EP0766009B1 - Système pour contrôler un moteur hydraulique - Google Patents

Système pour contrôler un moteur hydraulique Download PDF

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Publication number
EP0766009B1
EP0766009B1 EP96112086A EP96112086A EP0766009B1 EP 0766009 B1 EP0766009 B1 EP 0766009B1 EP 96112086 A EP96112086 A EP 96112086A EP 96112086 A EP96112086 A EP 96112086A EP 0766009 B1 EP0766009 B1 EP 0766009B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
line
connection
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
EP96112086A
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German (de)
English (en)
Other versions
EP0766009A2 (fr
EP0766009A3 (fr
Inventor
Egon Dipl.-Ing. Tittmann
Heinz Ing. Walter (Grad.)
Berthold Dipl.-Ing.(Fh) Pfuhl
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0766009A2 publication Critical patent/EP0766009A2/fr
Publication of EP0766009A3 publication Critical patent/EP0766009A3/fr
Application granted granted Critical
Publication of EP0766009B1 publication Critical patent/EP0766009B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a control device of a hydraulic motor according to the in the preamble of Claim 1 specified genus.
  • the inventive device for controlling a hydraulic motor with the characteristic features of the main claim has the advantage that the Measuring throttle and the associated pressure loss are eliminated, the previous advantages of the facility in essentially be maintained.
  • the Measuring choke also dispenses with one of the assigned Control lines.
  • This is now in the facility Pressure drop of the check valve designed as a directional cartridge to control the differential pressure controlled changeover valve exploited.
  • This check valve is in the facility already available for switching the on and off Plunger control.
  • the present Also set up on the bypass check valve Measuring choke can be dispensed with. Overall, with present facility to a greater extent Achieve energy savings.
  • the facility is also building less complex and inexpensive.
  • FIG. 1 shows a device for control of a hydraulic motor in a simplified representation
  • Figure 2 shows a longitudinal section through the simplified in Figure 1 Shut-off valve shown
  • Figure 3 is a flow chart for the check valve of Figure 2
  • Figure 4 is a longitudinal section by the switching valve shown in simplified form in FIG. 1 and FIG. 5 characteristic curves for the reflux volume flow from the Cylinder when closing.
  • a device 10 for controlling a hydraulic motor which here as a differential cylinder 11 is designed, for example, as a locking cylinder in a plastic injection molding machine for operating a mold is used.
  • the differential cylinder 11 has one its large effective area assigned cylinder space 12 and one associated with the smaller effective area Annulus 13, their area ratio as 2: 1 is trained.
  • the device 10 has essentially as components designed as an electro-hydraulic control valve Proportional valve 14, a pressure-dependent controlled Switch valve 15, a pilot operated check valve 16, a Check valve 17 and a safety valve 18.
  • the proportional valve 14 which is known per se, has two stages trained in a control loop not shown switched and points next to a spring-centered Neutral position 19 with associated zero relief a first Working position 21 and a second working position 22.
  • An inlet port 23 designated by P is from a Pump 24 via an inlet line 25 with pressure medium supplied, the in the feed line 25 Safety valve 18 is switched.
  • Return port 26 is via a tank line 27, in the check valve 16 is switched with the tank 28 in Connection. From a first marked with A.
  • Motor connection 29 leads a first working line 31 into the Annulus 13 of the differential cylinder 11.
  • a second motor connection 32 designated by B is via a second working line 32 with the cylinder space 12 connected.
  • valve 16 As shown in FIG. 1 in connection with FIG. 2, there is the check valve 16 connected in the tank line 27 from a 2/2-way cartridge 34 in seat valve type, the hydraulically from a pilot valve Solenoid valve 35 is pilot controlled.
  • the check valve 16 is designed as a normally closed valve, because in the Way cartridge 34 of the valve body 36 on a spring 37 its assigned seat is pressed.
  • the separates Valve body 36 has an A connection 38 located on the end face from a laterally located B connection 39. During the A connection 38 over a section of the tank line 27 with the Proportional valve 14 has connection, the B port 39 relieved to tank 28.
  • the way cartridge 34 is more common Formed with an area ratio of 1: 1.6.
  • a control connection 41 of the directional cartridge 34 carries a first one Control line 42 to solenoid valve 35, which is a 4/3-way valve is executed.
  • a second leads from solenoid valve 35 Control line 43 via a throttle point 40 to the between Proportional valve 14 and check valve 16 lying section the tank line 27, so that the pressure upstream from Check valve 16 can be tapped in the tank line.
  • a third control line goes from the solenoid valve 35 44 from which leads to the switching valve 15.
  • the solenoid valve 35 has one Middle position 46, in which it is the first to third Control line 42 to 44 via the fourth control line 45 to Relieved tank 28.
  • the solenoid valve 35 in two Working positions are deflected, namely in one Parallel position 47 and 48 in a cross position Check valve can open and close the Tank line 27 also a kind of check valve function take.
