EP0850364B1 - Dispositif de commande d'un mecanisme d'entrainement hydrostatique - Google Patents

Dispositif de commande d'un mecanisme d'entrainement hydrostatique Download PDF

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Publication number
EP0850364B1
EP0850364B1 EP96931065A EP96931065A EP0850364B1 EP 0850364 B1 EP0850364 B1 EP 0850364B1 EP 96931065 A EP96931065 A EP 96931065A EP 96931065 A EP96931065 A EP 96931065A EP 0850364 B1 EP0850364 B1 EP 0850364B1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydrostatic drive
supply line
resonator
pressure 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.)
Expired - Lifetime
Application number
EP96931065A
Other languages
German (de)
English (en)
Other versions
EP0850364A1 (fr
Inventor
Rudolf Scheidl
Gerald Riha
Michael Garstenauer
Siegfried Grammer
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0850364A1 publication Critical patent/EP0850364A1/fr
Application granted granted Critical
Publication of EP0850364B1 publication Critical patent/EP0850364B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators
    • F15B21/125—Fluid oscillators or pulse generators by means of a rotating valve

Definitions

  • the invention relates to a device for controlling a hydrostatic Drive with a resonator connected to the hydrostatic drive and on the other hand connected to a pressure medium supply line and to a return line is, and with a periodically actuated switching valve that the resonator alternately connects to the pressure medium supply line and the return line.
  • a device for controlling a hydrostatic Drive with a resonator connected to the hydrostatic drive and on the other hand connected to a pressure medium supply line and to a return line is, and with a periodically actuated switching valve that the resonator alternately connects to the pressure medium supply line and the return line.
  • a device is e.g. from "ENERGIE FLUIDE, Vol. 14, No. 83, Dec. 1975, Paris FR, pages 28-32 ".
  • the throttle losses of throttle-controlled hydrostatic drives avoid it is known not to drive the drive continuously via a throttle valve, but periodically to a hydraulic medium supply line or a return line to be connected via a check valve connected in parallel Switching valves. Opening the switching valve in the hydraulic fluid supply line causes an acceleration of the drive, its inertia when closing this switching valve to relax the compressible hydraulic fluid in the Drive range leads to a pressure that is less than the closing pressure of the Check valve is in the area of the return line, so that over the return line Hydraulic fluid can be sucked in until the switching valve in the supply line opens again and the process is repeated.
  • the working pressure for the hydrostatic drive regardless of the way to work between the maximum pressure offered via the hydraulic medium supply line and to be able to adjust the pressure of the return line, it has already been proposed to connect the hydrostatic drive to a resonance pipe, which via a periodically actuated switching valve alternating with a pressure medium supply line and a return line is connected to standing in the resonance tube Generate pressure waves of the hydraulic fluid under resonance conditions.
  • a pressure outlet in a vibration node of the developing standing pressure waves in the resonance pipe succeed at this pressure outlet to provide a working pressure for the drive without the resonance conditions influenced by the drive's way to work.
  • the invention is therefore based on the object of a device for control hydrostatic drives of the type described in such a way that the use of a resonance tube is unnecessary and speeds are preferably controlled can be.
  • the resonator has at least one Pressure chamber with a movable, vibratory chamber limitation for Change in chamber volume shows that the movable chamber boundary a part of a single-mass transducer consisting of mass and spring or such a single-mass transducer itself and that alternate with the Pressure medium supply line, the return line and the hydrostatic drive connectable Pressure chamber via the switching valve with one in the over-resonance range of the Switching frequency lying at a vibrating mass can be applied.
  • the pressure chamber which can be changed in terms of its volume, interacts achieved with the single-mass transducer that during the connection the pressure chamber on the one hand with the pressure medium supply line and on the other hand with pressure medium flowing into the pressure chamber during the pressure chamber connection with the hydrostatic drive according to that in the spring of the single-mass oscillator stored energy is pressed out of the pressure chamber again, so that a volume flow dependent on the switching frequency of the switching valve sets hydraulic pressure medium, which is therefore also advantageous over the switching frequency of the switching valve can be controlled.
