EP0229330A2 - Mécanisme pivotant entraîné par deux cylindres séparés à bielle-manivelle - Google Patents

Mécanisme pivotant entraîné par deux cylindres séparés à bielle-manivelle Download PDF

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Publication number
EP0229330A2
EP0229330A2 EP86117269A EP86117269A EP0229330A2 EP 0229330 A2 EP0229330 A2 EP 0229330A2 EP 86117269 A EP86117269 A EP 86117269A EP 86117269 A EP86117269 A EP 86117269A EP 0229330 A2 EP0229330 A2 EP 0229330A2
Authority
EP
European Patent Office
Prior art keywords
swivel
cylinders
cylinder
slewing
pressure
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
EP86117269A
Other languages
German (de)
English (en)
Other versions
EP0229330B1 (fr
EP0229330A3 (en
Inventor
Andreas Dipl.-Ing. Graf
Gert Hartwig
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.)
CESSIONE;MAK SYSTEM GESELLSCHAFT MBH
Original Assignee
Krupp Mak Maschinenbau 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 Krupp Mak Maschinenbau GmbH filed Critical Krupp Mak Maschinenbau GmbH
Publication of EP0229330A2 publication Critical patent/EP0229330A2/fr
Publication of EP0229330A3 publication Critical patent/EP0229330A3/de
Application granted granted Critical
Publication of EP0229330B1 publication Critical patent/EP0229330B1/fr
Expired 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement

Definitions

  • the invention relates to a swivel mechanism with two separate cylinder crank drives as a drive, both swivel cylinders work double-acting and in particular have a piston rod led out on one side to form a differential piston arrangement and a swivel angle less than 360 degrees, as for use in crane and excavator systems , and the dead centers of the cylinder crank drives are arranged offset from one another with respect to the swivel cylinder and the swivel cylinders can be actuated by means of a preferably electro-hydraulic control by a pump via control elements.
  • Swivel mechanisms of this type are able to cover a swivel range of 180 ° and more. For this you need a special design of the geometry and the hydraulic control if you want to ensure increased demands on the uniformity of the swiveling speed under all loads as well as safe entry into the end positions. Swivel mechanisms of this type are known in which the cylinders are only driven from one side when traveling through a swivel direction, for example a cylinder over a certain swivel angle range from the rod space and the other cylinder over another swivel angle range from the floor space. Both areas partially overlap.
  • the control takes place either via a control valve for both cylinders with corresponding black-and-white distributor valves or one control valve per cylinder.
  • the cylinder spaces that are not actively acted upon are generally activated by externally controllable valves, so that they can suck in oil from the oil reservoir or push oil back into this reservoir or exchange the oil between the two cylinder spaces.
  • the suction function can of course also be achieved by a simple check valve between the cylinder and the oil tank.
  • swing mechanism controls also use one of the known load pressure sensing methods, in which the load pressure of each cylinder is fed back to a separate control element, such as a variable displacement pump or pressure compensator, which adjusts the pump pressure so that it is a constant amount higher than the load pressure .
  • a separate control element such as a variable displacement pump or pressure compensator, which adjusts the pump pressure so that it is a constant amount higher than the load pressure .
  • Controls have therefore also been proposed in which a common control element is used for both cylinders, so that both cylinders are supplied with the same system pressure. Such a solution leads to non-uniform swiveling speeds, even if the dead center areas of the cylinders are excluded, as by activation.
  • the object of the invention is to provide a swivel mechanism of the generic type with a simple swivel mechanism control which supplies the swivel cylinders with oil in all operating states sufficiently and enables a uniform swivel movement and ensures that a driving load is tied up at high swivel speeds.
  • the hydraulic supply be carried out according to the load-sensing method, the load pressure being able to be influenced by the load pressures of both swivel cylinders. It is thereby achieved that an active driving through of pivot cylinder dead centers with a corresponding switchover does not lead to the feared load pressure peaks and can therefore be carried out, even if both cylinders remain pressurized up to the dead centers.
  • load-sensing methods are generally known, as is known from DE-OS 34 13 866.
  • Another possibility is that only that of the two floor spaces of the swivel cylinder can be pressurized via control valves, the piston rod of which is extended further, while the other floor space is switched to self-priming or provided with a filling pressure.
  • the swivel cylinders be provided with arrangements for end position damping on their rod side. Furthermore, it is provided that the rod spaces of the swivel cylinders can be acted upon by lowering brake valves, wherein the braking function on the swivel cylinder can be switched on with the respective self-priming floor space.
  • the rapid swiveling behavior under load is positively influenced by the fact that the floor spaces of the swiveling cylinders are provided with throttle check valves for the oil that runs off.
  • each swivel cylinder can be controlled via an associated proportional valve, which has load pressure sensing connections and that the mean value of both sensed load pressures can be fed to the control element as a control variable.
  • the lower of the two sensed load pressures of the swivel cylinder serves as a control variable for the control element, provided that both swivel cylinders are activated. It also has a positive effect that the higher of the two sensed load pressures of the swivel cylinders, reduced to a value proportional to the control of the proportional valve, serves as a control variable for the control element.
  • the two swivel cylinders 1 and 2 shown are fastened on the bottom side to a common pivot point 3 of an abutment 4.
  • Your piston rods 5 and 6 are attached to a swivel platform 8 at points 9 and 10 arranged offset by an angle 7.
  • Both swivel cylinders 1 and 2 are double-acting and can therefore be pressurized with pressure oil from the floor space side as well as from the rod side. They have internal end position dampers 11 on the rod side, which are intended to reduce the swiveling speed when approaching the end stops.
  • the swivel cylinder 1 determines the one end position 8, the swivel cylinder 2 the other end position 8 '.
  • the total pivot angle 12 corresponds to the pivot angles 13 and 14 of the articulation points 9 and 10 of the piston rods 5 and 6. It is therefore greater than 180 °.
  • the bottom dead center of the swivel cylinder 1 is reached when the swivel stage center has reached point 15.
  • the bottom dead center of the pivot cylinder 2 is correspondingly given at point 16 of the pivot stage 8.
  • a transmitter 60 and at dead center 16 a transmitter 61 is fixed to the foundation. Both transmitters 60, 61 are supported by a cam 62 attached to the swivel platform 8 during passage through the respective dead centers 15 or 16 actuated.
  • the corresponding functions are described in connection with the explanation of the circuit diagram according to FIG. 5.
  • the pivot cylinders 1 and 2 are connected to a hydraulic system on the bottom side via lines 17 and 18 and on the rod side on lines 19 and 20 according to the control diagram in FIG. 2.
