EP2138720A2 - Dispositif de réglage pour le réglage de machines à pistons axiaux. - Google Patents

Dispositif de réglage pour le réglage de machines à pistons axiaux. Download PDF

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Publication number
EP2138720A2
EP2138720A2 EP09007975A EP09007975A EP2138720A2 EP 2138720 A2 EP2138720 A2 EP 2138720A2 EP 09007975 A EP09007975 A EP 09007975A EP 09007975 A EP09007975 A EP 09007975A EP 2138720 A2 EP2138720 A2 EP 2138720A2
Authority
EP
European Patent Office
Prior art keywords
control
adjusting
adjusting device
actuating
piston
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Withdrawn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
EP09007975A
Other languages
German (de)
English (en)
Other versions
EP2138720A3 (fr
Inventor
Manfred Kirchhoff
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.)
Mali Holding AG
Original Assignee
Mali Holding 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 Mali Holding AG filed Critical Mali Holding AG
Publication of EP2138720A2 publication Critical patent/EP2138720A2/fr
Publication of EP2138720A3 publication Critical patent/EP2138720A3/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Withdrawn legal-status Critical Current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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F04B49/10—Other safety measures

Definitions

  • the present invention generally relates to the hydraulic adjustment of mechanical systems, wherein the adjustment range of the respective system extends in opposite directions to either side of a zero crossing.
  • the adjustment range can be a swivel range but also a linear range.
  • the invention relates to an adjusting device according to the preamble of claim 1.
  • the pumping or driving action depends on the pivoting angle of the respective pivotable element. At zero swing angle, the pumping or driving action of the machine is zero, while it increases with swinging out of zero position with increasing swing angle.
  • hydraulically actuated actuators are often used, e.g. be controlled by solenoid operated multi-way valves.
  • an adjustable axial piston machine in swash plate construction in which the swash plate surface is formed on a pivotable about a pivot axis, substantially semi-cylindrical cradle body, with its semi-cylindrical outer surface in a corresponding hollow cylindrical Support surface is mounted in the machine housing of the axial piston machine, and provided for pivoting the cradle body actuating means which are in operative connection with a lever which is connected to the cradle body and whose longitudinal central axis intersects the pivot axis.
  • the adjusting devices are designed as double-acting actuating cylinder adjusting piston units, each with two arranged in the opposite effective direction control piston surfaces.
  • the actuating cylinder actuating piston unit comprises a transverse split actuating piston consisting of two adjusting piston parts.
  • the two Stellkolbenmaschine be braced by spring assemblies against each other, have the same dimensions and produce the same size, oppositely directed spring forces.
  • neutral position Nullhub too of the machine
  • the weighing body is held by the spring assemblies on the Stellkolbenmaschine in its center position. Since only the spring assemblies are responsible for the zero position, they must be sufficiently strong in relation to the spring force, which must be overcome in normal operation at a deflection from the zero position significant counter forces.
  • a hydrostatic displacement unit in the form of a swashplate axial piston machine with an actuatable by an actuator adjusting device for adjusting the displacement volume is known, wherein the actuating device is in operative connection with a restoring force generating neutral position centering.
  • the zero position centering has a first functional position in which the actuating device can be acted upon by the restoring force and has a second functional position in which the actuating device can be relieved of the restoring force.
  • two return pistons of the neutral position centering are longitudinally displaceably mounted in a housing bore of the housing of the displacer unit, which operatively connected to opposite contact surfaces of a driver element of the pivotally mounted swash plate can be brought.
  • the return piston can be acted upon by means of a respective spring, which is arranged in a control pressure chamber, in the direction of the driver element.
  • Each of the return pistons has a control pressure surface counteracting the spring, wherein the control pressure chamber arranged in front of the control pressure surface is connected to a control pressure line in which, for example, a control pressure is applied, which acts on a setting cylinder of the control device that is in operative connection with the lift actuator.
  • a mechanical feedback device for resetting the control piston.
  • This includes a return lever which engages in a corresponding groove in the actuating piston.
  • the return lever is in operative connection with the control piston.
  • the return lever of the return device is pivotally mounted about an axis.
  • a pin is formed, which deflects one of two rocker arms upon pivoting of the return lever.
  • a return spring is arranged between the hook-shaped end portions of the rocker arm.
  • the rocker arms engage with the spool to apply the aforementioned restoring force.
  • the return spring causes the centering of the control piston after switching off the control pressures acting on the control piston.
  • Additionally are on the adjusting piston Centering arranged by which the actuator piston is centered in the neutral position.
  • the mechanical return means are coupled via opposing acting, the restoring force generating springs in such a manner to the actuating means that the effect of the tension springs in the neutral position of the actuating means and the control repeals.
  • control means comprise a valve arrangement
  • control element comprises a valve slide of the valve arrangement.
  • a control valve is associated with each of the pressure surfaces within the valve arrangement, wherein the control valves work in opposite directions and the control slide of the two control valves are mechanically rigidly coupled and form a common valve spool.
  • control valves can each be designed as 3/3-way valves and be electromagnetically controllable.
  • the mechanical return means comprise a pivotable mounted about a pivot axis, two-armed return lever, that the tension springs engage with one end on one arm of the return lever, and that the other arm of the return lever so mechanically with the control is coupled, that a pivoting movement of the return lever is converted into a deflection movement of the control.
