EP1873363B1 - Pumpe mit variabler Förderleistung und Steuerung dafür - Google Patents

Pumpe mit variabler Förderleistung und Steuerung dafür Download PDF

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Publication number
EP1873363B1
EP1873363B1 EP07075612A EP07075612A EP1873363B1 EP 1873363 B1 EP1873363 B1 EP 1873363B1 EP 07075612 A EP07075612 A EP 07075612A EP 07075612 A EP07075612 A EP 07075612A EP 1873363 B1 EP1873363 B1 EP 1873363B1
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EP
European Patent Office
Prior art keywords
stroke
pump
pressure
engine
solenoid
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.)
Expired - Lifetime
Application number
EP07075612A
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English (en)
French (fr)
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EP1873363A2 (de
EP1873363A3 (de
Inventor
Douglas Hunter
Dennis Koenig
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.)
SLW Automotive Inc
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SLW Automotive Inc
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Filing date
Publication date
Application filed by SLW Automotive Inc filed Critical SLW Automotive Inc
Priority claimed from US10/406,575 external-priority patent/US7018178B2/en
Publication of EP1873363A2 publication Critical patent/EP1873363A2/de
Publication of EP1873363A3 publication Critical patent/EP1873363A3/de
Application granted granted Critical
Publication of EP1873363B1 publication Critical patent/EP1873363B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • 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
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • F04C2270/01—Load
    • 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
    • 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

