EP0262098B1 - Système hydraulique de régénération pour des circuits hydrauliques avec pompes et soupapes distributrices à compensation de pression pour les outils d'engins de terrassement - Google Patents

Système hydraulique de régénération pour des circuits hydrauliques avec pompes et soupapes distributrices à compensation de pression pour les outils d'engins de terrassement Download PDF

Info

Publication number
EP0262098B1
EP0262098B1 EP87830015A EP87830015A EP0262098B1 EP 0262098 B1 EP0262098 B1 EP 0262098B1 EP 87830015 A EP87830015 A EP 87830015A EP 87830015 A EP87830015 A EP 87830015A EP 0262098 B1 EP0262098 B1 EP 0262098B1
Authority
EP
European Patent Office
Prior art keywords
pressure
actuator
delivery
discharge
valve
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
EP87830015A
Other languages
German (de)
English (en)
Other versions
EP0262098A1 (fr
Inventor
Piero Tha
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.)
Trinova SpA
Original Assignee
Trinova SpA
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 Trinova SpA filed Critical Trinova SpA
Priority to AT87830015T priority Critical patent/ATE52560T1/de
Publication of EP0262098A1 publication Critical patent/EP0262098A1/fr
Application granted granted Critical
Publication of EP0262098B1 publication Critical patent/EP0262098B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F15B2011/0243—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits the regenerative circuit being activated or deactivated automatically
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single 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
    • F15B2211/30—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
    • F15B2211/50—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
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5156—Pressure control characterised by the connections of the pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/78—Control of multiple 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 present invention relates in general to hydraulic control circuits for the working members of earth-moving machines.
  • the invention relates to a hydraulic control circuit of the type including a pump for supplying a hydraulic fluid under pressure and a plurality of reversible hydraulic actuators, in part linear and in part rotary, for the actuation of respective working members each of which has an associated hydraulic spool valve connected with the delivery and the discharge of the associated working member and positionable, with continuous adjustment, by means of associated control means, into three positions corresponding to displacement of the working member in a first direction, stopping thereof, and displacement in a second direction opposite the first, and pressure compensators of the "load-sensing" type interposed between the said source of supply and the said distributor valves for maintaining the difference between the pressure delivered by the said supply source and the pressure in the working members substantially constant, the said pressure compensators including normally open two-way spool valves each having an end subjected to an opening pressure coming from the associated working member downstream of the associated distributor valve with respect to the delivery flow as well as to the action of a biasing spring, and an opposite end subjected to a closure pressure coming from the
  • the negative load acts on the end of the linear actuator cylinder and the movement is controlled by the discharge flow cross-section ("meter-out") of the associated distributor valve and the flow of fluid is normally all discharged.
  • the end of the cylinder housing the linear actuator rod is connected during the movement to the "load-sensing" pump which therefore sends to this side a flow of fluid proportional to the product of the delivery flow cross-section ("meter-in") of the distributor valve and the square root of the "load-sensing" pressure difference, whilst from the end of the actuator cylinder there is discharged a flow rate proportional to the product of the discharge flow cross-section of the distributor valve and the square root of the load pressure.
  • the object of the present invention is that of obviating the above-mentioned disadvantage, avoiding unnecessary demands for fluid flow from the pump in the said conditions or in similar operating conditions.
  • the subject of the present invention is a hydraulic circuit of the type initially defined, characterised by the fact that at least one of the hydraulic actuators has associated therewith a fluid flow recovery device including at least one recovery line which interconnects the actuator discharge, upstream of the associated distributor valve with respect to the discharge flow, to the delivery of the actuator between the associated compensator and the associated distributor valve, the said fluid flow recovery line including a unidirectional valve operable to allow the passage of fluid only from the discharge towards the delivery of the actuator to obtain an additional closure pressure on the spool of the compensator.
  • the advantage is obtained that, in the case of lowering of a load, the output to the actuator rod end of the actuator cylinder is provided by the flow of fluid leaving the base end which is divided between the discharge cross-section and the delivery cross-section of the distributor. By suitably dimensioning these areas it is possible to avoid the need for an anti-cavitation valve on the rod end of the actuator cylinder.
  • the preceding considerations can be applied to the case in which the operating conditions of the linear actuator are reversed with respect to what has been described above with reference to the lowering of a negative load by the lifting arm of an excavator.
  • the invention permits the unnecessary requirements for output of the "load-sensing" pump towards the base end of the actuator cylinder. In this case, however, it is not in general possible to eliminate the need for an anti-cavitation valve.
  • the invention can provide a double configuration, when necessary, by providing the fluid flow recovery device with two recovery lines in parallel for the purpose of obtaining the above- described effect in both directions of operation of the corresponding linear actuator.
  • the recovery device according to the invention is equally applicable, in a double configuration with two recovery lines, to one or more of the rotary hydraulic actuators.
  • Figure 1 the essential components of a hydraulic control circuit for the working members of an earth-moving machine are illustrated.
  • these working members comprise a series of linear hydraulic actuators 1, 2, 3, 4 serving for the actuation of the excavator arm (raising-penetration-positioning- crowding) and a series of rotary hydraulic motors 5, 6, 7 the first two of which are utilised for the translation manoeuvres of the excavator and the third for the rotation of the excavator arm.
  • the linear actuators 1-4 are gathered in a group, generally indicated 10, separate and distinct from the group, indicated 11, of rotary motors 5-7.