  • Figure 3 shows a flow diagram for the way cartridge 34 according to FIG. 2, the characteristic curve 49 dependence of the Flow Q represents the pressure drop ⁇ P.
  • This Characteristic curve 49 applies to a certain nominal size, the Characteristic curves for smaller nominal sizes of way cartridges have a steeper course, while larger nominal sizes have a flatter characteristic curve.
  • As from the Characteristic curve 49 shows is each flow through the Path cartridge 34 assigned a certain pressure drop, so that this pressure via the third control line 44 for activation of the switching valve 15 can be used.
  • FIG. 1 shows in more detail, this is controlled as a function of pressure Switching valve 15 switched into a return line 51, which directly the cylinder space 12 of the cylinder 11 connects the tank 28.
  • the switching valve 15 as a 2/2-way cartridge in slide construction with an area ratio executed by 1: 1.
  • the way cartridge 52 is normal closed valve, its front A connection 53 to the tank 28 is relieved, while the radial lying B port 54 over a portion of the Return line 51 is connected to the cylinder chamber 12.
  • the slider 55 is moved by a spring 56 in the direction of it Blocked position loaded and in the same direction by the pressure in the A connection 53.
  • the third control line 44 is on one Control port 57 connected so that its pressure Slide 55 against the force of the spring 56 in the opening direction can deflect.
  • the way cartridge 52 works as a continuous acting throttle valve that is the size of the over the Return line 51 flowing volume flow proportional to the size of the control pressure prevailing in the control connection 57 controls.
  • a bypass line 58 is also provided for the plunger circuit provided by the section of the tank line 27 branches off between proportional valve 14 and check valve 34 and opens into the second working line 33. In this way is the return port 26 of the proportional valve 14 below Bypassing changeover valve 15 and check valve 16 directly connected to the cylinder space 12. In these Bypass line 58 the check valve 17 is switched so that it opens to the cylinder chamber 12.
  • the differential cylinder 11 is opened the side of the annular space 13 pressurized, so that the piston rod retracts.
  • Proportional valve 14 in its first working position 21 controlled and at the same time the solenoid valve 35 in his Cross position 48 deflected.
  • Pressure medium passes through the proportional valve 14 and first working line 31 in the annular space 13; simultaneously the cylinder chamber 12 becomes twice as large Volume flow displaced. This displaced volume flow divides in two sub-streams.
  • One of these partial flows is flowing over the second working line 33 and over the control edge B-T in the proportional valve 14 in the tank line 27 and continue via the open directional cartridge 34 of the check valve 16 to the tank 28.
  • the cartridge 34 is open because whose control connection 41 via the first control line 42 and the solenoid valve 35 located in the cross position 48 for fourth control line 45 and thus to the tank.
  • the second control line 42 pressure prevailing upstream of the path cartridge 34 the tank line 27 tapped and in the cross position 48 located solenoid valve 35 and the third control line 44 guided into the control connection 57 of the changeover valve 15.
  • the characteristic curve 49 in FIG. 3 shows, changes this tapped upstream from the path cartridge 34 Control pressure depending on the size of the tank 28 flowing volume flow. With this control pressure thus control the opening of the switching valve 15 so that the second partial flow from the cylinder chamber 12 via the Return line 51 can flow directly to the tank 28.
  • the switching valve 15 With increasing flow through the cartridge 34 is also the switching valve 15 increasingly open.
  • the functions acceleration and braking can thus be during the closing process using the electro-hydraulic controlled proportional valve 14 in a flawless manner carry out. All functions for the closing movement can only be driven when the safety valve 18 with position monitoring is open. That is only then possible if an assigned protective grille is closed has been.
  • Proportional valve 14 the cylinder chamber 12 with pressure medium must act.
  • Proportional valve in its second working position 22 controlled so that pressure medium from the pump 24 to Cylinder chamber 12 arrives and the piston rod first great force is expelled.
  • the annular space 13 of the Cylinder 11 via the first working line 31, the Control edge A-T in the proportional valve 14, the tank line 27 and the check valve 16 to the tank 28 is relieved.
  • the Solenoid valve 35 assumes its central position 46, so that the control port 41 in the way cartridge 34 is relieved and thus the cartridge 34 as a check valve can work.
  • the check valve 16 must also can only be designed for a simple volume flow and can have a correspondingly small nominal size.
  • the device 10 can also with a Operate differential cylinder in which the extending Piston rod causes the mold to close. Further can be set up for additional functions such as Pressure build-up and decompression also additional Valve elements are installed.
  • the two-stage Proportional valve 14 can also be a single stage Use control valve. That just flowed through Switch valve 15 can also be double-flow Execute changeover valve. Present facility is suitable especially for locking devices of spray and Blow molding machines.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)
  • Magnetically Actuated Valves (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (8)