Definitions

  • the present invention relates to the control of the output of a variable displacement pump. More specifically, the present invention relates to control of an oil pump for oil pressure control in an internal combustion engine.
  • EP-A-0945619 there is described a control system for controlling hydraulic pumps in hydraulic construction machines, such as excavators in which a diesel engine serves as prime mover and drives the hydraulic pumps to deliver hydraulic fluid to hydraulic actuators.
  • the pumps are swash plate pumps and are equipped with regulators for controlling the tilting positions of the swash plates, the regulators comprising tilting actuators and servo valves.
  • Solenoid control valves control the pressure for controlling the tilting positions of the pumps.
  • a control system for controlling a variable displacement pump for controlling oil flow and oil pressure in a circuit in an engine comprising: a pump; a de-stroke actuating member capable of acting against an on-stroke actuating member for controlling the displacement of the pump; an engine fluid pressure circuit for receiving oil flow and oil pressure from the pump; a solenoid being operably associated with the de-stroke actuating member for selectively controlling the displacement of the pump, wherein forces act on said on-stroke actuating member and said de-stroke actuating member acts against both said on-stroke actuating member and said forces; an electronic control unit connected to and providing an input control signal to the solenoid for controlling oil flow and oil pressure; and wherein the de-stroke actuating member is hydraulically actuated and the solenoid is used to control oil flow and oil pressure from the pump.
  • the present invention also provides a variable displacement pump for an engine having an engine control unit comprising: a pump having a de-stroke actuator that acts against an on-stroke actuator and controls the pressure and flow of oil to a pressure lubricating circuit of the engine; a pilot pressure line that has oil flow and oil pressure supplied by the engine; a flow control valve for hydraulically varying the pump displacement by facilitating movement of said de-stroke actuator, wherein forces act on said on-stroke actuator and said de-stroke actuator acts against both said on-stroke actuator and said forces; a solenoid controlled by said engine control unit, said solenoid being operably associated with said flow control valve for providing control of oil flow through said flow control valve.
  • Figure 1 is a hydraulic schematic showing a first embodiment of the present invention
  • Figure 2 is a hydraulic schematic showing a second embodiment of the present invention
  • Figure 2a is a variation of the second embodiment of the present invention.
  • Figure 3 is a hydraulic schematic showing a third embodiment of the present invention.
  • Figure 4 is a hydraulic schematic showing a forth embodiment of the present invention.
  • Figure 5 is a hydraulic schematic showing a fifth embodiment of the present invention.
  • Figure 6 is a hydraulic schematic showing a sixth embodiment of the present invention.
  • Figure 7 is a hydraulic schematic showing a seventh embodiment of the present invention.
  • Figure 8 is a hydraulic schematic showing an eighth embodiment of the present invention.
  • a method of controlling a variable displacement pump 10 for an engine is provided.
  • the solenoid 26 is normally, or is defaulted to, the closed position when no power is supplied to the solenoid 26.
  • the solenoid 26 When the solenoid 26 is in the closed position there will be high fluid displacement by the pump 10.
  • an emergency event such as when there is an electrical failure, the solenoid 26 will move to its default position so the engine oil pressure will remain high and that the vehicle can continue operating until it can serviced.
  • the solenoid in a closed position the system could also be configured so that there is fluid displacement with the pump 10.
  • the pump is a vane-type variable displacement pump, as set forth in co-pending application Serial No. 10/021,566, filed December 12, 2000 (Publication No US 2002/0114708 ), the specification of which is incorporated by reference herein.
  • the pump is designed for an engine lubrication circuit.
  • the pump is generally shown at 10.
  • the pump 10 may be a vane pump which has the displacement varied by movement of an eccentric ring 11. It is also possible to incorporate other types of pumps, in which the stroke or displacement may be adjusted during operation.
  • a flow control valve 12 is used to mechanically vary the displacement of a pump 10, by moving the eccentric ring 11, based on an engine pilot pressure 14 acting on the flow control valve 12 which controls the volume of oil in each control chamber on each side of the eccentric ring 11.
  • a compression spring 16 acts against a pilot pressure 14 for maintaining some pressure on the flow control valve 12 and to provide a return pressure in absence of the pilot pressure 14.
  • the flow control valve 12 in this particular embodiment is a spool valve such as a three-way spool valve.
  • the flow control valve 12 can be a spool valve of any type of configuration.
  • the flow control valve 12 does not necessarily need to be a spool valve at all, as will be seen in Figure 6 .
  • the compression spring 16 gives the spool portion of the valve 12 travel distance that is proportional to the differential between the actual pressure of the system and the desired or target system pressure.
  • the differential pressure is variable by way of a valve 18, which controls the amount of pressure acting on the variable target piston 20 against spring 22 for varying the amount of spring 16 pressure on valve 12.
  • An engine control unit (ECU) 24 monitors the engine conditions and parameters such as temperature, speed and engine load. In this embodiment, the engine control unit 24 monitors the engine conditions pressure, speed, and engine load and then selects a desired oil pressure, and sends the appropriate current to the solenoid 26 acting on valve 18. This varies the pressure acting on the piston 20, changing its position and thereby reducing or increasing target pressure, depending upon the desired engine oil pressure target.
  • the flow control valve 12 then regulates the pump's 10 eccentric ring 11 to maintain target pressure.
  • FIG. 2 With respect to Figure 2 , like items referenced in Figure 1 are similarly designated with reference numerals differing by 100.
  • the operation of this embodiment is similar to the embodiment shown in Figure 1 .
  • the valve 112a includes a closed center valve portion 112b.
  • the main operating difference is the use of a pressure reducing and regulating valve 128.
  • the regulating valve 128 creates a fixed input pressure for the solenoid valve 118 in that the pressure, which in Figure 1 was taken from the discharge port of the pump 10 into the solenoid control valve 18, is now at a constant pressure and, therefore, provides better control of the variable target pressure acting on piston 120. This ultimately provides improved control over the desired movement of the eccentric ring 111 of the pump 110.
  • Fig. 2a operates in a similar manner as Fig. 2 .
  • the main difference between Fig. 2 and Fig. 2a is that the pressure reducing and regulating valve 128 of Fig. 2a creates a fixed target pressure that acts directly on the piston 120.
  • the solenoid 126 opens or closes to further adjust the pressure of fluid acting on the piston 120.
  • the solenoid 126 moves the valve 118a to the closed position there is an increase in variable target pressure.
  • the solenoid 126 moves the valve 118a to the open position the variable target pressure will decrease as the fluid moves to the sump with less resistance.
  • unreduced pressure is fed to the spool valve 112A before the pressure reducing and regulating valve 128 after the filter.
  • this embodiment is also a passive system for controlling oil flow and oil pressure since an engine control unit 124 controls the solenoid 126 for positioning the piston 120, however, the engine control unit 124 does not directly sense oil pressure.
  • this embodiment includes a solenoid 426 attached to the flow control spool valve 412 directly, to regulate the stroke or de-stroke conditions of the pump 410.
  • the solenoid 426 is connected directly to the engine control unit 424.
  • the engine control unit 424 samples the pilot pressure from a pressure transducer in the engine circuit in order to make the proper calculations as to the best spool position based on the current actual and target pressures.
  • Return spring 416 provides the return pressure for adjusting the flow control spool valve 412 in absence of solenoid 426 input, and allows for predetermined functions of spool position versus current.
  • FIG. 6 like items referenced in Figure 5 are similarly designated with reference numerals differing by 100.
  • a very simple control mechanism is used by the control solenoid 526 moving a valve 512A for controlling the de-stroke actuator of the pump 510.
  • the solenoid 526 adjusts the pressure acting on the large piston which pushes against the discharge pressure acting on the small piston on the opposite side.
  • An on-stroke return spring is provided for balancing the eccentric control ring against control inputs which can also work alone (as shown).
  • the engine control unit 524 samples the pilot pressure from a pressure transducer in the engine circuit in order to make the proper calculations as to the best valve 512A position.
  • Figure 7 is another embodiment wherein engine control unit 624 directly controls a solenoid 626 which acts directly on either the actuating piston for the eccentric ring or directly on the eccentric ring. This allows direct control of the displacement of the pump 610 based on ECU 624 monitoring of the pilot pressure of the oil pressure circuit, although this arrangement is not in accordance with the invention as defined in the claims which follows..
  • Figure 8 illustrates a further embodiment wherein the solenoid 726 directly actuates the spool flow control valve 712.
  • the ECU 724 is monitoring the engine oil circuit pressure and adjusting the solenoid in accordance with the necessary engine oil pressure, as calculated by the ECU.
  • pressure from the discharge is reduced by the solenoid valve and used to bias the position of the flow control spool valve 712 against the spring for varying the displacement of the pump.
  • Flow across the solenoid can be directed to the inlet port, as shown of the vane pump 710, but can also be drained to the sump.
  • Figures 1 through 4 are passive systems which allow the ECU to monitor engine conditions and provide a pressure target to the pump system, but the pump system is self-regulated to the pressure target by mechanical and hydraulic controls.
  • Figures 5 through 8 provide active control of the oil pressure by the ECU. In these embodiments, the ECU monitors the oil pressure and actively adjusts the system on a real time basis to control oil pressure in the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Claims (15)