  • This receives its hydraulic energy from a variable displacement pump 21, which sucks in oil from a tank 22 and supplies two 4/3 proportional valves 25 and 26 via lines 23 and 24. These are controlled by electrical sensors 60, 61, 63.
  • Each proportional valve 25, 26 actuates a swivel cylinder 1, 2. In the middle position, the oil inflows and outflows are blocked.
  • the valves are deflected to the left, the bottom sides of the cylinders 1 and 2 are pressurized with oil via lines 17 and 18 and the rod sides are connected to a return line 27 via lines 19 and 20.
  • Associated 4/2 black and white valves 28 and 29 also enable the pivoting cylinders 1, 2 to be activated.
  • the swivel cylinder 1 is connected to the return line 27 on the base side as well as on the rod side when valve 28 is electrically activated.
  • load pressure sensing lines 30 and 31 determine which load pressure is present on the respective pressure line 17, 18, 19 or 20 on the cylinder side at the proportional valve 25, 26. This is via a pressure change valve 32 and line 33 to the Transfer variable pump 21. This enables them to adjust their flow rate so that it remains approximately constant regardless of the load pressure. This means that the flow rate to the swivel cylinders 1 and 2 is load-independent and is only determined by the control of the proportional valves 25, 26.
  • the pressure change valve 32 has the effect that the higher of the two load pressures present at the valves 25 and 26 acts on the variable displacement pump 21. This would increase up to the maximum pressure of the variable displacement pump 21 - secured by the valve 34 - if both swivel cylinders 1 and 2 reached a dead center at the same time or if only one cylinder was connected to the pressure line 23 or 24 and reached the dead center. In these cases, the volume flow would be braked to zero and the variable displacement pump 21 would be informed of a high load via line 33, which it countered by increasing the delivery rate and maximum pressure increase.
  • the sensed load pressure at the swivel cylinder 1 or at the valve 25 can therefore not increase appreciably beyond the load pressure from the swivel cylinder 2 present at the valve 26, because both valves on the pressure side are connected via lines 23 and 24 to the same pressure source in the form of the variable displacement pump 21.
  • the lowering brake valves 37 and 38 are intended to brake the entry of the swivel cylinders 1, 2 into the rod-side end positions in addition to the internal damping 11. They are unlocked when the bottom sides are depressurized. In this case, the oil on the rod side can only flow out via the restrictors 39 and 40.
  • the throttles 41 and 42 on the floor side serve to limit the swiveling speed under external load when the piston rods 5, 6 are inserted into the swiveling cylinders 1, 2.
  • the throttles 41, 42 are bridged by the check valves 43, 44 when these are released by the pressure that is simultaneously present on the rod sides (lines 19, 20).
  • Lines 46 and 47 indicate the bottom dead centers of cylinders 1 and 2.
  • the rod spaces swiveling cylinder 1 (48) and Swivel cylinder 2 (49) to the dead centers 46 or. 47 pressurized, while the floor spaces pivot cylinder 1 (50) and pivot cylinder 2 (51) are connected to the return line 27.
  • the pivot cylinder 2 is subjected to pressure 51 'on the bottom side and 49' is relieved of the rod space side.
  • the associated lowering brake valve 38 is unlocked by the pressure 51 '.
  • the pivot cylinder 1 remains connected to the pump pressure 48 on the rod side.
  • the oil flow is not interrupted.
  • the rod chamber is depressurized, while the bottom chamber pivot cylinder 2 is still subjected to pressure 51 'and maintains the oil flow from the variable displacement pump 21.
  • the floor space pressure 50 and the rod space pressure 48 'of the swivel cylinder 1 remain activated from the dead center 46 by switching the associated proportional valve 25 to the middle position and the black-and-white valve 28 to the flow position. This relieves the pressure in line 17 and the lowering brake valve 37 switches to the blocking position.
  • the oil running off on the rod side is braked by the throttle 39 (compare 52 in FIG. 3).
  • the swiveling speed decreases and is braked to zero shortly before reaching the end position 8 'by the end position damping 11 additionally acting in the swiveling cylinder 2 (compare 53 in FIG. 3).
  • this measure also reduces the bottom pressure 55 of the pivot cylinder 1 from the high value 55 'to the value 55' ', which is equal to the value 57'.
  • an electrical control of the two proportional valves 25 and 26 for the pivot cylinders 1 and 2 is shown. These are shifted into the positions corresponding to the control slide by a manually operated control slide 63 via control magnets 64 to 67.
  • the electrical energy required for this is supplied by a battery 68.
  • a line 69 is connected to the negative pole
  • a line 70 corresponding to a wiper position 71 on the electrical resistor 72 is connected to part of the positive battery voltage.
  • the actuating magnets 65 and 67 are activated and deflect the valves in proportion to the position of the control slide 63. 2, the bottom sides of both swivel cylinders 1 and 2 are pressurized with pressure oil.
  • the transmitter 60 (see FIG. 1) is actuated and activates the magnet 65 and with it the floor space of the cylinder 1. With further swivel movement, the transmitter 61 is also actuated, so that the bottom space of the cylinder 2 is pressurized.
  • the encoders 60 and 61 can be both digital changeover switches and a rotary angle encoder (analog encoder), the signal of which is dependent on the angle of rotation is processed in a downstream signal processing unit to produce the two required changeover signals for the proportional valves 25, 26.
  • one floor space (cylinder 1) can be relieved via the switch 73 by moving the valve 25 back into the neutral position and the magnet 74 of the valve 28 (FIG. 2) is excited. This connects the cylinder 1 on the floor and rod side to the return 27 and thus unlocks it.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)
EP86117269A 1986-01-14 1986-12-11 Mécanisme pivotant entraîné par deux cylindres séparés à bielle-manivelle Expired EP0229330B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863600816 DE3600816A1 (de) 1986-01-14 1986-01-14 Schwenkwerk mit zwei separaten zylinder-kurbeltrieben als antrieb
DE3600816 1986-01-14