  • Each distributor valve 8, 9 is positionable in three conditions, corresponding respectively to displacement in a first direction of the associated actuator 1-7, stopping thereof, and displacement in a second direction opposite the first.
  • the input-output connections between the distributors 8, 9 and the associated actuators 1-7 are indicated in the drawing with A 1 , B 1 ... A 7 , B 7'
  • the positioning of the spools of the distributors 8, 9 in the three possible positions is obtained thanks to hydraulic control effected from a servo controlled valve unit, not illustrated in the drawing, including a series of control levers and pedals, known per se, which can be manually positioned in different positions corresponding to the said conditions of the distributors 8, 9.
  • the input-output control connections between the servo controls and the distributors 8, 9 are indicated a 1 , b 1 ... a 7 , b 7 .
  • the pump 12 is provided with a "load - sensing" control of type known per se, formed by means of a control circuit 14 by means of which the "load-sensing" pressure signals are derived by taking off signals 15 from the distributors 8 and signals 16 from the distributors 9.
  • compensators 17, 18 Associated with the distributor valves 8, 9 are respective compensators 17, 18 constituted by normally open two-way spool valves inserted in the delivery line 19 of the pump 12 between this latter and the associated distributor valves 8, 9.
  • the compensators 17, 18, which will be returned to below, have, in a manner known per se, the function of maintaining during operation the difference between the pressure delivered by the pump 12 and that in the working members 1-7 substantially constant for the purpose of ensuring the simultaneity of the various possible working movements of the machine independently of the controlled loads.
  • the hydraulic servo control devices are fed by the pump 13 under the control of a maximum pressure valve 20. Associated with this maximum pressure valve is a valve device, generally indicated 21, the function of which is that of preventing the hydraulic circuit from being able to find itself in saturation conditions.
  • the ways in which the depressurisation valve unit 21 can operate are described and illustrated in EP-A-0191275.
  • the rotary hydraulic motors 5, 6 and 7 are associated with braking valve means controlled by the pressure in the delivery duct 19 and prearranged to vary the discharge resistance of the motors in dependence on the pressure existing in the supply duct.
  • These braking valve means are constituted, in a manner known per se from EP-A-0232683 by a single counterbalanced controlled valve 22 inserted in a discharge duct 23 which is common to the three distributors 9 and subjected to the action of a control pressure coming from the pump 13 through a pressure limiting unit, generally indicated 24.
  • This control pressure signal which corresponds to the lowest supply pressure of the rotary actuators 5-7, could alternatively be derived from a selector valve logic system in a manner known from the above-mentioned Patent documents.
  • one or more of the actuators 1-7 can be associated with a fluid flow recovery device operatively cooperating with the corresponding compensators 17, 18 to avoid unnecessary demands for delivery from the pump 12 in certain operating conditions.
  • Figure 2 relates to the application of the fluid-flow recovery device, generally indicated 25, to the linear hydraulic actuator 1 provided for raising and lowering the excavator arm.
  • Figure 2 shows in simplified and diagrammatic form the delivery circuit from the pump 12 and discharge to a reservoir 26 of the linear actuator 1 in the position of the associated distributor valve 8 corresponding to lowering of a load.
  • the distributor valve 8 has been omitted for simplicity and its representation replaced by two schematic representations 8a, 8b of the associated delivery sections ("meter-in” area) and discharge sections ("meter-out” area) respectively through a delivery line 27 and a discharge line 28.
  • the liquid under pressure coming from the pump 12 is supplied to the cylinder 1a of the linear actuator 1 on the side of the rod 1b, whilst the opposite end 1c of the cylinder 1a is connected to the discharge.
  • the compensator 17, which is inserted in the duct 19 between the pump 12 and the distributor valve 8, is constituted by a normally open two- position and two-way spool valve 29 having a side 29a subjected to an opening pressure coming from the linear actuator 1 through a line 30 as well as to the action of a biasing spring 31, and an opposite side 29b subjected to a closure pressure coming from the input of the distributor valve 8 through a line 32.
  • a non-return valve 33 Between the compensator 17 and the distributor valve 8 there is disposed a non-return valve 33.
  • the fluid flow recovery device 25 includes, in the case of Figure 2, a recovery line 34 which interconnects the discharge 28 from the base end 1c of the actuator 1, upstream of the discharge section 8b of the distributor valve 8 with respect to the discharge flow, and the delivery 27 to the rod end 1 of the actuator 1, upstream of the delivery section 8a of the distributor valve with respect to the delivery flow.
  • a unidirectional valve 35 operable to allow the passage of fluid only from the discharge 28 towards the delivery 27 of the actuator 1, and a calibrated throttle 36 for control of the fluid flow.
  • the line 32 is connected upstream of the unidirectional valve 33 with respect to the delivery flow.
  • this line 32 could alternatively be connected downstream of the valve 33, as is illustrated in the variant of Figure 3 in which the same reference numerals as in Figure 2 have been utilised.
  • FIG. 4 shows the application of the flow rate recovery device 25 according to the invention to the case in which the linear actuator 1 is in discharge through the discharge section 8b of the distributor valve 8 from the rod end 1 b and in delivery from the base end 1c through the delivery section 8a of the distributor valve 8.
  • the circuit configuration and the manner of operation are entirely identical to those previously described with reference to Figure 3.
  • the recovery device 25 can have a double configuration, as illustrated in Figure 1 with reference to the linear actuator 2, by utilising two recovery ines 34 in parallel, with respective non-return valves 35 and throttles 36 connected one to the line 27 and the other to the line 28 of the actuator.
  • Figure 5 in which the same reference numerals are used as in the preceding Figures (and in which 9a, 9b indicate respectively the delivery sections and discharge sections of the distributor valve 9), illustrate the application to a rotary motor 5 with a single recover line 34, whilst Figure 1 shows the application of the double configuration to the rotary motor 6 with two recovery lines 34 joined together in parallel.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Flow Control (AREA)