  • the volume flow of the hydraulic pressure medium to the hydrostatic drive also from the opening time of the switching valve for the connection of the pressure chamber depends on the pressure medium supply line, can be used to control the volume flow this opening time can be set.
  • the efficiency of the control device according to the invention depends on the friction occurring in the area of the mass oscillator, the Fluid friction and the pressure losses in the area of the switching valve from time to time can be influenced by the opening time of the switching valve, especially if the volume flow is controlled via the switching frequency. It turned out that for a favorable efficiency, the opening time of the switching valve for the Pressure medium supply line proportional to the pressure in the connecting line of the Drive must be changed.
  • connection times for the Connection line of the hydrostatic drive results from the choice of opening times for the Connection line of the hydrostatic drive. If the connection time of the Drive to the pressure chamber compared to its connection time to the pressure medium supply line and shortened to the return line accordingly, so that Drive a hydraulic medium pressure exceeding the pressure in the pressure medium supply line to provide. If the connection times are increased the drive to the pressure chamber, on the other hand, the volume flow with the Advantage can be lowered that the efficiency in contrast to a volume flow control not deteriorated over the opening time of the pressure medium supply line becomes.
  • the pressure chamber can be designed in different ways since it essentially only on a vibrating, changing the chamber volume Chamber boundary arrives.
  • the pressure chamber of the resonator consist of a cylinder, the movable chamber boundary resulting piston with at least one spring acting on the piston Bulk vibrator forms. This cylinder can only be used from one side hydraulic pressure medium are applied.
  • Another embodiment for the pressure chamber of the resonator is then achieved if the movable chamber boundary of the pressure chamber from a bellows or a membrane.
  • a spring-loaded mass can also a simple single-mass oscillator is provided for such a pressure chamber with similar effects.
  • the Switching valve can be designed as a rotary piston valve with a rotary piston the pressure chamber or the pressure chambers via control slots to the pressure medium supply line, the return line or the connecting line for the hydrostatic Drive connecting connection chambers alternately connects.
  • the control slots for a quick Ensure opening and closing of these connections.
  • the provision of a rotary piston also offers the advantage of evenly over several pressure chambers to be able to arrange the scope distributed.
  • the pressure chambers can both are controlled axially as well as radially, as are the oscillation axes of the single-mass oscillators these pressure chambers radially or axially parallel to the rotary piston can run.
  • radial oscillation axes of the single-mass oscillators allow with a corresponding arrangement, a perfect mass balance. Swing axes parallel to the axis, however, offer design advantages for loading on both sides Resonators.
  • a rotary piston valve To control the switching times of a rotary piston valve, its switching frequency depends on the piston speed, can coaxial to the rotary piston, opposite the pressure chamber or the one arranged rotationally symmetrical to the rotary piston
  • Druckkammem rotatable control body preferably in the form of control discs or sleeves can be provided with the control slots of the rotary piston form interacting control edges. Through these control edges the Control slots of the rotary piston released or closed so that the Rotational position of the control body forming the control edges, the switching times of the switching valve can be adjusted.
  • Control discs act via radially aligned Control edges together with the front control slots of the rotary piston, while the control sleeves axially directed control edges for in the piston skirt have provided control slots.
  • the device for controlling a hydrostatic drive for example a working cylinder, has a resonator 2 which, by means of a periodically actuatable switching valve 3, alternates with a pressure medium supply line 4, with a return line 5 to an optionally pre-stressed hydraulic medium tank and with the hydrostatic one Drive 1 is connected.
  • the resonator 2 is formed by a pressure chamber 6 with a movable, vibratable chamber boundary 7, specifically by a cylinder 8, the piston 9 of which acts as a single-mass oscillator with a spring 10 when the piston 9 is connected via a switching valve 3 connected to a suitable drive 11 is applied in the resonance range of the single-mass oscillator.
