WO1998048174A1 - Systeme d'entrainement pour verin differentiel hydraulique - Google Patents

Systeme d'entrainement pour verin differentiel hydraulique Download PDF

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Publication number
WO1998048174A1
WO1998048174A1 PCT/EP1998/000348 EP9800348W WO9848174A1 WO 1998048174 A1 WO1998048174 A1 WO 1998048174A1 EP 9800348 W EP9800348 W EP 9800348W WO 9848174 A1 WO9848174 A1 WO 9848174A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive
pumps
cylinder
piston
differential cylinder
Prior art date
Application number
PCT/EP1998/000348
Other languages
German (de)
English (en)
Inventor
Filippo Pastorello
Wolfgang Hahmann
Original Assignee
Hydac Technology 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 Hydac Technology Gmbh filed Critical Hydac Technology Gmbh
Publication of WO1998048174A1 publication Critical patent/WO1998048174A1/fr

Links

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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to a drive for a differential cylinder according to the preamble of claim 1.
  • a drive for such a hydraulic cylinder is known from DE 40 08 792 A1.
  • This drive shows two variable displacement pumps that are driven by a common drive.
  • the first pump is used to convey working fluid from a tank into the enlarging cylinder space of the cylinder.
  • a counter-pressure is built up in this cylinder chamber in the working medium displaced from the other cylinder chamber and the piston is clamped hydraulically.
  • Both cylinder chambers are connected to each other via the second variable pump.
  • a synchronous drive for a hydraulic cylinder is indeed realized with the known drive;
  • the disadvantage of such a drive is that due to the use of variable pumps and the associated control device, the drive has a complicated structure and is expensive to manufacture.
  • Publ.No. 08014208 A is a generic drive for a hydraulic cylinder with two constant pumps having a common drive.
  • the known arrangement together with the valve control device serves to secure hanging loads acting on the working cylinder in such a way that a counterforce is generated in a neutral position, which helps to avoid an unwanted lowering of the load when the device is not actuated. Otherwise, the two constant pumps are used to control and thus extend and retract the piston rod of the hydraulic differential cylinder.
  • a special synchronous drive is not provided here.
  • a drive for a hydraulic differential cylinder is known with two jointly drivable constant pumps, the volumetric flow rate of one constant pump being significantly higher than that of the other in order to be able to provide a constant amount of fluid for actuating the differential cylinder , if this has to make large deflections in the short term, for example to control a mechanical control device in working machines or the like.
  • a synchronous drive for the differential cylinder is also not provided here and this known solution also has a complicated structure and is therefore expensive to manufacture.
  • the invention has for its object to provide a drive for a hydraulic differential cylinder with which a very precise synchronous drive for the differential cylinder can be achieved and which can be produced inexpensively.
  • a relevant object is achieved with the features of claim 1.
  • the constant pumps are arranged in parallel and are preferably connected on one side to the piston chamber of the cylinder via a common line.
  • the two constant pumps are connected to the annulus of the cylinder via a common second line.
  • a spring-loaded check valve is provided between the two constant pumps, which prevents hydraulic fluid from the circuit from entering the circuit to the second constant pump, which sucks additional hydraulic fluid from a tank via a further line to the volume difference between the piston space and
  • the hydraulic fluid that is unnecessary due to the volume difference between the piston space and the annular space is delivered to the tank via the second constant pump.
  • additional hydraulic fluid can be pumped from the tank into the circuit via a further line with a spring-loaded check valve.
  • this line is provided on the piston chamber side and is connected to the tank.
  • pressure lines are provided on the lines that connect the constant pumps to the cylinder, which protect the system from overloading. If the pressure is too high, the system can discharge hydraulic fluid via a line via the corresponding pressure valve. This line preferably conveys the hydraulic fluid delivered back into the tank.
  • cross-connected check valves are provided to hold the position of the piston in the cylinder between the lines connecting the cylinder to the constant pumps.
  • a hydraulically unlockable clamping device can alternatively be provided on the cylinder. This device ensures that the piston can only be extended or retracted when necessary.
  • the arrangement of an additional memory in the system which is connected via directional valves to the lines connecting the cylinder to the constant pumps, is particularly advantageous. In the event of a power failure, movement of the piston, albeit limited, is possible. This storage can either be fed equally by both constant pumps or only by a certain constant pump.
  • the memory is preferably arranged in connection with the pressure valves. These valves take over the functions of feeding and draining liquid in an emergency, as well as overload protection.
  • the regulation of the motor driving the constant pumps via a controller which is regulated as a function of the measured actual values in relation to a predetermined setpoint via an actuating signal, enables an optimal efficiency of the system, since control-related throttle valves are omitted, which saves costs.
