EP0327666A1 - Entraînement hydraulique - Google Patents

Entraînement hydraulique Download PDF

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Publication number
EP0327666A1
EP0327666A1 EP88112361A EP88112361A EP0327666A1 EP 0327666 A1 EP0327666 A1 EP 0327666A1 EP 88112361 A EP88112361 A EP 88112361A EP 88112361 A EP88112361 A EP 88112361A EP 0327666 A1 EP0327666 A1 EP 0327666A1
Authority
EP
European Patent Office
Prior art keywords
stroke
hydraulic drive
pressure
piston
working
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.)
Withdrawn
Application number
EP88112361A
Other languages
German (de)
English (en)
Inventor
Josef Nusser
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE3803009A external-priority patent/DE3803009C2/de
Application filed by Individual filed Critical Individual
Publication of EP0327666A1 publication Critical patent/EP0327666A1/fr
Withdrawn legal-status Critical Current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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure 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
    • F15B2211/625—Accumulators
    • 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
    • F15B2211/7055—Linear output members having more than two chambers
    • 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
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention relates to a hydraulic drive for linear movement with a hydraulically driven, stroke-movable, piston-cylinder assignment.
  • Such drives have the purpose of performing lifting movements to overcome a working resistance.
  • hydraulic cylinders which are fed with a flow of flow when the work surface is unchangeable and can only be acted upon at the same time.
  • the volume flow rate is analogous to the stroke, but also the working pressure to the lifting force.
  • the flow rate is subject to very strong pressure fluctuations when the lifting force is applied differently, which have a negative effect on the pump and the drive upstream of the pump.
  • the pump must be designed in such a way that it is able to generate a high pressure and to provide a large volume flow rate for the smooth-running range of the stroke movement to ensure a sufficient stroke speed.
  • This configuration requires in particular because of the high pressure required for the power stroke and the pressure reduction that is essential for the easy-running area, poor efficiency. Attempts have been made to eliminate these disadvantages by means of different flow rates which are generated by several independent pumps. Reversible variable pumps are also used. As a result, the flow volume could be approximated to the demand.
  • the stroke movement in the low-speed range is to be carried out as a rapid stroke with a low flow rate requirement, in order to then be continued in the power stroke in the case of greater working resistance by means of lifting force amplification.
  • Several hydraulic drives should be powered by just one pump and load peaks on the drive side should be avoided.
  • the multi-stage piston-cylinder design forms separate pressure spaces with the resulting partial work surfaces of different sizes and the work surface can be partially or completely acted upon by the working pressure of the flow and at the start of the preliminary stroke
  • the pressure chamber with the smallest assigned work surface is initially fed with flow and during the work stroke to overcome a greater working resistance, in addition until the intended stroke length is reached, the pressure chamber with the next larger work surface can be fed with flow in succession.
  • a multiple piston consists of the inner piston with a circular cross section and one or more annular pistons concentrically surrounding the inner piston with an annular working surface and is displaceable relative to the multiple cylinder adapted to it, thereby forming separate pressure chambers and separately pressurizable working surfaces the working pressure of the flow rate can be partially or completely applied to this working area and, at the beginning of the preliminary stroke, the pressure space with the smallest assigned working area is initially fed with flow rate and during the working stroke to overcome a greater working resistance, additionally until the intended stroke length is reached , the pressure chamber with the next larger work surface is fed with flow in succession.
  • the delivery flow can be switched into the pressure chambers as a function of force and / or path.
  • the rapid, error-free supply of the pressure chambers is ensured by the fact that the delivery flow is automatically switched into the pressure rooms to be supplied with delivery flow one after the other, and a counterpressure level in an already supplied pressure room is effective as a signal for the connection of the pressure room to be subsequently fed with delivery flow, whereby short switching distances and a direct switching process are given, in that the signal pressure acts as switching force for the switching process.
  • the pressure chambers are constantly filled with fluid and can be fed from the storage container or emptied into the same, depending on the direction of movement of the piston, until a pressure chamber concerned is supplied with flow and the flow between this pressure chamber and the reservoir is interrupted.
  • the smoothness of the return stroke of the piston is given by unlocking the check valves swipe the pressure chambers and the reservoir, so that the fluid can escape from the pressure chambers in the reservoir.
  • the return stroke is very safe and precise because the piston is double-acting.
  • a very reliable and compact design is achieved in that the signal and / or control elements are fully or partially integrated in the cylinder. Exact positioning of the end position is often necessary, largely without the need for end position damping.A low piston speed should be achieved shortly before the end of the stroke, in that one or more pressure chambers with a larger work surface are fed with flow, regardless of the required lifting force.
  • the stepped piston is double-acting and formed by the piston rod 1 and the piston steps 6, 7, 8 and arranged in the adapted double-acting stepped cylinder 2 in a stroke-movable manner.
  • a plurality of separate pressure spaces 3, 4, 5 and work surfaces 22 of different sizes and for the return stroke of the pressure space 9 are formed.
  • the delivery flow generated by the pump 10 is fed into the pressure chamber 3 via the 4/2 way valve 11 through a corresponding switching position via the feed line 12.
  • By closing the check valve 13 a pressure is created in the pressure chamber 3 which, because of the comparatively small working surface 22 and a low flow volume, moves the stepped piston to the front at high speed.
  • the filling flow flows through the check valves 18, 20 into the increasing pressure Rooms 4, 5 and the contents of the pressure chamber 9 can be emptied into the pressure accumulator 14 or the tank 15 via the valve 11.
  • the connecting valve 16 opens and the delivery flow can feed the pressure chamber 4 via the line 17.
  • the pressure in the pressure chamber 4 increases, so that the check valve 18 closes and the lifting force increases.
  • the connecting valve 19 opens and the flow can also feed the pressure chamber 5 and the check valve 20 closes. In this switch position, the stepped piston can deliver its greatest lifting force.
  • the flow into the pressure chambers 3, 4, 5 is interrupted and can be conducted into the pressure chamber 9.
  • the check valves 13, 18, 20 are relaxed.
  • the stepped piston travels back stroke and the pressure chambers 3, 4, 5 are emptied via the lines 23 into the tank 21 or to maintain a low preload pressure in the pressure accumulator 24 and, if the preload pressure is exceeded, only partially into the tank 21 via the pressure relief valve 25
  • the pressure of the filling stream held by the pressure accumulator 24 ensures that the pressure spaces 3, 4, 5 are always filled with the filling stream without bubbles, even during the filling process.
  • the cylinder cover 26 can be attached so that the pressure chamber 27 is formed and connected to the line 23 via the line 28 and the check valve 29.
  • the contents of the pressure chamber 27 can escape into the line 23 until, at the desired stopping point, the flow supply to the pressure chambers 3, 4, 5 is interrupted and the check valve 29 is closed.
  • the double piston 29 shown in FIG. 3 consists of the inner piston 30 with a circular cross section and the ring piston 31 surrounding the inner piston 30 and the adapted cylinder 32.
  • the inner piston 30 and the outer ring piston 31 have different working surfaces 22 and form with them the assigned pressure chambers 3, 4.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP88112361A 1988-02-02 1988-07-29 Entraînement hydraulique Withdrawn EP0327666A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE3803009A DE3803009C2 (de) 1987-02-04 1988-02-02 Hydraulischer Antrieb