  • the switching valve 3 (switching position D) connects the resonator 2 to the pressure medium supply line 4, in order to then establish the connection to the return line 5 in the switching position R, namely in the time t R , in accordance with the inertia of the mass oscillator Hydraulic fluid from the return line 5 is sucked into the pressure chamber 6.
  • the hydraulic medium is then pressed over the piston 9 by the spring 10 into the connecting line 12 during the time t A , which corresponds to half the period in FIG. 2.
  • the volume flow through the resonator 2 is thus primarily dependent on the switching frequency f of the switching valve 3 and the relative opening time t D of the pressure medium supply line 4 within a switching period.
  • the opening time t D for the control of the volume flow q be used as the manipulated variable.
  • the opening time t D can be set in order to optimize the efficiency, which must be taken into account due to the inevitable friction and pressure losses.
  • the opening time t D is to be selected in proportion to the pressure available to the drive 1.
  • the opening time t A for the connecting line 12 need not correspond to half the period. If an opening time t A is chosen to be less than half the period, a pressure exceeding the pressure in the pressure medium supply line 4 can be provided for the drive 1. With longer opening times t A , however, the volume flow can be reduced without loss of efficiency.
  • 4 and 5 illustrate the relationships determined for optimum efficiency between the relative opening time t A , the pressure p at port A, based on the constant pressure in the pressure medium supply line, and the relative volume flow q, for opening times t A, on the one hand, and on the other hand, larger half the period, whereby the opening times t A were plotted on the x-axis of a spatial coordinate system, the relative pressure p on the y-axis and the volume flow q based on a nominal flow on the z-axis. The losses occurring were taken into account by a relative damping factor of 5%. 4 that the relative pressure p can be increased considerably as the opening times t A become smaller. If the opening times t A are extended over half the period, the volume flow q can again be controlled in the region of small quantities according to FIG. 5.
  • connection line 12 connected for a hydrostatic drive, but what is not absolutely necessary, because separate drives also have a common one Resonator can be controlled.
  • the mass of the single-mass oscillator does not have to pass through the piston 9 of a cylinder 8 are formed, as shown in FIG. 7, in which the pressure spaces 6 by membrane 14 are limited, the connecting flanges 15 for corresponding switching valves with the Connect the vibrating mass 16 in a liquid-tight manner and at the same time the springs 10 of the Form mass oscillators.
  • FIGS. 8 to 11 One with multiple resonators the associated switching valves uniting device that meet these requirements is shown schematically in FIGS. 8 to 11. It essentially exists from a housing 18 receiving a rotary piston 17, in which each other Cylinder bores opposite each other in pairs, aligned radially to the rotary piston 17 19 are supported with pistons 9 loaded by springs 10, which Represent mass oscillators according to FIG. 1.
  • the control sleeve 20 and the control body 27 can be rotated, specifically by means of drives which are not shown in detail for reasons of clarity.
  • the opening time t A for the switching connection A is determined by the rotational position of the control sleeve 20.
  • the division of the switching times t D and t R over the remaining period results from the rotational position of the control body 27 relative to the control sleeve 20.
  • control system As indicated in a block diagram in FIG. 1.
  • the drive 11 for the switching valve 3 and an actuating device 35 for the control sleeve 20 and the control body 27 are controlled via a control device 36 which controls the switching frequency f, the opening time t D for the switching connection D and optionally the opening time t A for the switching connection A. controls according to input characteristic fields that take into account the mutual dependency of the volume flow and the efficiency on the one hand on the manipulated variables and on the other hand on the pressure provided for the hydrostatic drive 1.
  • the switching valve 3 can therefore be set via the control device 36 in the sense of an optimal control of the drive 1 for the respective application.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Analytical Chemistry (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Vehicle Body Suspensions (AREA)
  • Valve Device For Special Equipments (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Reciprocating Pumps (AREA)