  1. Steuerungssystem zur Steuerung einer Pumpe mit variabler Förderleistung zur Steuerung von Ölfluss und Öldruck in einem Kreislauf in einem Motor, umfassend:
    eine Pumpe (10);
    ein Destroke-Betätigungsglied, das imstande ist, gegen ein Onstroke-Betätigungsglied zu wirken, zur Steuerung der Förderleistung der Pumpe (10);
    einen Motorflüssigkeits-Druckkreislauf zum Empfangen von Ölfluss und Öldruck von der Pumpe (10);
    einen Schaltmagnet (26), der operativ mit dem Destroke-Betätigungsglied assoziiert ist, zur selektiven Steuerung der Förderleistung der Pumpe, wobei Kräfte auf das Onstroke-Betätigungsglied wirken und das Destroke-Betätigungsglied gegen sowohl des Onstroke-Betätigungsglied als auch die Kräfte wirkt;
    eine elektronische Steuereinheit (24), die mit dem Schaltmagnet (26) verbunden ist und dafür ein Eingangssteuerungssignal bereitstellt, zur Steuerung von Ölfluss und Öldruck; und
    wobei das Destroke-Betätigungsglied hydraulisch betätigt wird und der Schaltmagnet (26) zur Steuerung von Ölfluss und Öldruck von der Pumpe verwendet wird.
  2. Steuerungssystem nach Anspruch 1, wobei die elektronische Steuereinheit (24) mit einer Vorsteuerleitung (14), die mit dem Motorflüssigkeits-Druckkreislauf verbunden ist, verbunden ist und den Druck darin überwacht, wobei die elektronische Steuereinheit (24) Eingangssignale für den Schaltmagnet (26) als Reaktion auf Druckbedingungen in der Vorsteuerleitung (14) zur Steuerung der Förderleistung der Pumpe (10) erzeugt.
  3. Steuerungssystem nach Anspruch 1 oder 2, wobei die elektronische Steuereinheit (24) den Öldruck überwacht und das System zur Steuerung des Öldrucks in dem Motoröl-Druckkreislauf auf einer Echtzeitbasis aktiv anpasst.
  4. Steuerungssystem nach Anspruch 1, 2 oder 3, wobei ein Ventilglied (12) funktional zwischen dem Schaltmagnet (26) und dem Destroke-Betätigungsglied verbunden ist und einen Betrag von Hydraulikdruck steuert, der als Reaktion auf die Bewegung des Schaltmagnets (26) in das Destroke-Betätigungsglied eingegeben wird.
  5. Steuerungssystem nach Anspruch 4, wobei der Schaltmagnet (426; 526) direkt mit dem Ventilglied (412; 512A) verbunden ist und das Öffnen und Schließen des Ventilglieds steuert.
  6. Steuerungssystem nach Anspruch 5, wobei das Ventilglied (512A) mit einem Sumpf verbunden ist, so dass, wenn der Schaltmagnet (526) das Ventilglied öffnet, ein Eingangsdruck zu dem Betätigungsglied zunimmt.
  7. Steuerungssystem nach Anspruch 5 oder 6, wobei der Eingangsdruck zu dem Destroke-Betätigungsglied abnimmt, wenn der Schaltmagnet (526) das Ventilglied schließt.
  8. Steuerungssystem nach einem der vorstehenden Ansprüche, weiter Überwachen von Motorbedingungen umfassend, die aus der Gruppe ausgewählt werden, die Motortemperatur, Motordrehzahl, Motorlast und Kombinationen davon umfasst.
  9. Steuerungssystem nach einem der Ansprüche 1 bis 8, weiter einen Kolbenbildungsteil des Destroke-Betätigungsglieds und einen Kolben an einer Onstroke-Seite der Pumpe umfassend, wobei der Kolben an der Destroke-Seite größer als der Kolben an der Onstroke-Seite der Pumpe ist.
  10. Steuerungssystem nach einem der Ansprüche 1 bis 9, wobei die Kräfte Austrittsdrücke umfassen.
  11. Steuerungssystem nach einem der Ansprüche 1 bis 10, wobei die Kräfte Federkräfte umfassen, die von einem Federglied verursacht werden, das operativ mit dem Onstroke-Betätigungsglied verbunden ist.
  12. Pumpe mit variabler Förderleistung für einen Motor mit einer Motorsteuerungseinheit, umfassend:
    eine Pumpe (10) mit einem Destroke-Betätigungsglied, das gegen ein Onstroke-Betätigungsglied wirkt und den Druck und Fluss von Öl zu einem Druckschmierkreis des Motors steuert;
    ein Vorsteuerleitung (14), die den Ölfluss und Öldruck, die von dem Motor zugeführt werden, aufweist;
    ein Flusssteuerventil (12) zum hydraulischen Verändern der Pumpenförderleistung durch Erleichterung der Bewegung des Destroke-Betätigungsglieds, wobei Kräfte auf das Onstroke-Betätigungsglied wirken und das Destroke-Betätigungsglied sowohl gegen das Onstroke-Betätigungsglied als auch die Kräfte wirkt;
    einen Schaltmagnet (26), der von der Motorsteuerungseinheit (24) gesteuert wird, wobei der Schaltmagnet operativ mit dem Flusssteuerventil (12) assoziiert ist, um Steuerung des Ölflusses durch das Flusssteuerventil bereitzustellen.
  13. Pumpe mit variabler Förderleistung nach Anspruch 12, weiter einen Kolbenbildungsteil des Destroke-Betätigungsglieds und einen Kolben an einer Onstroke-Seite der Pumpe umfassend, wobei der Kolben an der Destroke-Seite größer als der Kolben an der Onstroke-Seite der Pumpe ist.
  14. Pumpe mit variabler Förderleistung nach Anspruch 12 oder 13, wobei die Kräfte Austrittsdrücke umfassen.
  15. Pumpe mit variabler Förderleistung nach Anspruch 12, 13 oder 14, wobei die Kräfte Federkräfte umfassen, die von einem Federglied verursacht werden, das operativ mit dem Onstroke-Betätigungsglied verbunden ist.
EP07075612A 2002-04-03 2003-04-03 Pumpe mit variabler Förderleistung und Steuerung dafür Expired - Lifetime EP1873363B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US36982902P 2002-04-03 2002-04-03
US10/406,575 US7018178B2 (en) 2002-04-03 2003-04-03 Variable displacement pump and control therefore for supplying lubricant to an engine
EP03252133.8A EP1350930B2 (de) 2002-04-03 2003-04-03 Regelbare Verdrängerpump sowie Steursystem dafür

