EP1730405A1 - Regulation de la pression de pompes a huile en fonction du regime du moteur - Google Patents

Regulation de la pression de pompes a huile en fonction du regime du moteur

Info

Publication number
EP1730405A1
EP1730405A1 EP04799011A EP04799011A EP1730405A1 EP 1730405 A1 EP1730405 A1 EP 1730405A1 EP 04799011 A EP04799011 A EP 04799011A EP 04799011 A EP04799011 A EP 04799011A EP 1730405 A1 EP1730405 A1 EP 1730405A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
piston
spring
speed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP04799011A
Other languages
German (de)
English (en)
Inventor
Dieter Dipl.-Ing. Voigt
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE2003157619 external-priority patent/DE10357619A1/de
Priority claimed from DE200410007323 external-priority patent/DE102004007323A1/de
Priority claimed from DE200410012726 external-priority patent/DE102004012726A1/de
Application filed by Individual filed Critical Individual
Publication of EP1730405A1 publication Critical patent/EP1730405A1/fr
Withdrawn legal-status Critical Current

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
    • F04C14/18—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
    • 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
    • F04C2270/05—Speed
    • 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
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular

Definitions

  • the invention relates to the control of the delivery pressure of hydraulic pumps. It relates, in particular, to a speed-dependent pressure regulation of so-called control oil pumps for the lubricating oil supply of internal combustion engines, which have a delivery quantity adjustment device and for their pressurization a control piston for generating a control pressure which is used to vary the delivery pressure of a device with a variable additional force can be applied.
  • Hydraulic pumps with a controllable delivery rate have reduced oil pump drive capacities compared with hydraulic pumps with a bypass control and are already being used as so-called control oil pumps with a constantly regulated delivery pressure for supplying lubricating oil to internal combustion engines.
  • control oil pumps corresponding to the largely speed-dependent oil pressure requirement of internal combustion engines, that the potential for improvement of control oil pumps can be almost completely utilized.
  • the resulting drive performance advantages of control oil pumps can make a significant contribution to reducing fuel consumption of internal combustion engines.
  • a control oil pump with variable oil pressure control is known from the patent DE 10237911 B4 and also described in WO 03/058071. In the former case, it is designed as an external gear pump with a displacement unit that executes the displacement adjustment with an axially variable meshing width.
  • the regulation of the operating oil pressure is carried out via the variable flow rate, wherein the axially variable positioning of the displacement unit is adjusted by a regulating pressure acting on it, which is provided by a control piston.
  • the control piston has a control spring and is acted upon counteracting the operating oil pressure, where he works as an oil pressure sensor and is designed for a corresponding desired operating oil pressure. It has control grooves communicating with oil bores, which generate the control pressure for acting on the displacement unit.
  • An embodiment of DE 10237911 B4 shows a two-stage switching of the operating oil pressure by a speed-dependent actuated by an acting centrifugal force switching valve.
  • a continuously variable control of the operating oil pressure by an electrical adjusting device of the control piston which is controlled by the control unit of the internal combustion engine.
  • a further exemplary embodiment has a spiral groove on a rotating shaft, in which speed-dependent oiling forces produce a pressure acting on the control piston for oil pressure regulation.
  • an advantageously stepless control of the operating oil pressure is either associated with an increased electrical control effort or, in the case of spiral pressure control, can only be used within a limited temperature range due to the temperature-variable oil viscosity.