  • adjusting means are provided with which the restoring force generated by the tension springs in the neutral position of the actuating means and the control element can be adjusted to zero, wherein the adjusting means comprise in particular equipped with an eccentric adjusting mechanism, with which the Pivoting axis of the return lever in the pivoting plane can be offset.
  • a further embodiment of the invention is characterized in that the adjusting means comprise two oppositely operating, mechanically coupled to each other actuating piston, the via associated control pressure chambers can be acted upon with a control pressure, and that the tension springs are each secured with one end to one of the control piston.
  • the two actuating pistons engage via associated piston rods on an adjusting lever, by means of which an axial piston machine (hydrostat) mounted pivotably with a bearing journal can be pivoted to change the volume throughput.
  • an axial piston machine hydrostat mounted pivotably with a bearing journal
  • adjusting means comprise a hydraulic cylinder adjustable in displaced directions, whose actuating forces can be transmitted in both directions by means of corresponding piston rods, and that the tension springs each engage with one end on one of the piston rods.
  • the hydraulic cylinder may advantageously be a steering cylinder of a hydraulically assisted vehicle steering system.
  • the adjusting device according to the invention can be used with particular advantage in a machine unit equipped with an axial piston machine, in particular a continuously variable transmission.
  • Fig. 1 is shown in a simplified functional diagram, a first embodiment of an adjusting device according to the invention.
  • the adjusting device 10 comprises as actuating means two control pistons 12 and 15, which are each slidably mounted in an associated cylinder 11 and 14 and with the cylinder 11, 14 define a control pressure chamber 13 and 16, respectively, via control pressure lines 30 and 33 with a control pressure can be acted upon.
  • the two adjacent to the control pressure chambers 13, 16 pressure surfaces (51, 52 in Fig. 2A ) of the actuating piston 12, 15 act in the opposite direction.
  • the two adjusting pistons 12, 15 are rigidly connected in the example shown via a rod-like connecting element 18, but can also - as in Fig.
  • control pressures for the control pressure chambers 13, 16 of the actuating piston 12, 15 are provided via a control valve arrangement, which is connected on the input side to a feed line 35.
  • the control valve arrangement consists of two opposite directions arranged, electromagnetically actuated control valves 28 and 31, which are designed as 3/3-way valves (instead of the electromagnetic shown in the example but also just as good hydraulic or other actuators can be used).
  • Each of the control valves 28, 31 is actuated by means of an actuator (electromagnet) 29 and 32, respectively, and outputs in a conventional manner a control force to the control valve Valve slide, which is thereby displaced in the axial direction, so that the control pressure to the associated actuating piston 12, 15 passed and at the same time the respective opposite control pressure chamber 13, 16 relieved to the tank.
  • valve slide 27 by a corresponding control signal to one of the electromagnets 29, 32 to the left or right from the in Fig. 1 deflected shown neutral position, one of the control pressure chambers 13, 14 is acted upon by a corresponding control pressure and the actuating piston assembly 12, 15 is also made of their in Fig. 1 shown neutral position deflected.
  • To control the adjustment is generated by increasing the deflection of the restoring force by means of the deflection of the piston assembly 12, 15 and introduced into the valve spool 27 by a mechanical feedback so that it counteracts the magnetic force of the controlled electromagnet 29 and 32 respectively.
  • a pivot lever assembly which comprises a two-armed, pivotable about a pivot axis 24 return lever 23 which engages with a fork-shaped coupling piece 25 at the free end of one arm mounted on a valve spool 27 coupling pin 26.
  • two tension springs 21 and 22 are fixed with their one end in opposite directions.
  • the tension springs 21, 22 are attached to one of the adjusting pistons 12, 15.
  • valve spool 27 is deflected to the right and it flows according to Fig. 2C Hydraulic fluid via the control pressure line 30 in the control pressure chamber 13 of the control pressure piston 12 and there builds a control pressure, while 15 hydraulic fluid is discharged via the control pressure line 33 from the control pressure chamber 16 of the other actuating piston.
  • valve spool 27 is deflected due to the no longer compensated tensile force of the stretched tension spring in the opposite direction and causes an automatic and accurate return of the actuating piston 12, 15 in the neutral position.
  • Fig. 3A shows again the neutral position
  • Fig. 3B analogous to Fig. 2D the deflection to the right
  • the adjusting pistons 12, 15 act via the piston rods 18a, 18b and the bearing axle 36 on an adjusting lever 37 which is fastened to the (indicated) bearing journal 38 of an axial piston machine.
  • the displacement of the actuating piston thus leads to a pivoting of the axial piston machine and an associated change in the volume flow rate.
  • FIG. 4 Another embodiment of the adjustment device according to the invention, as is particularly suitable for hydraulic steering systems or the like, is known in Fig. 4 schematically illustrated:
  • a steering cylinder or generally a hydraulic cylinder 41 has a arranged in the cylinder center Control piston 53, which can be acted upon from either side via corresponding lines with a control pressure.
  • To control the control pressure turn two control valves 48 and 49 are provided, which analogous to Fig. 1 interact.
  • From the actuating piston 53 extending from both sides of the cylinder 41 outstanding two piston rods 42, 43, which are equipped at the free end with means (eg holes, eyes or the like.)
  • means eg holes, eyes or the like.
  • the tension springs 46, 47 engage a return lever 50, which, like the return lever 23 Fig. 1 the restoring forces on the valve assembly 48, 49 and preferably is also equipped with an adjustment mechanism 39.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Servomotors (AREA)
EP09007975A 2008-06-24 2009-06-18 Dispositif de réglage pour le réglage de machines à pistons axiaux. Withdrawn EP2138720A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH9632008 2008-06-24

