EP0807212B1 - Dispositif pour actionner une commande hydrostatique - Google Patents

Dispositif pour actionner une commande hydrostatique Download PDF

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Publication number
EP0807212B1
EP0807212B1 EP96901186A EP96901186A EP0807212B1 EP 0807212 B1 EP0807212 B1 EP 0807212B1 EP 96901186 A EP96901186 A EP 96901186A EP 96901186 A EP96901186 A EP 96901186A EP 0807212 B1 EP0807212 B1 EP 0807212B1
Authority
EP
European Patent Office
Prior art keywords
pressure
resonant
resonance
pipe
resonator
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
EP96901186A
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German (de)
English (en)
Other versions
EP0807212A2 (fr
Inventor
Rudolf Scheidl
Werner Leitner
Gerald Riha
Dietmar Schindler
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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Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0807212A2 publication Critical patent/EP0807212A2/fr
Application granted granted Critical
Publication of EP0807212B1 publication Critical patent/EP0807212B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/20—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of a vibrating fluid
    • 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

Definitions

  • the invention relates to a device for controlling a hydrostatic Drive with a periodically actuated switching valve, the one with the hydrostatic drive connected resonance pipe for training standing Hydraulic fluid pressure waves alternate under resonance conditions a pressure medium supply line and connects to a return line.
  • the invention is therefore based on the object of a device for control a hydrostatic drive of the type described with simple constructive means so that the working pressure for the drive regardless of the way to work between the hydraulic fluid supply line offered maximum pressure and the pressure of the return line can be set, with a high efficiency and one good dynamics.
  • the invention solves the problem in that the resonance tube one Has pressure output in a vibration node of the standing pressure waves and that the switching times of the switching valve with a constant switching frequency are controllable.
  • a pressure outlet in a vibration node standing pressure waves that form in the resonance tube can initially a working pressure for the drive is made available to this pressure outlet without the resonance conditions caused by the drive's work path influence.
  • the fixed reflection end for the pressure waves is not through formed the drive, as is the case when connecting the drive to the resonance pipe end the case is.
  • the arrangement of the pressure outlet in a vibration node of the pressure waves the pressure waves of this Orders assigned to the node are suppressed at the pressure outlet can, so that despite a pulsed control, the temporal pulsation of the Working pressure at the pressure outlet is comparatively low.
  • the pulsation in time of the working pressure made available to the drive can further reduce in further development of the invention be provided that the resonance tube connected to the control valve forms a main resonator, at the pressure outlet at least one secondary resonator connects with a resonance tube, which in turn has a pressure outlet in an oscillation node that forms in this resonance tube has standing pressure waves, and that the resonance tube of the main resonator either connected in parallel with an additional resonance tube or at both ends with oppositely actuated switching valves with the pressure medium supply line and the return line can be connected.
  • the resonance tube of the main resonator either connected in parallel with an additional resonance tube or at both ends with oppositely actuated switching valves with the pressure medium supply line and the return line can be connected.
  • At least two secondary resonators are provided, these are each on connect the pressure output of the previous resonator and with exception of the secondary resonator on the output side from a parallel connection of to form at least two resonance tubes, one of which is the pressure outlet for connecting the subsequent resonator, thus also in the area the secondary resonators the resonance conditions for themselves in their resonance tubes forming pressure waves can be maintained.
  • pressure waves can be correspondingly higher Suppress order so that the remaining ripple to the respective Tolerance ranges can be adjusted.
  • the mutual spatial arrangement of the resonance tubes connected in parallel plays no role in the operation of this parallel connection.
  • the parallel Resonance pipes can therefore according to the respective space to be ordered. Particularly simple, space-saving design relationships arise in this context if the parallel Surround resonance tubes coaxially.
  • a control device for tracking the Switching frequency to the possibly changing resonance frequency of the immediate can be assigned to the control valve connected resonators.