  • the object is therefore achieved in a second step according to the invention in a simple manner in that the control piston of a control oil pump is acted upon both with operating oil pressure as well as with an additional centrifugal pressure, which is generated dependent on the centrifugal force of an oil column in a rotating radial bore.
  • 1 shows an external gear-control oil pump according to the invention with a control piston arranged in the pump housing
  • 2 shows an oil pressure diagram with the oil pressure requirement of an internal combustion engine and the oil pressure curve of a control oil pump according to the invention
  • Fig. 3 an external gear oil pump according to Figure 1, in which the control piston, however, has a decoupled differential pressure piston.
  • FIG. 4 shows a section of an external gear oil pump with an arrangement of the oil pressure control according to the invention in its displacement unit;
  • FIG. 5 shows an alternative to Figure 4 arrangement of a solenoid valve for oil pressure increase.
  • Fig. 1 shows a first embodiment of an external gear control oil pump according to the invention for an internal combustion engine, in which the oil pressure control is performed by a control piston 1, which is arranged in a pump housing 2.
  • a mounted in a housing cover 3 drive shaft 4 carries a first feed wheel 5, which is in meshing engagement with a second feed wheel 6.
  • the feed wheel 6 is mounted on a stationary pin 7, the right side of the feed wheel 6 a pressure piston 8 and the left side carries a spring piston 9.
  • the meshing width of the conveyor wheels 5 and 6 can be varied, whereby a change in the flow rate of the control oil pump possible in a known manner is.
  • the axial displacement of the displacement unit 10 takes place as a function of the external forces acting on them. While the pressure piston 8 is constantly acted upon by the operating oil pressure acting in its chamber 11, here tapped behind an oil filter 32 as the supply pressure for the internal combustion engine, the force of a restoring spring 12 and a pressure force of a control pressure acting in the spring chamber 13 act on the spring piston 9. The control pressure is generated as required by the control piston 1 in a known manner and fed via a control bore 14 in the spring chamber 13.
  • the control piston 1 is constantly acted upon at its front-side active surface 15 via its central bore with operating oil pressure.
  • a the operating oil pressure counteracting control spring 16 of the control piston 1 is designed for a certain basic operating oil pressure, for example, 1, 0 bar.
  • a control pin 17 of the control piston 1 acted upon with operating oil pressure, left-side pressure groove 18 and one with the Environment associated, right-hand relief groove 19, a corresponding control pressure is regulated in the spring chamber 13 in a known manner via the control bore 14.
  • This control pressure sets via the axial positioning of the displacement unit 10, the required for a given nominal operating oil flow rate.
  • the operating as oil pressure sensor control piston 1 reacts with a corresponding axial displacement, so that the pressure prevailing in the spring chamber 13 control pressure is either increased or decreased and a flow adjustment for the purpose of oil pressure correction to the set operating oil pressure.
  • the control piston 1 is acted upon by an additional force.
  • he has a differential pressure piston 20 for this purpose. While a reference pressure surface 21 of the differential pressure piston 20 is constantly acted upon by a pressure connection 22 with the pressure prevailing in a pressure chamber 23 of the pump housing 2 discharge pressure, is a reference pressure surface 21 opposite centrifugal pressure surface 24 hydraulically via a pressure connection 25 with the inner end of a radial bore 26 of the rotary feed wheel fifth in pressure connection. The radially outwardly ending radial bore 26 in a tooth head of the rotating feed wheel 5 is acted upon by the feed pressure of the pressure chamber 23 in the rotational angle position of feed wheel 5 shown.
  • the centrifugal force of the oil in the radial bore 26 generates a radially outwardly directed, speed-dependent centrifugal pressure, so that the pressure acting from the pressure chamber 23 to the radial bore 26 discharge pressure is reduced at its radially inner end to the centrifugal pressure.
  • the two pressure connections 22 and 25 of the differential pressure piston 20 or also the drive pin 29 may contain filters, for example the filters 30 and filters 31, to avoid contamination-related malfunctions.