  • FIG. 2 shows a representation of a first variant with pressure valves for protection against overload and non-return valves for holding the position of the piston in the differential cylinder
  • Fig. 3 is an illustration of an alternative embodiment of
  • FIG. 2 with a hydraulically unlockable clamping device for holding the differential cylinder
  • FIG. 4 shows a further development of the drive for a differential cylinder from FIG. 2 with an additional memory and directional valves for emergency movements in the event of a power failure
  • FIG. 5 shows a variant of FIG. 4,
  • Fig. 6 is an illustration of a drive for a differential cylinder with a closed system
  • Fig. 7 is an illustration of a drive for a differential cylinder with a controlled drive.
  • 1 shows a differential cylinder 1 with a piston 2.
  • the differential cylinder 1 has a piston chamber 3 and an annular chamber 4.
  • the differential cylinder 1 has the effective piston surface A 3 in the piston space 3 and the effective piston ring surface A 4 in the annular space.
  • the difference between the two surfaces (A 3 - A 4 ) corresponds to the cross-sectional area A St of the piston rod.
  • two constant pumps 5 and 6 are provided, which are driven by means of a motor 7.
  • the two constant pumps 5 and 6 are connected in parallel and connected to the piston chamber 3 and the annular chamber 4 via lines 8 and 9.
  • a spring-loaded check valve 1 3 is provided on the side of the line 8 which is connected to the piston chamber 3, between the constant pump 6 and the line section 11.
  • the system is connected via lines 1 1 and 1 2 to a tank (not shown) in which hydraulic fluid is stored.
  • a spring-loaded check valve 10 is provided on the side of the line 9, which is connected to the annular space 4, between the constant displacement pumps 5 and 6.
  • a spring-loaded check valve 1 3 is provided on the side of the line 8 which is connected to the piston chamber 3, between the constant pump 6 and the line section 11.
  • the two constant pumps 5 and 6 deliver hydraulic fluid via the line 8 into the piston chamber 3. This increases the volume in the piston chamber 3, the piston 2 extends. Simultaneously with the increase in volume of the piston space 3, the volume of the annular space 4 decreases. The hydraulic fluid displaced from the annular space 4 is conveyed into the piston space 3 by the constant pump 5.
  • the constant pumps 5 and 6 move the hydraulic fluid into promote the opposite direction.
  • the constant pump 5 conveys liquid into the annular space 4. Due to the piston movement, the hydraulic fluid is displaced from the piston space 3 and taken up by the constant pumps 5 and 6, the constant pump 6 delivering the hydraulic fluid back to the tank via line 12.
  • a pressure valve 21 is connected to line 8 and a pressure valve 22 is connected to line 9 in order to protect the drive against overload.
  • the hydraulic fluid discharged via the pressure valves 21 and 22 in the event of an overload is supplied to the tank via a line 23.
  • a first embodiment is shown in Fig. 2, in which it is ensured that the piston 2 in the differential cylinder 1 holds its position when necessary.
  • two unlockable check valves 25 and 26 are provided, which can be unlocked crosswise by means of lines 27 and 28 and thus opened.
  • FIG. 1 An alternative embodiment, which also ensures that the position of the piston is held in differential cylinder 1, is shown in FIG.
  • a hydraulically unlockable clamping device 31 is provided on the differential cylinder 1.
  • FIG. 4 essentially corresponds to FIG. 2, but in addition a memory 41 is provided which enables the piston 2 in the differential cylinder 1 to make emergency movements in the event of a power failure.
  • the memory 41 is connected to the constant pumps 5 and 6 via check valves and is charged by the constant pumps 5, 6.
  • the valves 42 and 43 take over both the overload protection of the drive and, in the event of emergency operation, the feeding of hydraulic fluid into the annular space 4 or the piston space 3 and the rear line of displaced hydraulic fluid from the other room into the tank.
  • Figure 5 shows a variant of Figure 4, according to which the memory 41 is fed by a certain constant pump, according to the illustration of Figure 5 by the constant pump 5.
  • Figure 6 corresponds essentially to Figure 4, but this drive is a closed system in which the hydraulic fluid has no contact with the atmosphere.
  • a reservoir 61 is provided which stores the hydraulic fluid.
  • FIG. 7 shows a further development of FIG. 6 according to which the drive is regulated by means of a controller 71 in accordance with a predetermined setpoint, symbolically indicated by the arrow 72.
  • the setpoint is compared with an actual value measured on differential cylinder 1, symbolically indicated by arrow 73.
  • the controller 71 emits an actuating signal according to which the operation of the motor 7 is changed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système d'entraînement pour un vérin différentiel hydraulique (1), comportant deux pompes partageant le même entraînement, ces pompes étant des pompes à cylindrée constante (5, 6). Puisque les cylindrées desdites pompes (5, 6) présentent, par révolution (V6, V5), le même rapport que le rapport de section entre la section de tige de piston (ASt) et la surface de segment de piston (A4) du vérin différentiel (1), le système d'entraînement décrit destiné à un vérin différentiel hydraulique permet un entraînement à vitesse constante très précis de ce vérin et est également économique à produire.
PCT/EP1998/000348 1997-04-17 1998-01-23 Systeme d'entrainement pour verin differentiel hydraulique WO1998048174A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1997116081 DE19716081C1 (de) 1997-04-17 1997-04-17 Antrieb für einen hydraulischen Differentialzylinder
DE19716081.6 1997-04-17