  • To the main resonator can be used for this purpose for a specific measuring location predetermined pressure setpoint determined a certain position of the switching valve be with that at this measuring point at the corresponding switching valve position certain actual pressure is compared, so that a possibly occurring Target actual value difference via an adjustment of the switching frequency of the switching valve can be corrected.
  • Another option is to locate one Monitor the vibration node of the standing pressure waves. A change the resonance frequency due to a constant switching frequency of the switching valve a shift of the node, so that at the original Node pressure vibrations are detected by a controller the switching frequency of the switching valve for adaptation to the resonance frequency can be exploited.
  • the switching valve must be comparatively complying with the resonance frequencies ensure high switching frequencies, with pressure pulses flanks as steep as possible.
  • another Embodiment of the invention proposed the switching valve as a rotary piston valve with a rotary piston coaxially enclosing the resonance tube form, the axially arranged one behind the other in a housing, on the one hand with the hydraulic medium supply line and on the other hand with the Return line connected through annular chambers and in the area of these annular chambers Control edges forming, with through openings of the resonance tube has interacting passage openings, the release of which by a rotatable control sleeve with control edges for the switching times is controllable.
  • This rotary piston valve determines the switching frequency of the switching valve, so that the switching frequency is very simple Rotary drive can be controlled.
  • the rotary piston opens and closes the Passages of the resonance tube alternately in the area of the two Housing chambers, the switching times additionally through the control sleeve can be adjusted, which is adjustable in relation to the resonance tube is stored and through their control edges, the passage openings in the resonance tube releases sooner or later.
  • this control sleeve With the help of this control sleeve, the Pressure pulse width and thus the desired working pressure in a simple way Set way.
  • the tubular body can be used to achieve the required orthotropic properties of the resonance tube or the resonance tubes consist of a corrugated tube. It it is also possible to manufacture plastic pipes in a correspondingly orthotropic manner, whereby however, care must be taken to ensure that the dissipation in the tubular body itself is possible stays small. Can use the orthotropy for reducing friction also the elongation behavior of the tubular body in the circumferential and longitudinal directions be coordinated so that one can Fluid pressure caused circumferential expansion and the associated Shortening a corresponding change in length of the tubular body sets. Corresponds to the negative at a given hydraulic fluid pressure Longitudinal expansion of the tube body of the liquid compression, so none occurs Ralative movement between hydraulic fluid and tubular body.
  • the device for controlling a hydrostatic drive 1, which acts as a working cylinder has a switching valve 2, which has a suitable Drive 3 is actuated periodically.
  • This switching valve 2 connects a resonance tube 4 alternately with a hydraulic medium supply line 5 and one Return line 6 to a prestressed hydraulic fluid tank.
  • the length of the Resonance tube 4 corresponds to an integer multiple of the wavelength of the pressure waves of the hydraulic medium that form in the resonance tube 4 due to the pressure pulses resulting from the actuation of the switching valve Spread over the length of the resonance tube 4.
  • the resonance tube 4 also forms a fixed reflection end for these pressure waves standing under resonance conditions in the resonance tube 4 different pressure waves Order with vibration nodes, in which the through these nodes going pressure waves have no amplitude, so that by a Pressure outlet 7 in the area of such a node, the associated him Pressure waves are suppressed and the connected to this pressure outlet 7 Actuator 1 is subjected to a working pressure, which accordingly is less subject to fluctuations.
  • the commute to work Pressure output 7 connected drive 1 has the resonance conditions no influence in the resonance tube 4, which creates simple control conditions, because of the switching times of the switching valve that determine the pressure pulse width 2 the effective value at a switching frequency that is matched to the resonance frequency the working pressure at the pressure outlet 7 between any one of the pressure in the hydraulic medium supply line 5 corresponding maximum pressure and a minimum pressure corresponding to the pressure in the return line 6 is set can be.
  • the factors influencing the resonance conditions cannot always be considered be viewed constantly.
