EP1942277A2 - Réglage de la pression dynamique pour pompes hydrauliques - Google Patents

Réglage de la pression dynamique pour pompes hydrauliques Download PDF

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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.)
Withdrawn
Application number
EP20070122222
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German (de)
English (en)
Inventor
Dieter Dipl.-Ing. Voigt
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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
Application filed by Individual filed Critical Individual
Publication of EP1942277A2 publication Critical patent/EP1942277A2/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • 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
    • 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)
EP20070122222 2007-01-03 2007-12-04 Réglage de la pression dynamique pour pompes hydrauliques Withdrawn EP1942277A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710001066 DE102007001066A1 (de) 2007-01-03 2007-01-03 Staudruck-Regelung für Hydraulikpumpen

Publications (1)

Publication Number Publication Date
EP1942277A2 true EP1942277A2 (fr) 2008-07-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070122222 Withdrawn EP1942277A2 (fr) 2007-01-03 2007-12-04 Réglage de la pression dynamique pour pompes hydrauliques

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EP (1) EP1942277A2 (fr)
DE (1) DE102007001066A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013001750A1 (de) 2013-01-31 2014-07-31 Volkswagen Aktiengesellschaft Verfahren zur Regelung eines Öldrucks für einen Verbrennungsmotor sowie entsprechend ausgestaltete Ölpumpe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007039589A1 (de) 2007-08-22 2009-02-26 Voigt, Dieter, Dipl.-Ing. Regelölpumpe mit verstellwegabhängiger Öldruckregelung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10237801B4 (de) 2002-01-12 2004-05-27 Voigt, Dieter, Dipl.-Ing. Vorrichtung zur Druckregelung von Hydraulikpumpen
DE102004007323A1 (de) 2004-02-14 2005-08-04 Voigt, Dieter, Dipl.-Ing. Druckregelung für Ölpumpen
DE102007008177A1 (de) 2006-08-29 2007-07-26 Voigt, Dieter, Dipl.-Ing. Bypass-Druckbegrenzung für Außenzahnrad-Regelölpumpen
DE102006051575A1 (de) 2006-11-02 2007-09-13 Voigt, Dieter, Dipl.-Ing. Druckregelung für Außenzahnrad-Regelölpumpen

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10237801B4 (de) 2002-01-12 2004-05-27 Voigt, Dieter, Dipl.-Ing. Vorrichtung zur Druckregelung von Hydraulikpumpen
DE102004007323A1 (de) 2004-02-14 2005-08-04 Voigt, Dieter, Dipl.-Ing. Druckregelung für Ölpumpen
DE102007008177A1 (de) 2006-08-29 2007-07-26 Voigt, Dieter, Dipl.-Ing. Bypass-Druckbegrenzung für Außenzahnrad-Regelölpumpen
DE102006051575A1 (de) 2006-11-02 2007-09-13 Voigt, Dieter, Dipl.-Ing. Druckregelung für Außenzahnrad-Regelölpumpen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013001750A1 (de) 2013-01-31 2014-07-31 Volkswagen Aktiengesellschaft Verfahren zur Regelung eines Öldrucks für einen Verbrennungsmotor sowie entsprechend ausgestaltete Ölpumpe

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Publication number Publication date
DE102007001066A1 (de) 2007-08-02

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