EP0766009A2 - Système pour contrÔler un moteur hydraulique - Google Patents

Système pour contrÔler un moteur hydraulique Download PDF

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Publication number
EP0766009A2
EP0766009A2 EP96112086A EP96112086A EP0766009A2 EP 0766009 A2 EP0766009 A2 EP 0766009A2 EP 96112086 A EP96112086 A EP 96112086A EP 96112086 A EP96112086 A EP 96112086A EP 0766009 A2 EP0766009 A2 EP 0766009A2
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
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.)
Granted
Application number
EP96112086A
Other languages
German (de)
English (en)
Other versions
EP0766009B1 (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 device for controlling a hydraulic motor according to the type specified in the preamble of claim 1.
  • a hydraulic differential cylinder can be controlled via an electrohydraulic directional control valve, which cooperates with a proportionally operating changeover valve which is controlled as a function of the differential pressure.
  • This changeover valve can be controlled via a measuring throttle which is connected to a volume flow controlled by the control valve.
  • volume flows can be controlled when controlling the hydraulic motor, the size of which considerably exceeds the nominal size of the control valve itself.
  • a plunger circuit can also be implemented when the piston rod is extended, the volume flow flowing out of the annular space being at least partially returned to the cylinder space.
  • the control valve therefore does not have to process volume flows in excess of its nominal size in either working direction of the differential cylinder.
  • the measuring throttle enables a particularly precise control of the volume flow, it can be disadvantageous in some cases that the measuring throttle requires additional effort, especially since two control lines are also required to control the differential pressure-controlled changeover valve.
  • the measuring throttle generates an additional pressure loss in the volume flow, which must already overcome the flow resistances of the control valve and a check valve.
  • an additional bypass check valve is required when a small measuring throttle is arranged between the motor and the control valve in order to avoid unnecessary pressure losses.
  • the device according to the invention for controlling a hydraulic motor with the characterizing features of the main claim has the advantage that the measuring throttle and the pressure loss associated with it are eliminated, the previous advantages of the device being essentially retained. With the elimination of the measuring throttle, one of the assigned control lines is no longer required.
  • the pressure drop of the check valve designed as a directional cartridge is now used to control the differential pressure-controlled changeover valve. This check valve is already present in the device for switching the plunger control on and off.
  • the bypass check valve can also be used Measuring choke can be omitted. Overall, energy saving can be achieved to an increased extent with the present device. In addition, the facility builds less complex and inexpensive.
  • FIG. 1 shows a device for controlling a hydraulic motor in a simplified representation
  • FIG. 2 shows a longitudinal section through the shut-off valve shown in simplified form in FIG. 1
  • FIG. 3 shows a flow diagram for the shut-off valve according to FIG. 2
  • FIG. 4 shows a longitudinal section through the simplified view shown in FIG. 1
  • FIG. 1 shows a device 10 for controlling a hydraulic motor, which is designed here as a differential cylinder 11, as is used, for example, as a locking cylinder in a plastic injection molding machine for actuating a mold.
  • the differential cylinder 11 has a cylinder space 12 assigned to its large effective area and an annular space 13 assigned to the smaller effective area, the area ratio of which is 2: 1.
  • the device 10 essentially has, as components, a proportional valve 14 designed as an electrohydraulic control valve, a pressure-controlled changeover 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 a two-stage design, is switched into a control circuit (not shown in more detail) and, in addition to a spring-centered neutral position 19 with associated zero relief, has a first working position 21 and a second working position 22.
  • An inlet connection 23, designated P, is supplied with pressure medium by a pump 24 via an inlet line 25, the safety valve 18 being connected to the inlet line 25.
  • a return port 26 designated T is connected to the tank 28 via a tank line 27, into which the check valve 16 is connected.
  • a first working line 31 leads from a first motor connection 29 labeled A into the annular space 13 of the differential cylinder 11.
  • a second motor connection 32 labeled B is correspondingly connected to the cylinder chamber 12 via a second working line 32.
  • the shut-off valve 16 connected to the tank line 27 consists of a 2/2-way cartridge 34 of the poppet type, which is hydraulically piloted by a solenoid valve 35 serving as a pilot valve.
  • the check valve 16 is designed as a normally closed valve, since in the directional cartridge 34, the valve body 36 is pressed onto its associated seat by a spring 37.
  • the valve body 36 separates an A connection 38 located on the end face from a laterally located B connection 39. While the A connection 38 is connected to the proportional valve 14 via a section of the tank line 27, the B connection 39 to the tank 28 is relieved .
  • the path cartridge 34 is formed in the usual way with an area ratio of 1: 1.6.
  • a first control line 42 leads from a control connection 41 of the directional cartridge 34 to the solenoid valve 35, which is designed as a 4/3-way valve.
  • a second control line 43 leads from the solenoid valve 35 via a throttle point 40 to the section of the tank line 27 lying between the proportional valve 14 and the check valve 16, so that the pressure upstream from the check valve 16 in the tank line can be tapped.
  • a third control line 44 leads from the solenoid valve 35 and leads to the changeover valve 15.
  • the solenoid valve 35 is connected to the tank 28 via a fourth control line 45.
  • the solenoid valve 35 has a central position 46, in which it relieves the first to third control lines 42 to 44 via the fourth control line 45 to the tank 28.
  • the solenoid valve 35 can be deflected in two working positions, namely in a parallel position 47 and in a cross position 48. In addition to opening and closing the Tank line 27 also take over a kind of check valve function.
  • FIG. 3 shows a flow diagram for the directional cartridge 34 according to FIG. 2, the characteristic curve 49 representing the dependence of the flow Q on the pressure drop ⁇ P.
