EP1852610A1 - Dispositif de levage variable pour double engrenage excentré - Google Patents

Dispositif de levage variable pour double engrenage excentré Download PDF

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Publication number
EP1852610A1
EP1852610A1 EP07107133A EP07107133A EP1852610A1 EP 1852610 A1 EP1852610 A1 EP 1852610A1 EP 07107133 A EP07107133 A EP 07107133A EP 07107133 A EP07107133 A EP 07107133A EP 1852610 A1 EP1852610 A1 EP 1852610A1
Authority
EP
European Patent Office
Prior art keywords
hubverstelleinrichtung
eccentric
chambers
hydraulic
housing
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Withdrawn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
EP07107133A
Other languages
German (de)
English (en)
Inventor
Hermann Golle
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.)
Golle Motor AG
Original Assignee
Golle Motor AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Golle Motor AG filed Critical Golle Motor AG
Publication of EP1852610A1 publication Critical patent/EP1852610A1/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Withdrawn legal-status Critical Current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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • F04B49/126—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts with a double eccenter mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft

Definitions

  • the invention relates to a device for continuous adjustment of the working stroke in driven by radial eccentric or Axiaexzenter pumps of any kind, especially in common rail pumps for diesel and gasoline injection systems.
  • Hubverstellende facilities are known in manifold versions.
  • lever systems which are switched on between a cam and the piston to be driven, especially double eccentrics are used for stroke adjustment.
  • a second outer eccentric is mounted on an inner, connected to the drive shaft eccentric and from the angular position of the two eccentric to each other results in a certain stroke size.
  • publication DD 31201 works with hydraulic piston valve and handwheel analogous to the above-mentioned publications.
  • the DE 32 22 577 uses the reaction forces occurring between the eccentrics for "arbitrary adjustment” and uses it for freewheels, piston valves and other components.
  • the invention has for its object to arrange at Hubverstellenden radial and Axialnockenantrieben with in- or juxtaposed eccentrics simple, self-acting control and regulating devices and thus to create cost-effective cam drives with continuous stroke adjustment.
  • a drive shaft 2 mounted in the housing 1 is provided with an inner eccentric 3 and a control eccentric 4, whose midpoint ME is offset by the amount e from the midpoint M of the drive shaft 2.
  • an outer eccentric 5 is mounted, whose housing part 6 fixedly connected to it has an inner contour 7.
  • This inner contour 7 forms, together with the control eccentric 4, an annular space 8 concentric with ME, which contains the adjustment system.
  • a lid 9 closes off the annular space 8, whereby at the same time the axial guidance of the outer eccentric 5 is made.
  • a torsion spring 10 is fixedly connected on the one hand to the drive shaft 2, on the other hand to the housing part 6 / lid 9 and constitutes a main element of the control and regulating system described in FIG.
  • roller tappet 11 In operative connection with the eccentrics 3 and 5 is a roller tappet 11 which is guided in the housing 1 and the actual work system (piston, lever member o. ⁇ .) Drives.
  • the actual work system lever member o. ⁇ .
  • several pistons can be arranged concentrically with the drive shaft 2.
  • Fig. 1 also shows a supply for a control medium in the control and regulation system.
  • a supply bore 13 is connected via a ring channel 14 located in the drive shaft 2 continuously with distributor bores 15 (FIG. 5).
  • distributor bores 15 also connected to the drive shaft 2 rotating piece with improved hydraulic seal the connection from the housing 1 to the drive shaft 2 produce.
  • the feed can also be controlled in such a way that, dispensing with the annular groove 14, a rotary slide-like feed takes place between 13 and 15.
  • the radial, with 13 corresponding distributor hole 15 is the eccentrics 3; 5 assigned so that only in the u. T. position (bottom dead center, zero crossing) the connection between 13 and 15 is made. This reduces the adjustment forces. Outside the range of u. T. position, the system is hydraulically locked. At the same time, vibration phenomena imposed on the system by the drive or by flow and pressure fluctuations are suppressed.
  • Fig. 2 shows the associated position of the eccentric 3 and 5 such that a zero stroke is set.
  • the center ME is similar to FIG. 1 by the amount e above the midpoint M of the drive shaft second
  • FIG. 3 shows, compared to FIG. 2, the 180 ° adjustment of the outer eccentric 5.
  • the center ME is displaced by 2e with respect to M, and the maximum stroke is set with the 180 ° stroke.
  • This stroke is usually not used in the technical design, but apply a partial twist.
  • Fig. 5 shows the adjustment system in the initially known training with swing wings.
  • the control eccentric 4 and thus the inner eccentric 3 and the drive shaft 2 - Fig. 1 are firmly connected to the swing vanes 16, with the housing part 6 (and thus the outer eccentric 5 - Fig. 1), the swing vanes 16 a.
  • the housing part 6 and thus the outer eccentric 5 - Fig. 1
  • the swing vanes 16 a In the position shown is now 6, 16a clockwise so compared to 4; 16 preceded that the maximum required stroke is set.