Publications (1)

Publication Number Publication Date
EP0327666A1 true EP0327666A1 (fr) 1989-08-16

Family

ID=6346439

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88112361A Withdrawn EP0327666A1 (fr) 1988-02-02 1988-07-29 Entraînement hydraulique

Country Status (1)

Country Link
EP (1) EP0327666A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0499826A1 (fr) * 1991-02-16 1992-08-26 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Dispositif de commande pour appareil de démolition
EP0711927A3 (fr) * 1994-10-11 1997-03-26 Pneumatic Energy Inc Multiplicateur de pression pneumatique
WO1997020146A1 (fr) * 1995-11-24 1997-06-05 Mannesmann Rexroth Gmbh Procede et dispositif pour piloter le systeme hydraulique d'une machine
US5784943A (en) * 1996-03-15 1998-07-28 Tamrock Oy Arrangement in a hydraulic cylinder
AT510542A1 (de) * 2010-10-29 2012-05-15 Metso Paper Inc Druckspeicherfüllverfahren für ein fluidsystem
FR3044368A1 (fr) * 2015-12-01 2017-06-02 Peugeot Citroen Automobiles Sa Dispositif de controle d’un organe a controler par deux cylindres concentriques et independants
CN108679008A (zh) * 2018-07-19 2018-10-19 江苏师范大学 一种可改变增压比的连续输出增压器及控制方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191221945A (en) * 1912-09-26 1913-07-31 George Homeyard Improved Arrangements for Controlling the Pressure Water of Hydraulic Machines.

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191221945A (en) * 1912-09-26 1913-07-31 George Homeyard Improved Arrangements for Controlling the Pressure Water of Hydraulic Machines.

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0499826A1 (fr) * 1991-02-16 1992-08-26 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Dispositif de commande pour appareil de démolition
US5199658A (en) * 1991-02-16 1993-04-06 Krupp Maschinentechnik Gesellschaft Mit Beschrankter Haftung Dual-force hydraulic drive for a demolition tool
EP0711927A3 (fr) * 1994-10-11 1997-03-26 Pneumatic Energy Inc Multiplicateur de pression pneumatique
WO1997020146A1 (fr) * 1995-11-24 1997-06-05 Mannesmann Rexroth Gmbh Procede et dispositif pour piloter le systeme hydraulique d'une machine
US6145307A (en) * 1995-11-24 2000-11-14 Mannesman Rexoth Ag Method and device for controlling a hydraulic installation of a utility vehicle
US5784943A (en) * 1996-03-15 1998-07-28 Tamrock Oy Arrangement in a hydraulic cylinder
AT510542A1 (de) * 2010-10-29 2012-05-15 Metso Paper Inc Druckspeicherfüllverfahren für ein fluidsystem
AT510542B1 (de) * 2010-10-29 2013-04-15 Metso Paper Inc Druckspeicherfüllverfahren für ein fluidsystem
FR3044368A1 (fr) * 2015-12-01 2017-06-02 Peugeot Citroen Automobiles Sa Dispositif de controle d’un organe a controler par deux cylindres concentriques et independants
CN108679008A (zh) * 2018-07-19 2018-10-19 江苏师范大学 一种可改变增压比的连续输出增压器及控制方法
CN108679008B (zh) * 2018-07-19 2020-06-16 江苏师范大学 一种可改变增压比的连续输出增压器及控制方法

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