Publications (3)

Publication Number Publication Date
EP0229330A2 true EP0229330A2 (fr) 1987-07-22
EP0229330A3 EP0229330A3 (en) 1987-12-16
EP0229330B1 EP0229330B1 (fr) 1989-11-15

Family

ID=6291798

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86117269A Expired EP0229330B1 (fr) 1986-01-14 1986-12-11 Mécanisme pivotant entraîné par deux cylindres séparés à bielle-manivelle

Country Status (2)

Country Link
EP (1) EP0229330B1 (fr)
DE (2) DE3600816A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4757685A (en) * 1987-08-24 1988-07-19 Caterpillar Inc. Pressure responsive hydraulic control circuit
WO2005011948A1 (fr) * 2003-07-24 2005-02-10 Bbg Gmbh & Co. Kg Outil
US7059126B2 (en) 2003-10-16 2006-06-13 Caterpillar Inc. System for preventing swing wag for a work machine with a boom assembly
CN104140048A (zh) * 2014-08-06 2014-11-12 山东丰汇设备技术有限公司 一种用于塔机的液压驱动回转机构

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19603400A1 (de) * 1996-01-31 1997-08-07 Claas Saulgau Gmbh Landwirtschaftliche Maschine mit in Fahrtrichtung gestaffelt angeordneten Arbeitswerkzeugen

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3630120A (en) * 1970-05-04 1971-12-28 Int Harvester Co Swinging apparatus
DE2443760A1 (de) * 1974-09-13 1976-03-25 Krone Bernhard Gmbh Maschf Steuerung fuer einen zylinderantrieb zur herbeifuehrung einer drehbewegung
FR2304801A1 (fr) * 1975-03-17 1976-10-15 Massey Ferguson Inc Mecanisme de pivotement
FR2453297A1 (fr) * 1979-03-20 1980-10-31 Bouter Andre Mecanisme de renversement controle
US4240327A (en) * 1978-05-30 1980-12-23 Harris Corporation Fluid operated linear actuator control system
DE3413866A1 (de) * 1983-04-13 1984-11-15 Linde Ag, 6200 Wiesbaden Hydrostatisches antriebssystem
DE3508691C1 (de) * 1985-03-12 1986-07-10 Eisenwerke Kaiserslautern Göppner GmbH, 6750 Kaiserslautern Hydraulisches Erdbaufahrzeug mit einem schwenkbaren Ausleger

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3630120A (en) * 1970-05-04 1971-12-28 Int Harvester Co Swinging apparatus
DE2443760A1 (de) * 1974-09-13 1976-03-25 Krone Bernhard Gmbh Maschf Steuerung fuer einen zylinderantrieb zur herbeifuehrung einer drehbewegung
FR2304801A1 (fr) * 1975-03-17 1976-10-15 Massey Ferguson Inc Mecanisme de pivotement
US4240327A (en) * 1978-05-30 1980-12-23 Harris Corporation Fluid operated linear actuator control system
FR2453297A1 (fr) * 1979-03-20 1980-10-31 Bouter Andre Mecanisme de renversement controle
DE3413866A1 (de) * 1983-04-13 1984-11-15 Linde Ag, 6200 Wiesbaden Hydrostatisches antriebssystem
DE3508691C1 (de) * 1985-03-12 1986-07-10 Eisenwerke Kaiserslautern Göppner GmbH, 6750 Kaiserslautern Hydraulisches Erdbaufahrzeug mit einem schwenkbaren Ausleger

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4757685A (en) * 1987-08-24 1988-07-19 Caterpillar Inc. Pressure responsive hydraulic control circuit
WO1989002010A1 (fr) * 1987-08-24 1989-03-09 Caterpillar Inc. Circuit de commande hydraulique sensible a la pression
WO2005011948A1 (fr) * 2003-07-24 2005-02-10 Bbg Gmbh & Co. Kg Outil
US7059126B2 (en) 2003-10-16 2006-06-13 Caterpillar Inc. System for preventing swing wag for a work machine with a boom assembly
CN104140048A (zh) * 2014-08-06 2014-11-12 山东丰汇设备技术有限公司 一种用于塔机的液压驱动回转机构

Also Published As

Publication number Publication date
EP0229330B1 (fr) 1989-11-15
DE3600816A1 (de) 1987-07-16
DE3666970D1 (en) 1989-12-21
EP0229330A3 (en) 1987-12-16

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