeeinheit 5 wirkendem Förderdruck infolge eines erhöhten Druckverlustes des Filters 34, kann es zu Regelungsproblemen kommen. Der Regeldruck in der Kammer 11 kann im normalen Regelbetrieb vom Regelkolben 13 maximal auf das Druckniveau des Öldruckes der Kammer 9 gesteigert werden, wobei die Feder 12 ab einer gewissen Reibung der Verschiebeeinheit 5 eine Nachregelung im Sinne einer erhöhten Fördermenge dann nicht mehr durchführen kann und ein Öldruckeinbruch resultiert.In the case of an adjustment of the
Zur Vermeidung dieser für einen Verbrennungsmotor kritischen Betriebssituation bei zu niedrigem Öldruck weist der Kolben 8 in seinem oberen Schnittbereich eine unter hohem Förderdruck stehende Drucktasche 50 auf, die den Förderdruck über eine Bohrung 51 mit einem Filterelement 52 einer Bohrung 53 des Laufzapfens 6 zuführt, die bei normalem Regelbetrieb vom Regelkolben 13 in
Die
Die erfindungsgemäße Ausbildung einer Regelölpumpe mit einer Staudruck-Regelung ermöglicht auf einfache Weise einen mit der Drehzahl ansteigenden Öldruck beispielsweise etwa entsprechend dem Öldruckbedarf eines mit Schmieröl zu versorgenden Verbrennungsmotors.The inventive design of a control oil pump with a dynamic pressure control allows in a simple manner increasing with the speed of oil pressure, for example, approximately according to the oil pressure demand of a to be supplied with lubricating oil combustion engine.
Claims (7)
dadurch gekennzeichnet, dass die Hydraulikpumpe als Außenzahnrad-Regelölpumpe ausgeführt und ihre Fördermengenverstelleinrichtung als Verschiebeeinheit (5) mit einer vom Öldruck beaufschlagten Kammer (9) und einer vom Regeldruck beaufschlagten Kammer (11) ausgebildet ist.Speed-dependent pressure control for hydraulic pumps according to claim 1,
characterized in that the hydraulic pump designed as an external gear oil pump and their Fördermengenverstelleinrichtung is formed as a displacement unit (5) with an oil pressure applied to the chamber (9) and acted upon by the control pressure chamber (11).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE200710001066 DE102007001066A1 (en) | 2007-01-03 | 2007-01-03 | Rotation speed dependent pressure controller for hydraulic pumps, particularly for lubricating pumps of internal combustion engines, has two conveyor wheels and oil pocket, extending adjacent to conveyor wheel in rotational direction |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1942277A2 true EP1942277A2 (en) | 2008-07-09 |
Family
ID=38268349
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20070122222 Withdrawn EP1942277A2 (en) | 2007-01-03 | 2007-12-04 | Dynamic pressure control for hydraulic pumps |
Country Status (2)
Country | Link |
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EP (1) | EP1942277A2 (en) |
DE (1) | DE102007001066A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013001750A1 (en) | 2013-01-31 | 2014-07-31 | Volkswagen Aktiengesellschaft | Method for controlling oil pressure for combustion engine, involves keeping oil pressure in first speed range of engine constant and increasing oil pressure in second speed range with increasing speed so as to be above first speed range |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007039589A1 (en) | 2007-08-22 | 2009-02-26 | Voigt, Dieter, Dipl.-Ing. | Regular oil pump with adjustment-dependent oil pressure control |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10237801B4 (en) | 2002-01-12 | 2004-05-27 | Voigt, Dieter, Dipl.-Ing. | Device for regulating the pressure of hydraulic pumps |
DE102004007323A1 (en) | 2004-02-14 | 2005-08-04 | Voigt, Dieter, Dipl.-Ing. | Pressure regulator for automotive oil pump has first piston operating in conjunction with a second variable-pressure piston |
DE102007008177A1 (en) | 2006-08-29 | 2007-07-26 | Voigt, Dieter, Dipl.-Ing. | External toothing pinion-type control oil pump for lubrication of combustion engines, has intermeshing feed pinions with axially displaceable unit |
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 |
-
2007
- 2007-01-03 DE DE200710001066 patent/DE102007001066A1/en not_active Withdrawn
- 2007-12-04 EP EP20070122222 patent/EP1942277A2/en not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10237801B4 (en) | 2002-01-12 | 2004-05-27 | Voigt, Dieter, Dipl.-Ing. | Device for regulating the pressure of hydraulic pumps |
DE102004007323A1 (en) | 2004-02-14 | 2005-08-04 | Voigt, Dieter, Dipl.-Ing. | Pressure regulator for automotive oil pump has first piston operating in conjunction with a second variable-pressure piston |
DE102007008177A1 (en) | 2006-08-29 | 2007-07-26 | Voigt, Dieter, Dipl.-Ing. | External toothing pinion-type control oil pump for lubrication of combustion engines, has intermeshing feed pinions with axially displaceable unit |
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 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013001750A1 (en) | 2013-01-31 | 2014-07-31 | Volkswagen Aktiengesellschaft | Method for controlling oil pressure for combustion engine, involves keeping oil pressure in first speed range of engine constant and increasing oil pressure in second speed range with increasing speed so as to be above first speed range |
Also Published As
Publication number | Publication date |
---|---|
DE102007001066A1 (en) | 2007-08-02 |
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