  • the toughness and the Compressibility of the hydraulic fluid with the fluctuations Temperature so that the device to the changing resonance conditions must be adjusted if the highest possible efficiency is desired becomes.
  • This adjustment can be made comparatively simply by a tracking the switching frequency of the switching valve 2 can be reached, as shown in FIG. 1 is indicated schematically.
  • the drive 3 for the switching valve 2 controlled by a control device 8, the possible shift of a vibration node monitored.
  • Belt filters 10 can be used to relocate vibration nodes on the specified one Pressure amplitudes occurring at the node of the vibration node assigned pressure waves detected and for controlling the switching valve drive 3 in the sense of tracking the switching frequency to the resonance frequency be exploited.
  • the band filter 10 can be set to the respective switching frequency of the switching valve can be matched, which in Fig. 1 by a Control line 11 between the switching valve drive 3 and the band filter 10 is illustrated.
  • the higher order pressure waves can be provided in general particularly favorable conditions in the area of a vibration node the fundamental wave of the pressure vibrations, i.e. in the longitudinal center of the Resonant tube 4.
  • the fundamental wave and the pressure harmonics suppressed with an odd atomic number at the pressure outlet 7.
  • the pressure output 7 of the Resonance tube 4 an additional resonance tube 12 and optionally in further sequence additional resonance tubes 13 are connected, namely each at the pressure outlet 7 of the immediately upstream resonance tube. If the pressure outlet 7 is arranged in the center, the resonance pipes each designed with half the length of the upstream resonance tube, as shown in Figs. 2 to 4.
  • FIG. 3 Another possibility is a fixed reflection end for the main resonator A. form, according to FIG. 3, is at the end of the resonance tube 4 to To provide switching valve 2 counter-operated switching valve 2a, so that Resonance pipe 4 on one side with the hydraulic medium supply line 5 and is connected at the other end to the return line 6 and vice versa, and with the respective resonance frequency.
  • the resonance tubes can be made orthotropic, a correspondingly lower rigidity is required in the axial direction, so that the tubular body is carried along by the hydraulic fluid in the axial direction can be.
  • the resonance pipes consist of corrugated tubes, which is illustrated in FIG. 5 for the main resonator A. is. In such a case, of course, must be ensured be that the pipe ends are held in place, which for reasons of clarity is not shown in detail.
  • the connection of the pressure outlet 7 must however permit a corresponding pipe movement.
  • the pressure outlet 7 is formed by a connecting sleeve 14, which from Resonance tube 4 is penetrated axially. Since the connector sleeve 14 Surrounds resonance tube 4 with a radial distance, the seal is through Ring cuffs 15 reached, the Relatiwerschieb between tube and Allow sleeve.
  • FIGS. 6 to 8 On Switch valve that meets these requirements is shown schematically in FIGS. 6 to 8 shown. It essentially consists of a resonant tube 4 Housing 16 in which a rotary piston coaxial with the resonance tube 4 17 is rotatably mounted, the two axially arranged one behind the other Intermediate chambers 18 and 19 of the housing 16 and in the area of both Has annular chambers 18, 19 through-openings 20 forming control edges, which cooperate with through openings 21 of the resonance tube 4.
  • a rotationally adjustable control sleeve 22 mounted in the housing 16 with Through openings 23 and control edges 24 formed by these is provided.
  • This control sleeve 22 can be adjusted via a ring gear 25.
  • the through openings 20 of the rotary piston 17 are in the opposite direction in the area of the annular chamber 19 connected to the return line 6 through the associated control edges 24 opened until they come out of the area of the passage openings 21 of the resonance tube 4 arrive, whereby an alternating Connection of the resonance tube 4 to the hydraulic medium supply line 5 and to the return line 6 is ensured.
  • the switching times are over the Determined rotational position of the control sleeve 22 relative to the resonance tube 4, while the switching frequency for a given number of over the scope distributed openings only from the speed of the rotary piston 17th depends. It can therefore be the pulse width at a set switching frequency by rotating the control sleeve 22 to control the hydrostatic Drive 1 can be adjusted as desired, which is in a corresponding Changes in the working pressure at the pressure outputs 7 noticeable.
  • annular chambers 18 are advantageous for this purpose and 19, in which pressure-elastic bodies are inserted for this purpose can, for example with compressed gas, e.g. B. nitrogen, filled ring tubes 27, which are indicated by dash-dotted lines in FIG. 6.
  • compressed gas e.g. B. nitrogen