Claims (3)

1. Circuit de commande hydraulique pour organes mobiles d'engins de terrassement comportant une pompe (12) pour fournir un fluide hydraulique sous pression et une pluralité de vérins hydrauliques réversibles (1-7), en partie linéaires et en partie rotatifs, pour l'actionnement d'organes mobiles associés, à chacun desquels est associée une soupape à bobine hydraulique respective (8, 9) reliée à une canalisation d'alimentation (27) et une canalisation d'évacuation (28) des vérins associés (1-7) et pouvant être positionnée par ajustement continu par un moyen de commande associé, à trois positions correspondant au déplacement du vérin dans une première direction, à son arrêt, et à son déplacement dans une deuxième direction opposée à la première, et des compensateurs de pression (17, 18) du type à "détection de charge" interposés entre ladite source d'alimentation (12) et lesdites soupapes distributrices (8, 9) pour maintenir sensiblement constante la différence entre la pression d'alimentation provenant de ladite source d'alimentation (12) et la pression des vérins (1-7), lesdits compensateurs (17, 18) comportant des soupapes à bobine bidirectionnelle, normalement ouvertes (29), ayant chacune un côté (29a) soumis à une pression d'ouverture provenant du vérin associé en aval de la soupape distributrice associée (8, 9) par rapport au débit d'alimentation, ainsi qu'à l'action d'un ressort de rappel (31) et un côté opposé (29b) soumis à une pression de fermeture provenant de l'orifice d'entrée de la soupape distributrice associée (8, 9) caractérisé en ce qu'à au moins l'un des vérins hydrauliques (1-7) est associé un dispositif de régénération du débit (25) comportant au moins une ligne de régénération (34) qui relie l'orifice d'évacuation (28) du vérin (1-7) en aval de la soupape distributrice associée (8, 9) par rapport au débit d'évacuation, à l'orifice d'alimentation (27) du vérin (1-7), entre le compensateur associé (17-18) et la soupape distributrice (8, 9), ladite canalisation de régénération du débit (34) comportant une soupape monodirectionnelle (35) ayant pour fonction de n'autoriser le passage du fluide que de l'orifice d'évacuation (28) vers l'orifice d'alimentation (27) du vérin (1-7), afin d'obtenir une pression de fermeture supplémentaire sur la bobine (29) du compensateur (17, 18).
2. Dispositif selon la revendication 1, caractérisé en ce que la canalisation de régénération (34) comporte outre un étranglement calibré (36).
3. Circuit selon la revendication 1 ou 2, caractérisé en ce que le ou chaque dispositif de régénération du débit (25) comporte deux canalisations de régénération (34) reliées en parallèle.
EP87830015A 1986-09-24 1987-01-19 Système hydraulique de régénération pour des circuits hydrauliques avec pompes et soupapes distributrices à compensation de pression pour les outils d'engins de terrassement Expired - Lifetime EP0262098B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87830015T ATE52560T1 (de) 1986-09-24 1987-01-19 Stroemungsrueckgewinnungssystem fuer hydraulikkreislaeufe mit pumpen und druckkompensierten verteilungsventilen fuer arbeitsglieder von erdbewegungsmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT6773186 1986-09-24
IT67731/86A IT1195178B (it) 1986-09-24 1986-09-24 Sistema di recupero di portata per circuiti idraulici con pompe e di stributori compensati in pressione per organi di lavoro di macchine movimento terra