  1. Installation pour commander un moteur hydraulique notamment un vérin de fermeture d'une machine d'injection de matière plastique, dans laquelle le moteur est constitué par un vérin différentiel (11) avec une chambre annulaire (13) et une chambre de cylindre (12), commandé par l'intermédiaire d'une vanne de régulation (14) électrohydraulique, comprenant :
    un composant générant une pression de commande qui au moins lorsqu'on vide la chambre (12) du cylindre est commuté sur un premier débit volumique donné par la vanne de régulation (14) et qui génère ainsi une pression de commande permettant de commander une vanne de commutation (15) à fonctionnement proportionnel, commandée en fonction de la différence de pression, vanne qui lorsqu'on vide la chambre (12) du vérin commande un second débit volumique vers le réservoir, en parallèle au premier débit volumique,
    un circuit à piston plongeur pour faire revenir un débit volumique sortant de la chambre annulaire à travers une conduite de dérivation (58) équipée d'un clapet anti-retour (17) fermé en direction du branchement de retour (26) pour revenir dans la chambre de cylindre (12) mise en pression, et
    une vanne d'arrêt (16) branchée dans une conduite de réservoir allant du branchement de retour (26) de la vanne de commutation (14) vers le réservoir et commandée par une vanne de commande amont (35).
    caractérisée en ce que
    la fonction du composant générant la pression de commande est assurée par la vanne d'arrêt (16) et au moins une conduite de commande (44) relie sa vanne de commande amont (35) à une vanne de commutation (15) à fonctionnement proportionnel vers la commande.
  2. Installation selon la revendication 1,
    caractérisée en ce que
    la vanne de commutation (15) est en forme de cartouche à tiroir à deux voies (52) à fonctionnement continu dont le branchement latéral (54), insensible à la pression est relié à la chambre (12) du vérin, alors que le branchement du côté frontal (53) sensible à la pression est déchargé vers le réservoir (28), et le tiroir (55) est sollicité dans le même sens de la pression dans le branchement (53) du côté de la face frontale par la force développée par un ressort (56) et dans le sens opposé par la pression dans la troisième conduite de commande (44), le tiroir (55) étant sollicité par le ressort (56) dans le sens d'une position de blocage et s'ouvrant contre la force du ressort (56).
  3. Installation selon la revendication 1 ou 2,
    caractérisée en ce que
    la vanne d'arrêt (16) présente une caractéristique de débit (49) correspondant à une résistance hydraulique (Δp) augmentant en continu avec le débit (Q).
  4. Installation selon la revendication 3,
    caractérisée en ce que
    la vanne d'arrêt (16) est une cartouche-tiroir à deux voies (34) du type soupape à siège dont le branchement du côté frontal (38) est relié à la vanne de régulation (14) et le branchement latéral (39) au réservoir (28), le corps de vanne (16) étant sollicité par le ressort (37) et la pression dans le branchement de commande (41) dans le sens de la fermeture, et par la pression dans le branchement du côté frontal (38) dans le sens de l'ouverture, avec en particulier un rapport de surfaces de 1 :1,6.
  5. Installation selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    la vanne d'arrêt (16) est branchée dans la conduite de réservoir (27) partant de la vanne de régulation (14), en aval de l'embranchement de la conduite de dérivation (58).
  6. Installation selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    le volume annulaire (13) du moteur hydraulique (11) reçoit du fluide sous pression pour fermer le moule.
  7. Installation selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce que
    l'électrovanne (35) servant à la commande amont de la vanne d'arrêt (16) est une vanne à 4/3 voies dont partent deux conduites de commande (42, 43) pour commander la cartouche-tiroir (34), une quatrième conduite de commande (45) étant reliée au réservoir (28) et une troisième conduite de commande (44) étant reliée au branchement de commande (57) de la vanne de commutation (15).
  8. Installation selon l'une ou plusieurs des revendications 1 à 7,
    caractérisée en ce que
    la conduite active (33) reliée à la chambre (12) du vérin, la conduite de dérivation (58) et la conduite de retour (51) constituent dans la zone comprise entre la vanne de régulation (14) et la chambre (12) du vérin un point de jonction commun.
EP96112086A 1995-09-26 1996-07-26 Système pour contrôler un moteur hydraulique Expired - Lifetime EP0766009B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19535677 1995-09-26
DE19535677A DE19535677A1 (de) 1995-09-26 1995-09-26 Einrichtung zur Steuerung eines hydraulischen Motors