Publications (1)

Publication Number Publication Date
WO1998048174A1 true WO1998048174A1 (fr) 1998-10-29

Family

ID=7826809

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/000348 WO1998048174A1 (fr) 1997-04-17 1998-01-23 Systeme d'entrainement pour verin differentiel hydraulique

Country Status (2)

Country Link
DE (1) DE19716081C1 (fr)
WO (1) WO1998048174A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19857378A1 (de) * 1998-12-12 2000-06-21 Lfk Gmbh Hydraulischer Manipulator
DE10303360A1 (de) * 2003-01-29 2004-08-19 O & K Orenstein & Koppel Gmbh Hydrauliksystem für verdrängergesteuerte Linearantriebe
GB0329243D0 (en) * 2003-12-17 2004-01-21 Thales Plc Apparatus and methods for actuation
US7325398B2 (en) * 2004-03-05 2008-02-05 Deere & Company Closed circuit energy recovery system for a work implement
DE102006045211A1 (de) * 2006-09-25 2008-04-03 Robert Bosch Gmbh Hydrostatisches Getriebe
DE102013212937A1 (de) * 2013-07-03 2014-07-10 Voith Patent Gmbh Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3154921A (en) 1962-01-19 1964-11-03 Caterpillar Tractor Co Fluid pressure system and control
DE2048782A1 (de) * 1969-10-06 1971-04-22 Elektrohydraulische Anlagen An Hydraulikanlage fur eine Maschine mit mehreren hydraulisch angetriebenen Be wegungsvornchtungen
GB2042077A (en) * 1979-01-31 1980-09-17 Johnson Progress Ltd Filter presses
JPS58121306A (ja) * 1982-01-11 1983-07-19 Kobe Steel Ltd 油圧シリンダの伸縮保持用油圧回路
US4630441A (en) * 1984-09-04 1986-12-23 The Boeing Company Electrohydraulic actuator for aircraft control surfaces
EP0314660A1 (fr) * 1987-10-28 1989-05-03 BT Industries Aktiebolag Dispositif de levage hydraulique
DE4008792A1 (de) 1990-03-19 1991-09-26 Rexroth Mannesmann Gmbh Antrieb fuer einen hydraulischen zylinder, insbesondere differentialzylinder
JPH0814208A (ja) 1994-06-29 1996-01-16 Sumitomo Constr Mach Co Ltd ブ−ム伸縮・起伏シリンダの自然縮み防止装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3154921A (en) 1962-01-19 1964-11-03 Caterpillar Tractor Co Fluid pressure system and control
DE2048782A1 (de) * 1969-10-06 1971-04-22 Elektrohydraulische Anlagen An Hydraulikanlage fur eine Maschine mit mehreren hydraulisch angetriebenen Be wegungsvornchtungen
GB2042077A (en) * 1979-01-31 1980-09-17 Johnson Progress Ltd Filter presses
JPS58121306A (ja) * 1982-01-11 1983-07-19 Kobe Steel Ltd 油圧シリンダの伸縮保持用油圧回路
US4630441A (en) * 1984-09-04 1986-12-23 The Boeing Company Electrohydraulic actuator for aircraft control surfaces
EP0314660A1 (fr) * 1987-10-28 1989-05-03 BT Industries Aktiebolag Dispositif de levage hydraulique
DE4008792A1 (de) 1990-03-19 1991-09-26 Rexroth Mannesmann Gmbh Antrieb fuer einen hydraulischen zylinder, insbesondere differentialzylinder
JPH0814208A (ja) 1994-06-29 1996-01-16 Sumitomo Constr Mach Co Ltd ブ−ム伸縮・起伏シリンダの自然縮み防止装置

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 007, no. 227 (M - 248) 7 October 1983 (1983-10-07) *
PATENT ABSTRACTS OF JAPAN vol. 096, no. 005 31 May 1996 (1996-05-31)

Also Published As

Publication number Publication date
DE19716081C1 (de) 1998-08-13

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