  • the characteristic curve 49 represents the dependence of the flow Q on the pressure drop ⁇ P.
  • the flow resistance also increases with the flow.
  • This characteristic curve 49 applies to a specific nominal size, the characteristic curves for smaller nominal sizes of way cartridges having a steeper course, while larger nominal sizes have a flatter characteristic curve course.
  • a certain pressure drop is assigned to each flow through the directional cartridge 34, so that this pressure can be used via the third control line 44 to actuate the changeover valve 15.
  • the pressure-controlled changeover valve 15 is connected to a return line 51, which connects the cylinder space 12 of the cylinder 11 directly to the tank 28.
  • the changeover valve 15 is designed as a 2/2-way cartridge in a slide construction with an area ratio of 1: 1.
  • the directional cartridge 52 is designed as a normally closed valve, the front-side A connection 53 to the tank 28 is relieved, while the radial B connection 54 is connected to the cylinder chamber 12 via a section of the return line 51.
  • the slide 55 is loaded by a spring 56 in the direction of its blocking position and in the same direction by the pressure in the A connection 53.
  • the third control line 44 is connected to a control connection 57 so that its pressure pushes the slide 55 against the force of the spring 56 in the opening direction can deflect.
  • the directional cartridge 52 works as a continuously acting throttle valve, which is the size of the over Return line 51 flowing volume flow proportional to the size of the control pressure prevailing in the control port 57 controls.
  • a bypass line 58 is also provided for the plunger circuit, which branches off from the section of the tank line 27 between the proportional valve 14 and the blocking valve 34 and opens into the second working line 33. In this way, the return port 26 of the proportional valve 14 is directly connected to the cylinder chamber 12, bypassing the changeover valve 15 and check valve 16.
  • the check valve 17 is connected in this bypass line 58 in such a way that it opens towards the cylinder chamber 12.
  • the differential cylinder 11 is pressurized on the side of the annular space 13 so that the piston rod retracts.
  • the proportional valve 14 is controlled into its first working position 21 and at the same time the solenoid valve 35 is deflected into its cross position 48.
  • Pressure medium delivered by the pump 24 reaches the annular space 13 via the proportional valve 14 and the first working line 31; at the same time, a twice as large volume flow is displaced from the cylinder chamber 12.
  • This displaced volume flow is divided into two partial flows.
  • One of these partial flows flows via the second working line 33 and via the control edge BT in the proportional valve 14 into the tank line 27 and further via the open directional cartridge 34 of the shut-off valve 16 to the tank 28.
  • the directional cartridge 34 is opened because its control connection 41 is via the first control line 42 and the solenoid valve 35 located in the cross position 48 fourth control line 45 and thus to the tank.
  • the pressure prevailing upstream from the directional cartridge 34 in the tank line 27 is tapped via the second control line 42 and conducted into the control connection 57 of the changeover valve 15 via the solenoid valve 35 located in the cross position 48 and the third control line 44.
  • this control pressure tapped upstream of the directional cartridge 34 changes depending on the size of the volume flow flowing to the tank 28.
  • the opening of the changeover valve 15 can thus be controlled, so that the second partial flow can flow out of the cylinder chamber 12 via the return line 51 directly to the tank 28.
  • the changeover valve 15 is increasingly opened.
  • a first characteristic curve 61 shows the course of the volume flow flowing to the tank 28 via the proportional valve 14, while a second characteristic curve 62 shows the second partial flow flowing to the tank 28 via the changeover valve 15. It can be clearly seen from FIG. 5 that the changeover valve 15 only opens relatively delayed in relation to the proportional valve 14.
  • the third characteristic curve 63 now illustrates the total volume flow Q flowing to the tank, which here is almost twice as large in the end stroke range as the partial flow controlled by the proportional valve 14 according to characteristic curve 61.
  • the proportional directional control valve 14 can therefore be used in a relatively small nominal size.
  • the pressure drop of the check valve 16 is used, which is in any case available for performing a plunger control.
  • the via the proportional valve 14 and the directional cartridge 34 for The volume flow flowing out of the tank therefore no longer needs to flow through a third throttle point in the form of a measuring throttle, so that the control system saves energy.
  • only a single, third control line 44 is required in order to lead the tapped control pressure via the solenoid valve 35 to the changeover valve 15.
  • the functions of acceleration and braking can thus be carried out in a faultless manner during the closing process with the aid of the electrohydraulically controlled proportional valve 14.
  • the entire functions for the closing movement can only be operated when the safety valve 18 with position monitoring is open. This is only possible if an assigned protective grille has been closed.
  • the piston rod in the differential cylinder 11 must be extended, for which purpose the proportional valve 14 must pressurize the cylinder chamber 12.
  • the proportional valve is controlled in its second working position 22, so that pressure medium from the pump 24 reaches the cylinder chamber 12 and the piston rod is first ejected with great force.
  • the annular space 13 of the cylinder 11 is relieved to the tank 28 via the first working line 31, the control edge AT in the proportional valve 14, the tank line 27 and the check valve 16.
  • the solenoid valve 35 assumes its central position 46 so that the control connection 41 in the directional cartridge 34 is relieved and the directional cartridge 34 can thus operate as a check valve.
  • the device 10 can also be operated with a differential cylinder, in which the extending piston rod causes the mold to close.
  • additional valve elements can also be installed in the device for additional functions such as pressure build-up and decompression.
  • a one-stage control valve can also be used.
  • the single-flow switch valve 15 can also be double-flow Execute changeover valve.
  • the present device is particularly suitable for locking devices of injection molding and blowing machines.