Publications (2)

Publication Number Publication Date
EP2138720A2 true EP2138720A2 (fr) 2009-12-30
EP2138720A3 EP2138720A3 (fr) 2010-01-20

Family

ID=40524962

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09007975A Withdrawn EP2138720A3 (fr) 2008-06-24 2009-06-18 Dispositif de réglage pour le réglage de machines à pistons axiaux.

Country Status (1)

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EP (1) EP2138720A3 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010009975A1 (de) * 2010-03-03 2011-09-08 Sauer-Danfoss Gmbh & Co Ohg Verstellvorrichtung für Axialkolbenmaschinen
DE102012010726A1 (de) * 2011-10-31 2013-05-02 Alpha Fluid Hydrauliksysteme Müller GmbH Proportionalhydraulischer Linearantrieb
EP2860397A1 (fr) * 2013-09-24 2015-04-15 CLAAS Selbstfahrende Erntemaschinen GmbH Système d'entraînement pour organes de travail entraînés hydrauliquement d'une machine de travail
DE102014013925A1 (de) * 2014-09-18 2016-03-24 Alpha Fluid Hydrauliksysteme Müller GmbH Elektrohydraulischer Linearverstärker
WO2018189153A1 (fr) * 2017-04-13 2018-10-18 Danfoss Power Solutions Gmbh & Co Ohg Alimentation électrique autonome pour moteurs et pompes hydrostatiques
DE102020205336A1 (de) 2020-04-28 2021-10-28 Robert Bosch Gesellschaft mit beschränkter Haftung Hydromaschine mit sicherer Nullstellung und Gleichgang-Stellzylinder

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4002017A1 (de) 1990-01-24 1991-07-25 Linde Ag Verstellbare axialkolbenmaschine in schraegscheibenbauweise
EP0544086A2 (fr) 1991-11-28 1993-06-02 Robert Bosch Gmbh Système hydraulique de direction assistée pour véhicules automobiles
DE19540654C1 (de) 1995-10-31 1996-12-19 Brueninghaus Hydromatik Gmbh Verstellvorrichtung mit hydraulischer Zentriereinrichtung
DE19926965A1 (de) 1999-06-14 2000-12-21 Linde Ag Hydrostatische Verdrängereinheit
EP0802896B1 (fr) 1995-11-10 2001-01-03 Mitsui Chemicals, Inc. Procede de purification d'acide naphtatlenedicarboxylique brut
DE10043451A1 (de) 1999-09-03 2001-04-19 Sauer Inc Einteilige Proportionalregelung
DE10259314A1 (de) 2002-12-18 2004-07-15 Brueninghaus Hydromatik Gmbh Elektromagnet