  • this position is achieved in that the torsion spring 10 (FIG. 1) and the auxiliary springs 17 effect this rotation until they abut against the stop pin 18.
  • the aggregate, z. As a pump moves in this way with maximum stroke and thus the largest flow (main stream).
  • a control loop is thus integrated in the simplest way in the device.
  • z. B constant input speed of the pump and constant control valve position, a pressure level is maintained in a consumer. If the consumer takes a smaller main current, the control current is increased, the control pressure in the pressure chamber 19 increases. As a result, the parts 5; 6 against the action of the springs 10; 17 shifted towards zero promotion. With increased main current in the consumer, the opposite conditions occur.
  • the accumulating in the spring chambers 20 leakage medium can flow through the auxiliary holes 21 in the housing 1. If, as is often the case, the housing 1 is internally under a certain lower admission, this form is also in the spring chambers 20 and supports the action of the springs 10; 17. With the size of the pump pre-pressure can thus be exercised in a certain way influence on the control behavior.
  • Fig. 6 shows in addition to Figure 5, the adjustment system designed such that in support of the springs 10; 17, a hydraulic control pressure is also fed to the rear spring chambers 20.
  • additional distributor bores 15a (FIG. 6) are arranged in the drive shaft 2 and the control eccentric 4.
  • the auxiliary bores 21 are eliminated.
  • a spool 22 located immediately adjacent the drive shaft 2, controls the inflow and outflow of the control medium into the chambers 19 and 20 ( Figure 6) via the manifold bores 15 and 15a.
  • This spool 22 can be operated in different ways.
  • the spool 22 is moved, for example via an angle lever 23 and a mechatronic actuator 24 (magnet, piezoelectric actuator) in the left end position, by a compression spring 25 in the right end position.
  • a mechatronic actuator 24 magnet, piezoelectric actuator
  • the spool 22 can be moved by a hydraulic pressure introduced into the chamber 26, but also the introduction of hydraulic pressure on both sides of the spool 22, optionally connected to one or both sides acting compression springs 25 and corresponding stops are possible embodiments.
  • the system is hydraulically locked.
  • the middle annular groove 27 coincides with 15, the chambers 19 (FIG. 6) are acted upon, while the chambers 20 are relieved via 15a and the right outer annular groove 27a - the stroke of the device is reduced.
  • the outflowing medium flows via the outflow channels 28 to the interior of the housing 1.
  • FIG. 8 shows an exemplary embodiment with four chambers 19; 20, wherein two channels open into each chamber, here called inlet bore 29 and 30 drain hole.
  • FIG. 9 shows the embodiment of FIG. 8 integrated in the device adjustment system.
  • a piston valve 22 control should be replaced for example by two separately controllable mechatronic actuators (magnet, piezoelectric actuator) 24; 24a.
  • the control pressure is via the supply hole 13 and located in the drive shaft 2 distribution hole 15 all four chambers 19; 20 (Fig. 8) without circuit of a piston valve or other valve constantly supplied, but also controlled in a rotary slide.
  • a throttle 31 a certain throttle effect in the influx to the chambers 19; 20 effect.
  • the system is thus hydraulically locked. Since the same pressure prevails in all chambers, leakage flows between the chambers do not occur.
  • FIG. 10 shows a mechanical / mechatronic adjustment system.
  • the drive shaft 2 and thus the inner eccentric 3 (FIG. 1) continue to a threaded spindle 33, while the outer eccentric 5 (FIG. 1) has a threaded spindle 33a corresponding to the housing part 6.
  • Both threaded spindles 33; 33a face each other coaxially and carry multi-start threads with large pitch, which are between 33; 33a is opposite (right or left).
  • a sliding sleeve 34 each with corresponding internal threads engages in both threaded spindles 33; 33a and provides the positive connection between the parts 2; 6 and thus the eccentrics 3; 5 ago.
  • a compression spring 25 may serve to return the sliding sleeve 34. Due to the opposing thread pitches to 33; 33a, the longitudinal forces resulting from the torque transmission cancel each other in the sliding sleeve 34, so that the adjusting forces are reduced.
  • FIGS. 11 and 12 show the application of the device according to the invention in axial piston machines.
  • FIG. 11 shows an axial eccentric 35 fixedly connected to the drive shaft 2 and via the adjusting and control system the second axial eccentric 35a is connected to the axial eccentric 35.
  • both eccentric 35; 35a set against each other so that a zero stroke is set for the guided in the housing 1 displacement piston 36.
  • FIG. 12 shows, compared to FIG. 11, the 180 ° configuration of both eccentrics 35; 35a to each other, it is set the maximum stroke.
  • a partial adjustment including all means 8 according to the invention; 15; 15a; 16; 16a; 19; 20 can be used, as have been described for Fig. 1 to Fig. 9.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Retarders (AREA)
EP07107133A 2006-05-05 2007-04-27 Dispositif de levage variable pour double engrenage excentré Withdrawn EP1852610A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006021723A DE102006021723A1 (de) 2006-05-05 2006-05-05 Hubverstelleinrichtung für Doppelexzenterantriebe