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP03252133.8A Division EP1350930B2 (de) 2002-04-03 2003-04-03 Regelbare Verdrängerpump sowie Steursystem dafür
EP03252133.8A Division-Into EP1350930B2 (de) 2002-04-03 2003-04-03 Regelbare Verdrängerpump sowie Steursystem dafür
EP03252133.8 Division 2003-04-03

Publications (3)

Publication Number Publication Date
EP1873363A2 EP1873363A2 (de) 2008-01-02
EP1873363A3 EP1873363A3 (de) 2008-04-23
EP1873363B1 true EP1873363B1 (de) 2010-07-21

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EP07075612A Expired - Lifetime EP1873363B1 (de) 2002-04-03 2003-04-03 Pumpe mit variabler Förderleistung und Steuerung dafür

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012009951A1 (de) 2012-05-18 2013-11-21 Thomas Magnete Gmbh Schaltventil mit einer Ventilhülse aus Kunststoff
CN104047665B (zh) * 2014-06-06 2016-08-24 湖南机油泵股份有限公司 一种电磁阀控单作用腔反馈可变排量叶片泵的控制系统
DE102014012306A1 (de) 2014-08-19 2016-02-25 Thomas Magnete Gmbh Steuerventil mit Bauteilen aus Kunststoff

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5545014A (en) * 1993-08-30 1996-08-13 Coltec Industries Inc. Variable displacement vane pump, component parts and method
US5876185A (en) * 1996-11-20 1999-03-02 Caterpillar Inc. Load sensing pump control for a variable displacement pump
JP3383754B2 (ja) 1997-09-29 2003-03-04 日立建機株式会社 油圧建設機械の油圧ポンプのトルク制御装置
US6202016B1 (en) * 1999-08-10 2001-03-13 Eaton Corporation Shift on the go transmission system

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Publication number Publication date
EP1873363A2 (de) 2008-01-02
EP1873363A3 (de) 2008-04-23

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