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

Claims (9)

  1. Un dispositif destiné à la commande d'un entraínement (1) hydrostatique doté d'une valve (2) de commutation pouvant être actionnée de façon périodique, qui raccorde un tube (4) de résonance, lequel communique par voie hydraulique avec l'entraínement (1) hydrostatique et lequel est consacré à la formation d'ondes de pression stationnaires dans le fluide hydraulique sous des conditions de résonance, en alternance à une conduite (5) d'alimentation en fluide de pression et à une conduite (6) de retour, caractérisé en ce que le tube (4) de résonance présente, au niveau d'un noeud d'oscillation des ondes de pression stationnaires, une sortie (7) de pression communiquant par voie hydraulique avec l'entraínement (1) hydrostatique, et que les temps de commutation de la valve (2) de commutation pour une fréquence de commutation donnée peuvent être pilotés.
  2. Un dispositif conforme à la revendication n° 1, caractérisé en ce que le tube (4) de résonance raccordé à la valve (2) de commutation constitue un résonateur (A) principal, à la sortie (7) de pression duquel est raccordé au moins un résonateur (B) secondaire doté d'un tube (12) de résonance, lequel à son tour présente, au niveau d'un noeud d'oscillation des ondes de pression stationnaires se formant dans ce tube (12) de résonance. une sortie (7) de pression communiquant par voie hydraulique avec l'entraínement (1) hydrostatique, et que le tube (4) de résonance du résonateur (A) principal peut être raccordé à la conduite (5) d'alimentation en fluide de pression et à la conduite (6) de retour, soit au travers d'un tube (4a) de résonance supplémentaire branché en parallèle ou, en ses deux extrémités, au travers de valves (2, 2a) de commutation pouvant être actionnées dans des modes contraires.
  3. Un dispositif conforme à la revendication n° 2, caractérisé en ce que, lorsque au moins deux résonateurs (B. C) secondaires ont été prévus, chacun d'entre eux est raccordé à la sortie (7) de pression du résonateur (A, B) précédent et, à l'exception du résonateur (C) secondaire côté sortie, est constitué d'une connexion en parallèle de deux tubes (12, 12a) de résonance au moins, desquels l'un présente la sortie (7) de pression pour le raccordement du résonateur (C) secondaire suivant.
  4. Un dispositif conforme à une des revendications n° 1 à n° 3, caractérisé en ce que lors d'un branchement en parallèle de deux tubes (4, 4a; 12. 12a) de résonance. ceux-ci s'entourent l'un l'autre de façon coaxiale.
  5. Un dispositif conforme à une des revendications n° 1 à n°4, caractérisé en ce que un dispositif (8) de régulation, permettant d'ajuster la fréquence de commutation à la fréquence de résonance variable du résonateur (A), lequel est raccordé directement à la valve (2) de commande, est dédié à la valve (2) de commutation.
  6. Un dispositif conforme à une des revendications n° 1 à n° 5, caractérisé en ce que la valve (2) de commutation est conçue sous forme de valve à tiroir rotatif dotée d'un tiroir (17) rotatif, qui entoure le tube (4) de résonance de façon coaxiale, qui traverse des chambres (18, 19) annulaires, lesquelles sont disposées l'une derrière l'autre dans la direction axiale à l'intérieur d'un corps (16) et lesquelles sont raccordées d'une part à la conduite (5) d'alimentation en fluide de pression et d'autre part à la conduite (6) de retour, et qui à proximité de ces chambres (18, 19) annulaires présente des ouvertures (20) de passage, formant des arêtes de commande, agissant de pair avec des ouvertures (21) de passage du tube (4) de résonance, dont l'ouverture peut être commandée à l'aide d'une douille (22) de commande à angle de rotation modifiable, pourvue d'arêtes (24) de commande pour les temps de commutation.
  7. Un dispositif conforme à la revendication n° 6, caractérisé en ce que des corps à élasticité de compression, de préférence des flexibles (27) remplis d'un gaz sous pression, sont prévus dans les chambres (18, 19) annulaires du corps (16) de la valve (2) de commutation.
  8. Un dispositif conforme à une des revendications n° 1 à n° 7, caractérisé en ce que le corps de tube du tube (4) de résonance ou, le cas échéant, des tubes (4, 4a, 12, 12a, 13) de résonance, est conçu de façon orthotrope, avec une rigidité dans la direction de la périphérie supérieure à celle dans la direction axiale.
  9. Un dispositif conforme à la revendication n° 8, caractérisé en ce que le corps de tube du tube (4) de résonance ou, le cas échéant, des tubes (4, 4a, 12, 12a. 13) de résonance, est constitué d'un tube à pliage en étoile.
EP96901186A 1995-02-01 1996-01-31 Dispositif pour actionner une commande hydrostatique Expired - Lifetime EP0807212B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT16995 1995-02-01
AT169/95 1995-02-01
AT0016995A AT403219B (de) 1995-02-01 1995-02-01 Vorrichtung zum ansteuern eines hydrostatischen antriebes
PCT/AT1996/000015 WO1996023980A2 (fr) 1995-02-01 1996-01-31 Dispositif pour actionner une commande hydrostatique