Claims (10)

  1. Un dispositif, destiné au pilotage d'un entraínement hydrostatique, doté d'un résonateur, qui est raccordé d'une part à l'entraínement hydrostatique et d'autre part à une conduite d'alimentation en fluide de pression et à une conduite de retour, et doté d'une valve de commutation pouvant être actionnée de façon périodique, qui raccorde le résonateur alternativement avec la conduite d'alimentation en fluide de pression et avec la conduite de retour, caractérisé en ce que le résonateur (2) présente au moins une chambre (6) de pression, qui est dotée d'une délimitation (7) de chambre mobile, pouvant vibrer et servant à faire varier le volume de la chambre, que la délimitation (7) de chambre mobile fait partie d'un résonateur à une masse, qui comprend une masse et un ressort (10), ou constitue elle-même un tel résonateur à une masse, et que la chambre (6) de pression, qui peut être raccordée alternativement à la conduite (4) d'alimentation en fluide de pression, à la conduite (5) de retour et à l'entraínement (1) hydrostatique, peut être soumise par la valve (3) de commutation à une fréquence de commutation, qui est supérieure à la fréquence de résonance du résonateur à une masse.
  2. Un dispositif conforme à la revendication n° 1, caractérisé en ce que la fréquence de commutation de la valve (3) de commutation est réglable.
  3. Un dispositif conforme à la revendication n° 1 ou n° 2, caractérisé en ce que le temps (tD) d'ouverture de la valve (3) de commutation pour le raccordement de la chambre (6) de pression avec la conduite (4) de fluide de pression est réglable.
  4. Un dispositif conforme à une des revendications n°1 à n°3, caractérisé en ce que le temps d'ouverture (tA) de la valve (3) de commutation pour le raccordement de la chambre (6) de pression avec l'entraínement (1) hydrostatique est réglable.
  5. Un dispositif conforme à une des revendications n°1 à n°4, caractérisé en ce que la conduite (12) de connexion entre la chambre(6) de pression et l'entraínement (1) hydrostatique est raccordée à un accumulateur (13) oléo-hydraulique.
  6. Un dispositif conforme à une des revendications n°1 à n°5, caractérisé en ce que la chambre (6) de pression du résonateur (2) est constituée par un vérin (8), dont le piston (9) donnant la délimitation (7) de chambre mobile constitue le résonateur à une masse, avec au moins un ressort (10) agissant sur le piston (9).
  7. Un dispositif conforme à la revendication n° 6, caractérisé en ce que le résonateur (2) est conçu sous forme d'un vérin (8) pouvant être sollicité des deux côtés, dont les deux chambres (6) de pression sont raccordées, de façon indépendante, d'un côté à la conduite (4) d'alimentation en fluide de pression et à la conduite (5) de retour et de l'autre côté à un entraínement (1) hydrostatique, par des valves (3) de commutation dont les périodes de commutation sont déphasées de 180° l'une par rapport à l'autre.
  8. Un dispositif conforme à une des revendications n°1 à n°5, caractérisé en ce que la délimitation (7) de chambre mobile de la chambre (6) de pression du résonateur (2) est constituée d'un soufflet ou d'une membrane (14).
  9. Un dispositif conforme à une des revendications n°1 à n°8, caractérisé en ce que la valve (3) de commutation est conçue sous forme de valve à tiroir rotatif dotée d'un tiroir (17) rotatif, qui raccorde la chambre (6) de pression ou, selon le cas, les chambres (6) de pression, au travers de rainures (21, 22, 23) de commande, alternativement à des chambres (24, 25, 26) de raccord connectées, selon le cas, à la conduite (4) d'alimentation en fluide de pression, à la conduite (5) de retour ou à la conduite (12) de raccordement de l'entraínement (1) hydrostatique.
  10. Un dispositif conforme à la revendication n° 9, caractérisé en ce que des corps de commande, dont la position angulaire est modifiable par rapport à la chambre (6) de pression ou, selon le cas, aux chambres (6) de pression, lesquelles sont disposées de façon symétrique en rotation par rapport au tiroir (17) rotatif, sont prévus, sont coaxiaux par rapport au tiroir (17) rotatif et sont de préférence conçus sous forme de galets ou de douilles (20) de commande, qui forment des arêtes (32, 33, 34) de commande agissant de pair avec les rainures (21, 22, 23) de commande du tiroir (17) rotatif.
EP96931065A 1995-09-12 1996-09-10 Dispositif de commande d'un mecanisme d'entrainement hydrostatique Expired - Lifetime EP0850364B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT150995 1995-09-12
AT1509/95 1995-09-12
AT0150995A ATA150995A (de) 1995-09-12 1995-09-12 Vorrichtung zum ansteuern eines hydrostatischen antriebes
PCT/EP1996/003964 WO1997010444A1 (fr) 1995-09-12 1996-09-10 Dispositif de commande d'un mecanisme d'entrainement hydrostatique