  • FIG. 2 shows an oil pressure diagram for an internal combustion engine with an oil supply through the control oil pump shown in FIG.
  • This auxiliary force of the differential pressure piston 20, which supports the force of the control spring 16, finally sets the operating oil pressure PR of the internal combustion engine, which is controlled by the control oil pump in accordance with the invention as a function of rotational speed, which is derived from the formula PR Po + PF x calculated.
  • the operating oil pressure PR must always be greater than the oil pressure requirement PB of the internal combustion engine
  • FIG. 3 A further illustrated in Fig. 3 embodiment of a control oil pump shows over the embodiment in Fig. 1 a modified control piston 41. He has a now axially displaceably guided on him differential pressure piston 42, which from the centrifugal pressure of the radial bore 26 of the feed wheel fifth resulting additional force via a spring 43 and a spring system 44 transmits to the control piston 41.
  • the spring 43 is almost powerless relaxed at the differential pressure piston 42 at.
  • the differential pressure piston 42 moves under increasing bias of the spring 43 to the right, with a corresponding additional force is transmitted to the control piston 41.
  • the regulation of the operating oil pressure applied to the active surface 45 now takes place only at a correspondingly increased pressure level in the manner mentioned.
  • the operating oil pressure can be largely adapted to the oil pressure requirement of an internal combustion engine to be supplied, so that corresponding drive power advantages result from the oil pressure minimization.
  • increased oil pressure demand of the internal combustion engine for example, for a quick operation of a hydraulic camshaft adjuster can be achieved by a controlled by an engine control unit solenoid valve 47, a pressure relief at the normally acted upon by centrifugal centrifugal pressure surface 48 of the differential pressure piston 42.
  • the delivery pressure which always acts on the reference pressure surface 49 of the differential pressure piston 42 then pushes the differential pressure piston 42 against its abutment 46, so that the spring 43 is pretensioned to a maximum extent and then an independently controlled speed an increased operating oil pressure of, for example, 5 bar.
  • a throttle 50 located in the pressure connection 25 causes a more effective pressure reduction at the centrifugal pressure surface 48 of the differential pressure piston 42 when the solenoid valve 47 is actuated.
  • the displacement unit 60 has a feed wheel 61 with a centrifugal pressure generating, arranged obliquely to the centrifugal force radial bore 62.
  • the feed wheel 61 is rotatably mounted on a hollow pin 63, which is integrally formed with a spring piston 64.
  • the axial position of the displacement unit 60 and thus the respective delivery rate of the external gear oil pump is on the one hand by the pressure acting on the pressure piston 65 in its chamber 66 operating oil pressure and on the other by counteracting Force on the spring piston 64 dependent, which are generated on the one hand by a return spring 67 and on the other by the force acting in its spring chamber 68 control pressure.
  • the control pressure is generated in this embodiment by an arranged in the pin 63 annular control piston 69. On the one hand, it is acted upon by the operating oil pressure acting in the chamber 66 and, on the other hand, it is supported by a control spring 70. It rests against a collar 71 of a pressure tube 72, which feeds the control pressure generated by the control piston 69 into the spring chamber 68 via its central bore 74. The collar 71 on the pressure tube 72 is supported on a cover 73 fixed in the spring piston 64. The pressure pipe 72 penetrates the control piston 69 sealingly with a sliding seat.
  • Its central bore 74 which is closed at its end facing the chamber 66, is constantly in pressure communication with a groove 75 of the control piston 69, for example via corresponding transverse bores in the pressure pipe 72 and in the control piston 69.