Family Cites Families (7)

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DE2141724A1 (de) * 1971-08-20 1973-03-01 Bosch Gmbh Robert Steuer- und regeleinrichtung fuer eine hydropumpe
US4145887A (en) * 1974-11-06 1979-03-27 U.S. Philips Corporation Swashplate compensation mechanism
DE2834420C2 (de) * 1978-08-05 1986-11-27 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Lenkventil
DE2913534A1 (de) * 1979-04-04 1980-10-16 Bosch Gmbh Robert Einrichtung zur regelung des foerderstroms und zur begrenzung des foerderdrucks einer verstellbaren pumpe
US5122037A (en) * 1991-07-12 1992-06-16 Sauer, Inc. Manual displacement control
DE4125706C1 (fr) * 1991-08-02 1993-01-14 Hydromatik Gmbh, 7915 Elchingen, De
US7111545B1 (en) * 2001-05-14 2006-09-26 Hydro-Gear Limited Partnership Return to neutral device for a hydraulic apparatus

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4002017A1 (de) 1990-01-24 1991-07-25 Linde Ag Verstellbare axialkolbenmaschine in schraegscheibenbauweise
EP0544086A2 (fr) 1991-11-28 1993-06-02 Robert Bosch Gmbh Système hydraulique de direction assistée pour véhicules automobiles
DE19540654C1 (de) 1995-10-31 1996-12-19 Brueninghaus Hydromatik Gmbh Verstellvorrichtung mit hydraulischer Zentriereinrichtung
EP0802896B1 (fr) 1995-11-10 2001-01-03 Mitsui Chemicals, Inc. Procede de purification d'acide naphtatlenedicarboxylique brut
DE19926965A1 (de) 1999-06-14 2000-12-21 Linde Ag Hydrostatische Verdrängereinheit
DE10043451A1 (de) 1999-09-03 2001-04-19 Sauer Inc Einteilige Proportionalregelung
DE10259314A1 (de) 2002-12-18 2004-07-15 Brueninghaus Hydromatik Gmbh Elektromagnet

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010009975A1 (de) * 2010-03-03 2011-09-08 Sauer-Danfoss Gmbh & Co Ohg Verstellvorrichtung für Axialkolbenmaschinen
DE102012010726A1 (de) * 2011-10-31 2013-05-02 Alpha Fluid Hydrauliksysteme Müller GmbH Proportionalhydraulischer Linearantrieb
DE102012010726B4 (de) 2011-10-31 2023-10-19 Alpha Fluid Hydrauliksysteme Müller GmbH Proportionalhydraulischer Linearantrieb
EP2860397A1 (fr) * 2013-09-24 2015-04-15 CLAAS Selbstfahrende Erntemaschinen GmbH Système d'entraînement pour organes de travail entraînés hydrauliquement d'une machine de travail
DE102014013925A1 (de) * 2014-09-18 2016-03-24 Alpha Fluid Hydrauliksysteme Müller GmbH Elektrohydraulischer Linearverstärker
DE102014013925B4 (de) 2014-09-18 2025-04-24 Alpha Fluid Hydrauliksysteme Müller GmbH Elektrohydraulischer Linearverstärker
WO2018189153A1 (fr) * 2017-04-13 2018-10-18 Danfoss Power Solutions Gmbh & Co Ohg Alimentation électrique autonome pour moteurs et pompes hydrostatiques
DE102020205336A1 (de) 2020-04-28 2021-10-28 Robert Bosch Gesellschaft mit beschränkter Haftung Hydromaschine mit sicherer Nullstellung und Gleichgang-Stellzylinder
DE102020205336B4 (de) 2020-04-28 2024-10-24 Robert Bosch Gesellschaft mit beschränkter Haftung Hydromaschine mit sicherer Nullstellung und Gleichgang-Stellzylinder

Also Published As

Publication number Publication date
EP2138720A3 (fr) 2010-01-20

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