Publications (1)

Publication Number Publication Date
EP1852610A1 true EP1852610A1 (fr) 2007-11-07

Family

ID=38153413

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07107133A Withdrawn EP1852610A1 (fr) 2006-05-05 2007-04-27 Dispositif de levage variable pour double engrenage excentré

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EP (1) EP1852610A1 (fr)
DE (2) DE102006021723A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202013011687U1 (de) * 2013-11-13 2015-02-23 C. & E. Fein Gmbh Oszillierend antreibbare Werkzeugmaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH226285A (de) * 1955-11-23 1943-03-31 Scintilla Ag Variable Kurbel mit hydraulischer Steuerungseinrichtung.
DE3222577A1 (de) * 1982-06-16 1983-12-22 Eichler, Wolfgang, 7500 Karlsruhe Doppelexzenter-antrieb fuer oszillierende verdraengerpumpen
WO1992000455A1 (fr) * 1990-06-29 1992-01-09 Whitemoss, Inc. Machine fluidique a pistons radiaux et/ou rotor reglable
FR2786228A1 (fr) * 1998-11-23 2000-05-26 Milton Roy Dosapro Dispositif d'entrainement a course reglable d'une bielle de pompe doseuse
EP1111234A2 (fr) * 1999-12-20 2001-06-27 Hydraulik-Ring GmbH Pompe à carburant

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH226285A (de) * 1955-11-23 1943-03-31 Scintilla Ag Variable Kurbel mit hydraulischer Steuerungseinrichtung.
DE3222577A1 (de) * 1982-06-16 1983-12-22 Eichler, Wolfgang, 7500 Karlsruhe Doppelexzenter-antrieb fuer oszillierende verdraengerpumpen
WO1992000455A1 (fr) * 1990-06-29 1992-01-09 Whitemoss, Inc. Machine fluidique a pistons radiaux et/ou rotor reglable
FR2786228A1 (fr) * 1998-11-23 2000-05-26 Milton Roy Dosapro Dispositif d'entrainement a course reglable d'une bielle de pompe doseuse
EP1111234A2 (fr) * 1999-12-20 2001-06-27 Hydraulik-Ring GmbH Pompe à carburant

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Publication number Publication date
DE102006021723A1 (de) 2007-11-08
DE102007038279A1 (de) 2009-02-12

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