  • the groove 75 of the control piston 69 is in the shown, middle control position simultaneously with a supplied with operating oil pressure from the chamber 66 pressure bore 76 as well as with a discharge hole 78 which is connected to a suction chamber 77, slightly in overlap. Deviations from the desired operating oil pressure, which acts on the end face of the control piston 69 from the chamber 66, are automatically corrected by axial control movements of the control piston 69 in the manner already mentioned about acting in the spring chamber 68 control pressure by an axial displacement of the displacement controlling the displacement unit 60 ,
  • a differential pressure piston 79 is arranged, which is axially movably mounted on a guide sleeve 80 in the cover 73 and the pivot pin 63 and according to the invention via a spring 81 elastically an additional force can be transmitted to the control piston 69.
  • the in a pressure pocket 82 of the spring piston 64 constantly acting delivery pressure of the control oil pump is on the one hand via a connection 83 of the spring piston 64 and on the other via the oblique radial bore 62 of the feed wheel 61, a directed
  • this delivery pressure is reduced in the radial bore 62 by the centrifugal pressure which acts as a function of the rotational speed, so that effectively only the centrifugal pressure generates an additional force on the differential pressure piston 79.
  • This additional force generated by the differential pressure piston 79 is limited in its abutment against a stop 85 by a then maximum bias of the spring 81, so that the adjusted, highest operating oil pressure of the control oil pump is then limited, for example to 5 bar.
  • the cavities in the pin 63 must be pressure-free.
  • a temporary increase in the operating oil pressure with increased oil pressure requirement of the internal combustion engine is also possible with an arrangement of the control piston 69 in the displacement unit 60.
  • a line 88 which is under operating oil pressure, has a solenoid valve 89 which, when electrically actuated by the engine control unit via a throttle bore 90, carries out a pressure increase superimposed on the control pressure of the spring chamber 68.
  • the displacement unit 60 of the return spring 67 to the right pushed into a position of increased oil flow with resulting increase in the operating oil pressure.
  • a pressure relief valve 91 limits the pressure in the spring chamber 68 to a certain value, so that the operating oil pressure acting in the chamber 66 can only increase to a corresponding maximum value. In this then speed-independent, maximum operating oil pressure, the control oil pump continues to work with active flow control, the control piston 69 is then no function.
  • FIG. 5 shows, as an alternative to FIG. 4, a further possible embodiment of an external gear control oil pump with a centrifugal pressure control integrated in the displacement unit 60.
  • a solenoid valve 93 is arranged, which is closed at a predetermined by the engine control unit raising the operating oil pressure and simultaneously depressurized via a nozzle 94, the chamber 66.
  • the return spring 67 then moves the displacement unit 60 to the position of maximum flow rate with a resulting increase in the operating oil pressure. Because of the then inactive flow rate control, however, a conventional bypass control with a pressure relief valve 95 is now required to limit the maximum operating oil pressure to, for example, 6 bar.
  • control piston 69 which is acted upon by operating oil pressure from the chamber 66, only supports itself via a prestressed control spring 97 on the differential pressure piston 79.
  • this simplified version has a somewhat different control characteristic compared with the embodiment in FIG. 4, since the additional force generated at the differential pressure piston 79 by centrifugal pressure can only influence the pressure regulation above a certain operating speed when the pretensioning force of the control spring 96 is overcome.
  • An oil-filled throttle chamber 97 formed between the cover 73 of the guide sleeve 80 of the differential pressure piston 79 and the collar 71 of the pressure tube 72 can steam the movement of the differential pressure piston 79 with a suitable choice of play between the guide sleeve 80 and the collar 71.
  • the control device according to the invention utilizes the centrifugal force caused by centrifugal force centrifugal pressure in the oil-filled radial bores of rotating components for speed-dependent oil pressure control of control oil pumps.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