Publications (2)

Publication Number Publication Date
EP0807212A2 EP0807212A2 (fr) 1997-11-19
EP0807212B1 true EP0807212B1 (fr) 2001-04-11

Family

ID=3483410

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96901186A Expired - Lifetime EP0807212B1 (fr) 1995-02-01 1996-01-31 Dispositif pour actionner une commande hydrostatique

Country Status (6)

Country Link
US (1) US5974800A (fr)
EP (1) EP0807212B1 (fr)
AT (2) AT403219B (fr)
CZ (1) CZ283346B6 (fr)
DE (1) DE59606770D1 (fr)
WO (1) WO1996023980A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATA150995A (de) * 1995-09-12 1997-12-15 Rudolf Scheidl Vorrichtung zum ansteuern eines hydrostatischen antriebes
DE19842534A1 (de) 1998-08-01 2000-02-03 Mannesmann Rexroth Ag Hydrostatisches Antriebssystem für eine Spritzgießmaschine und Verfahren zum Betreiben eines solchen Antriebssystems
US9121397B2 (en) 2010-12-17 2015-09-01 National Oilwell Varco, L.P. Pulsation dampening system for a reciprocating pump
US11338326B2 (en) 2019-04-07 2022-05-24 Resonance Technology International Inc. Single-mass, one-dimensional resonant driver
US11639728B2 (en) 2019-04-07 2023-05-02 Resonance Technology International Inc. Spool valve and piston geometry to reduce cavitation effects in a linear actuator

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3020720A (en) * 1957-02-20 1962-02-13 Albert K Spalding Method and means for producing hydraulic vibrations
FR1407445A (fr) * 1964-09-03 1965-07-30 Pic Sa Procédé et dispositif pour la transformation des différences de pression constante en pression pulsée
US3541782A (en) * 1968-10-24 1970-11-24 Shell Oil Co Control for resonant vibrating system
US3835810A (en) * 1969-09-04 1974-09-17 Energy Sciences Inc Pressure wave mixing
US3741073A (en) * 1971-01-29 1973-06-26 Moog Inc Hysteretic equalization in redundant electrically operated fluid powered servopositioning apparatus
ATE4662T1 (de) * 1978-07-03 1983-09-15 Mats Olsson Konsult Ab Niederfrequenz schallgeber.
DE2931797C2 (de) * 1979-08-04 1985-08-14 Kernforschungszentrum Karlsruhe Gmbh, 7500 Karlsruhe Steuervorrichtung für die Pulsationsbewegungen einer Pulskolonne
DE3314392A1 (de) * 1983-04-21 1984-10-25 Sieke, Helmut, Dipl.-Ing., 6200 Wiesbaden Verfahren und vorrichtung zur stufenlosen steuerung der geschwindigkeit und/oder beschleunigung von hydraulisch angetriebenen arbeitswerkzeugen
EP0229210A1 (fr) * 1986-01-16 1987-07-22 MOOG GmbH Régulateur pour un rouleau à paliers d'appui hydrostatiques
US4702315A (en) * 1986-08-26 1987-10-27 Bodine Albert G Method and apparatus for sonically stimulating oil wells to increase the production thereof
DE3852948T2 (de) * 1987-06-24 1995-09-21 Bies David A Schwingungsenergieerzeuger.
GB8823245D0 (en) * 1988-10-04 1989-04-19 British Aerospace Flextensional transducer
NL8902546A (nl) * 1989-10-13 1991-05-01 Pieter Faber Betonpompinrichting.
DE4116842A1 (de) * 1991-05-23 1992-11-26 Bw Hydraulik Gmbh Einrichtung zur hubbegrenzung eines hydraulikzylinders

Also Published As

Publication number Publication date
WO1996023980A2 (fr) 1996-08-08
WO1996023980A3 (fr) 1996-09-26
DE59606770D1 (de) 2001-05-17
ATE200559T1 (de) 2001-04-15
CZ283346B6 (cs) 1998-03-18
ATA16995A (de) 1997-04-15
AT403219B (de) 1997-12-29
CZ228597A3 (en) 1997-11-12
US5974800A (en) 1999-11-02
EP0807212A2 (fr) 1997-11-19

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