Landscapes

  • 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)
  • Valve Device For Special Equipments (AREA)
  • Magnetically Actuated Valves (AREA)
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
DE19535677A DE19535677A1 (de) 1995-09-26 1995-09-26 Einrichtung zur Steuerung eines hydraulischen Motors
DE19535677 1995-09-26

Publications (3)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1299012C (zh) * 2002-10-25 2007-02-07 日本阿尔斯泰克 旋回式破碎机的液压回路及其控制方法
CN108716493A (zh) * 2018-07-25 2018-10-30 台州东仪机械制造有限公司 气缸节能系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005035170B4 (de) * 2004-10-15 2013-11-21 Bosch Rexroth Ag Hydraulisch betätigte Gießeinheit
DE102017220832A1 (de) * 2016-11-24 2018-05-24 Robert Bosch Gmbh Hydraulische Gießeinheit

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4020451A1 (de) 1990-06-27 1992-01-02 Bosch Gmbh Robert Einrichtung zur steuerung eines hydraulischen motors

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3960059A (en) * 1974-12-09 1976-06-01 Caterpillar Tractor Co. Fast exhaust circuit for hydraulic jacks
US4194532A (en) * 1978-04-10 1980-03-25 Caterpillar Tractor Co. Control valve with bypass means
US5415076A (en) * 1994-04-18 1995-05-16 Caterpillar Inc. Hydraulic system having a combined meter-out and regeneration valve assembly

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4020451A1 (de) 1990-06-27 1992-01-02 Bosch Gmbh Robert Einrichtung zur steuerung eines hydraulischen motors

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1299012C (zh) * 2002-10-25 2007-02-07 日本阿尔斯泰克 旋回式破碎机的液压回路及其控制方法
CN108716493A (zh) * 2018-07-25 2018-10-30 台州东仪机械制造有限公司 气缸节能系统
CN108716493B (zh) * 2018-07-25 2024-05-03 台州东仪机械制造有限公司 气缸节能系统

Also Published As

Publication number Publication date
DE59610165D1 (de) 2003-04-03
DE19535677A1 (de) 1997-03-27
ATE233375T1 (de) 2003-03-15
EP0766009B1 (fr) 2003-02-26
KR970016176A (ko) 1997-04-28
TW360755B (en) 1999-06-11
EP0766009A3 (fr) 1999-06-09

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