Publications (3)

Publication Number Publication Date
EP0766009A2 EP0766009A2 (fr) 1997-04-02
EP0766009A3 EP0766009A3 (fr) 1999-06-09
EP0766009B1 true EP0766009B1 (fr) 2003-02-26

Family

ID=7773156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96112086A Expired - Lifetime EP0766009B1 (fr) 1995-09-26 1996-07-26 Système pour contrôler un moteur hydraulique

Country Status (5)

Country Link
EP (1) EP0766009B1 (fr)
KR (1) KR970016176A (fr)
AT (1) ATE233375T1 (fr)
DE (2) DE19535677A1 (fr)
TW (1) TW360755B (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3962670B2 (ja) * 2002-10-25 2007-08-22 株式会社アーステクニカ 旋動式破砕機の油圧回路およびその油圧回路の制御方法
DE102005035170B4 (de) * 2004-10-15 2013-11-21 Bosch Rexroth Ag Hydraulisch betätigte Gießeinheit
WO2018095963A1 (fr) * 2016-11-24 2018-05-31 Robert Bosch Gmbh Unité de coulée hydraulique
CN108716493B (zh) * 2018-07-25 2024-05-03 台州东仪机械制造有限公司 气缸节能***

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DE4020451A1 (de) * 1990-06-27 1992-01-02 Bosch Gmbh Robert Einrichtung zur steuerung eines hydraulischen motors
US5415076A (en) * 1994-04-18 1995-05-16 Caterpillar Inc. Hydraulic system having a combined meter-out and regeneration valve assembly

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Publication number Publication date
KR970016176A (ko) 1997-04-28
TW360755B (en) 1999-06-11
DE19535677A1 (de) 1997-03-27
EP0766009A2 (fr) 1997-04-02
DE59610165D1 (de) 2003-04-03
EP0766009A3 (fr) 1999-06-09
ATE233375T1 (de) 2003-03-15

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