La pression d'huile de pompes à huile réglables utilisées pour fournir du lubrifiant à des moteurs à combustion interne est réglée en fonction du régime du moteur par un piston de régulation (1) qui commande hydrauliquement le réglage du refoulement et sur lequel un piston à pression différentielle (20) exerce une force additionnelle variable. A cet effet, une force centrifuge variable en fonction du régime du moteur est générée dans un alésage radial (26) d'une roue de refoulement en rotation et appliquée au piston à pression différentielle (20).
EP04799011A 2003-12-10 2004-11-29 Regulation de la pression de pompes a huile en fonction du regime du moteur Withdrawn EP1730405A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE2003157619 DE10357619A1 (de) 2003-12-10 2003-12-10 Einrichtung zur drehzahlabhängigen Druckregelung von Ölpumpen
DE200410007323 DE102004007323A1 (de) 2004-02-14 2004-02-14 Druckregelung für Ölpumpen
DE200410012726 DE102004012726A1 (de) 2004-03-16 2004-03-16 Durckanhebung für Regelölpumpen
PCT/IB2004/003910 WO2005057013A1 (fr) 2003-12-10 2004-11-29 Regulation de la pression de pompes a huile en fonction du regime du moteur

Publications (1)

Publication Number Publication Date
EP1730405A1 true EP1730405A1 (fr) 2006-12-13

Family

ID=34681803

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04799011A Withdrawn EP1730405A1 (fr) 2003-12-10 2004-11-29 Regulation de la pression de pompes a huile en fonction du regime du moteur

Country Status (4)

Country Link
US (1) US20070111855A1 (fr)
EP (1) EP1730405A1 (fr)
JP (1) JP2007514097A (fr)
WO (1) WO2005057013A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1911974A1 (fr) * 2006-10-11 2008-04-16 Dieter Dipl.-Ing. Voigt Réglage de la pression pour pompes à huile régulée à denture extérieure
DE102006051575A1 (de) * 2006-11-02 2007-09-13 Voigt, Dieter, Dipl.-Ing. Druckregelung für Außenzahnrad-Regelölpumpen
DE102007039589A1 (de) * 2007-08-22 2009-02-26 Voigt, Dieter, Dipl.-Ing. Regelölpumpe mit verstellwegabhängiger Öldruckregelung
WO2011009455A2 (fr) * 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à piston axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
JP5950583B2 (ja) * 2011-03-27 2016-07-13 株式会社山田製作所 ポンプ装置
WO2013032577A2 (fr) * 2011-08-29 2013-03-07 Exxonmobil Upstream Research Company Système et procédé d'actionnement hydraulique à grande vitesse
JP6029878B2 (ja) * 2012-07-06 2016-11-24 株式会社山田製作所 制御バルブ
US9951771B2 (en) 2013-04-08 2018-04-24 Danfoss Power Solutions Inc. Selectable flow hydraulic gear pump
DE102013226744A1 (de) 2013-12-19 2015-06-25 Gesellschaft zur Förderung von Medizin-, Bio- und Umwelttechnologien e.V. Verfahren zum Regeln einer Ölpumpe mittels eines der Ölpumpe vorgeschalteten Frequenzumrichters sowie Regelsystem

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2526830A (en) * 1945-06-22 1950-10-24 Hpm Dev Corp Variable delivery gear pump
US3427980A (en) * 1965-03-22 1969-02-18 Rolls Royce Gear pump
US3446118A (en) * 1966-10-28 1969-05-27 Tozaburo Kuhara Variable torque hydraulic gear motor
US3588295A (en) * 1969-08-29 1971-06-28 Lowell E Burk Variable output gear pump or motor apparatus
GB1435451A (en) * 1974-05-15 1976-05-12 Tompkins L L Positive displacement fluid motors
ES445021A1 (es) * 1976-02-10 1977-06-01 Bendiberica Sa Perfeccionamientos en bombas de engranaje.
DE3528651A1 (de) * 1985-08-09 1987-02-19 Rohs Hans Guenther Prof Dr Ing Zahnradpumpe
US5724812A (en) * 1996-02-16 1998-03-10 Baker; William E. Variable displacement apparatus and method of using same
DE19846815B4 (de) * 1997-10-16 2014-08-07 Ixetic Bad Homburg Gmbh Ventilanordnung und Pumpe für ein Getriebe
DE19847132C2 (de) * 1998-10-13 2001-05-31 Schwaebische Huettenwerke Gmbh Außenzahnradpumpe mit Fördervolumenbegrenzung
US20010024618A1 (en) * 1999-12-01 2001-09-27 Winmill Len F. Adjustable-displacement gear pump
ATE326633T1 (de) 2002-01-12 2006-06-15 Dieter Dipl-Ing Voigt Vorrichtung zur druckregelung von hydraulikpumpen
DE10237911A1 (de) 2002-08-14 2004-02-26 Basf Ag Verwendung von Vinylamineinheiten enthaltenden Polymeren als Promoter für die Alkyldiketenleimung
AT413140B (de) * 2003-03-28 2005-11-15 Tcg Unitech Ag Zahnradpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005057013A1 *

Also Published As

Publication number Publication date
US20070111855A1 (en) 2007-05-17
JP2007514097A (ja) 2007-05-31
WO2005057013A1 (fr) 2005-06-23

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