Publications (2)

Publication Number Publication Date
EP0850364A1 EP0850364A1 (fr) 1998-07-01
EP0850364B1 true EP0850364B1 (fr) 2000-01-26

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ID=3515264

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Application Number Title Priority Date Filing Date
EP96931065A Expired - Lifetime EP0850364B1 (fr) 1995-09-12 1996-09-10 Dispositif de commande d'un mecanisme d'entrainement hydrostatique

Country Status (6)

Country Link
US (1) US6082108A (fr)
EP (1) EP0850364B1 (fr)
AT (2) ATA150995A (fr)
CZ (1) CZ286073B6 (fr)
DE (1) DE59604316D1 (fr)
WO (1) WO1997010444A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0857877A3 (fr) 1997-02-08 1999-02-10 Mannesmann Rexroth AG Convertisseur pneumatique-hydraulique
DE19842534A1 (de) 1998-08-01 2000-02-03 Mannesmann Rexroth Ag Hydrostatisches Antriebssystem für eine Spritzgießmaschine und Verfahren zum Betreiben eines solchen Antriebssystems
JP2005299682A (ja) * 2001-10-26 2005-10-27 Kyowa Hakko Kogyo Co Ltd 脈動空気振動波発生装置
US7464552B2 (en) * 2004-07-02 2008-12-16 Siemens Energy, Inc. Acoustically stiffened gas-turbine fuel nozzle

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3046951A (en) * 1961-03-27 1962-07-31 Honeywell Regulator Co Hydraulic control valve
US3228301A (en) * 1963-02-27 1966-01-11 Univ Iowa State Res Found Inc Pneumatic sawtooth oscillator
DE2414043A1 (de) * 1974-03-21 1975-10-02 Rainer Dipl Ing Sieke Verfahren und vorrichtung zur beaufschlagung eines mediums mit vibrationen
DE2516154A1 (de) * 1975-04-14 1976-10-21 Louda Guenther Impulsgeber
DE4324595C1 (de) * 1993-07-22 1994-12-15 Escher Wyss Gmbh Schüttelbock
US5540052A (en) * 1994-08-16 1996-07-30 Sieke; Ingrid D. Pulse hydraulic systems and methods therefor
AT403219B (de) * 1995-02-01 1997-12-29 Scheidl Rudolf Dipl Ing Dr Tec Vorrichtung zum ansteuern eines hydrostatischen antriebes

Also Published As

Publication number Publication date
ATA150995A (de) 1997-12-15
DE59604316D1 (de) 2000-03-02
EP0850364A1 (fr) 1998-07-01
US6082108A (en) 2000-07-04
CZ286073B6 (cs) 2000-01-12
ATE189295T1 (de) 2000-02-15
CZ74398A3 (cs) 1999-10-13
WO1997010444A1 (fr) 1997-03-20

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