EP0850364B1 - Vorrichtung zum ansteuern eines hydrostatischen antriebes - Google Patents
Vorrichtung zum ansteuern eines hydrostatischen antriebes Download PDFInfo
- 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
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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.
Landscapes
- 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)
Description
- Fig. 1
- eine erfindungsgemäße Vorrichtung zum Steuern eines hydrostatischen Antriebes in einem einfachen Blockschaltbild,
- Fig. 2
- eine zeitliche Abfolge der Schaltstellungen eines Schaltventiles in einem Koordinatensystem, auf dessen Ordinate die drei Schaltstellungen und auf dessen Abszisse die auf die Periodendauer bezogenen Schaltzeiten aufgetragen sind,
- Fig. 3
- die Abhängigkeit des auf einen Nennstrom bezogenen mittleren Volumenstromes durch den Resonator von der auf die Resonanzfrequenz bezogenen Schaltfrequenz des Schaltventiles und der auf die Schaltperiode bezogenen Öffnungszeit der Druckmittelversorgungsleitung in einem räumlichen Koordinatensystem, die
- Fig. 4 und 5
- die gegenseitige Abhängigkeit des mittleren Volumenstromes durch den Resonator, der auf die Schaltperiode bezogenen Öffnungszeit des Anschlusses für den hydrostatischen Antrieb und des auf den Druck in der Versorgungsleitung bezogenen Druckes in der Anschlußleitung für den hydrostischen Antrieb in einem räumlichen Koordinatensystem,
- Fig. 6
- ein Blockschaltbild einer gegenüber der Fig. 1 erweiterten erfindungsgemäßen Vorrichtung,
- Fig. 7
- eine weitere Ausführungsform eines Resonators in einem vereinfachten Axialschnitt,
- Fig. 8
- einen vereinfachten Axialschnitt durch ein Schaltventil,
- Fig. 9
- einen Schnitt nach der Linie IX-IX der Fig. 8,
- Fig. 10
- einen Schnitt nach der Linie X-X der Fig. 8 und
- Fig. 11
- einen Schnitt nach der Linie XI-XI der Fig. 8.
Claims (10)
- Vorrichtung zum Steuem eines hydrostatischen Antriebes mit einem Resonator, der einerseits an den hydrostatischen Antrieb und anderseits an eine Druckmittelversorgungsleitung und an eine Rückleitung angeschlossen ist, und mit einem periodisch betätigbaren Schaltventil, das den Resonator abwechselnd mit der Druckmittelversorgungsleitung und der Rückleitung verbindet, dadurch gekennzeichnet. daß der Resonator (2) wenigstens eine Druckkammer (6) mit einer beweglichen, schwingungsfähigen Kammerbegrenzung (7) zur Veränderung des Kammervolumens aufweist, daß die bewegliche Kammerbegrenzung (7) einen Teil eines aus Masse und Feder (10) bestehenden Einmassenschwingers oder einen solchen Einmassenschwinger selbst bildet und daß die abwechselnd mit der Druckmittelversorgungsleitung (4), der Rückleitung (5) und dem hydrostatischen Antrieb (1) verbindbare Druckkammer (6) über das Schaltventil (3) mit einer im Überresonanzbereich des Einmassenschwingers liegenden Schaltfrequenz beaufschlagbar ist.
- Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Schaltfrequenz des Schaltventiles (3) einstellbar ist.
- Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Öffnungszeit (tD) des Schaltventiles (3) für die Verbindung der Druckkammer (6) mit der Druckmittelleitung (4) einstellbar ist.
- Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Öffnungszeit (tA) des Schaltventiles (3) für die Verbindung der Druckkammer (6) mit dem hydrostatischen Antrieb (1) einstellbar ist.
- Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Anschlußleitung (12) zwischen der Druckkammer (6) und dem hydrostatischen Antrieb (1) mit einem Druckspeicher (13) verbunden ist.
- Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Druckkammer (6) des Resonators (2) aus einem Zylinder (8) besteht, dessen die bewegliche Kammerbegrenzung (7) ergebender Kolben (9) mit wenigstens einer auf den Kolben (9) wirkenden Feder (10) den Einmassenschwinger bildet.
- Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß der Resonator (2) als beidseitig beaufschlagbarer Zylinder (8) ausgebildet ist, dessen beide Druckräume (6) über zwei hinsichtlich ihrer Schaltperioden um 180° phasenversetzte Schaltventile (3) je für sich einerseits an die Druckmittelversorgungsleitung (4) und die Rückleitung (5) sowie anderseits an einen hydrostatischen Antrieb (1) angeschlossen sind.
- Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die bewegliche Kammerbegrenzung (7) der Druckkammer (6) des Resonators (2) aus einem Balg oder einer Membrane (14) besteht.
- Vorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß das Schaltventil (3) als Rotationskolbenventil mit einem Rotationskolben (17) ausgebildet ist, der die Druckkammer (6) bzw. die Druckkammern (6) über Steuerschlitze (21, 22, 23) mit an die Druckmittelversorgungsleitung (4), die Rückleitung (5) bzw. die Anschlußleitung (12) für den hydrostatischen Antrieb (1) verbundene Anschlußkammern (24, 25, 26) abwechselnd verbindet.
- Vorrichtung nach Anspruch 9, dadurch gekennzeichnet, daß zum Rotationskolben (17) koaxiale, gegenüber der Druckkammer (6) bzw. den zum Rotationskolben (17) rotationssymmetrisch angeordneten Druckkammern (6) drehverstellbare Steuerkörper, vorzugsweise in Form von Steuerscheiben oder -hülsen (20), vorgesehen sind, die mit den Steuerschlitzen (21, 22, 23) des Rotationskolbens (17) zusammenwirkende Steuerkanten (32, 33, 34) bilden.
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 (de) | 1995-09-12 | 1996-09-10 | Vorrichtung zum ansteuern eines hydrostatischen antriebes |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0850364A1 EP0850364A1 (de) | 1998-07-01 |
EP0850364B1 true EP0850364B1 (de) | 2000-01-26 |
Family
ID=3515264
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96931065A Expired - Lifetime EP0850364B1 (de) | 1995-09-12 | 1996-09-10 | Vorrichtung zum ansteuern eines hydrostatischen antriebes |
Country Status (6)
Country | Link |
---|---|
US (1) | US6082108A (de) |
EP (1) | EP0850364B1 (de) |
AT (2) | ATA150995A (de) |
CZ (1) | CZ286073B6 (de) |
DE (1) | DE59604316D1 (de) |
WO (1) | WO1997010444A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0857877A3 (de) | 1997-02-08 | 1999-02-10 | Mannesmann Rexroth AG | Pneumatisch-hydraulischer Wandler |
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)
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 |
-
1995
- 1995-09-12 AT AT0150995A patent/ATA150995A/de not_active Application Discontinuation
-
1996
- 1996-09-10 CZ CZ1998743A patent/CZ286073B6/cs not_active IP Right Cessation
- 1996-09-10 DE DE59604316T patent/DE59604316D1/de not_active Expired - Lifetime
- 1996-09-10 WO PCT/EP1996/003964 patent/WO1997010444A1/de active IP Right Grant
- 1996-09-10 EP EP96931065A patent/EP0850364B1/de not_active Expired - Lifetime
- 1996-09-10 US US09/043,260 patent/US6082108A/en not_active Expired - Fee Related
- 1996-09-10 AT AT96931065T patent/ATE189295T1/de active
Also Published As
Publication number | Publication date |
---|---|
ATA150995A (de) | 1997-12-15 |
DE59604316D1 (de) | 2000-03-02 |
EP0850364A1 (de) | 1998-07-01 |
US6082108A (en) | 2000-07-04 |
CZ286073B6 (cs) | 2000-01-12 |
ATE189295T1 (de) | 2000-02-15 |
CZ74398A3 (cs) | 1999-10-13 |
WO1997010444A1 (de) | 1997-03-20 |
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