Publications (2)

Publication Number Publication Date
EP0262098A1 EP0262098A1 (fr) 1988-03-30
EP0262098B1 true EP0262098B1 (fr) 1990-05-09

Family

ID=11304850

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87830015A Expired - Lifetime EP0262098B1 (fr) 1986-09-24 1987-01-19 Système hydraulique de régénération pour des circuits hydrauliques avec pompes et soupapes distributrices à compensation de pression pour les outils d'engins de terrassement

Country Status (7)

Country Link
EP (1) EP0262098B1 (fr)
JP (1) JP2564308B2 (fr)
AT (1) ATE52560T1 (fr)
DE (1) DE3762639D1 (fr)
ES (1) ES2015967B3 (fr)
GR (1) GR3000479T3 (fr)
IT (1) IT1195178B (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1208866B (it) * 1987-04-14 1989-07-10 Chs Vickers Spa Circuito idraulico di comando per organi di lavoro di macchine movimento terra con circuito di sovrali mentazione
AU603907B2 (en) * 1987-06-30 1990-11-29 Hitachi Construction Machinery Co. Ltd. Hydraulic drive system
US4938022A (en) * 1987-10-05 1990-07-03 Hitachi Construction Machinery Co., Ltd. Flow control system for hydraulic motors
DE3844401C2 (de) * 1988-12-30 1994-10-06 Rexroth Mannesmann Gmbh Regeleinrichtung für eine Verstellpumpe
JP2839625B2 (ja) * 1990-03-05 1998-12-16 日立建機株式会社 油圧駆動装置
US5220862A (en) * 1992-05-15 1993-06-22 Caterpillar Inc. Fluid regeneration circuit
JP2992434B2 (ja) * 1993-12-02 1999-12-20 日立建機株式会社 建設機械の油圧制御装置
US5755260A (en) * 1994-09-29 1998-05-26 Samsung Heavy Industries Co., Ltd. Mono-block control valve with regeneration conduit
JP3478931B2 (ja) * 1996-09-20 2003-12-15 新キャタピラー三菱株式会社 油圧回路
GB2344809B (en) * 1998-12-16 2002-10-02 Bamford Excavators Ltd Earth moving apparatus
DE10004905C2 (de) * 2000-02-04 2002-10-24 Orenstein & Koppel Ag Verfahren und Vorrichtung zur Steuerung eines Hubzylinders insbesondere von Arbeitsmaschinen
US7562615B2 (en) 2003-01-14 2009-07-21 Hitachi Construction Machinery Co., Ltd. Hydraulic working machine
JP4209705B2 (ja) * 2003-03-17 2009-01-14 日立建機株式会社 作業機の油圧回路
US20220307527A1 (en) * 2021-03-23 2022-09-29 Cnh Industrial America Llc System to reduce line loss in pressure control hydraulic circuit

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0191275A1 (fr) * 1985-02-14 1986-08-20 TRINOVA S.p.A. Système d'anti-saturation des circuits hydrauliques de commande pour les outils d'engins de terrassement
EP0232683A1 (fr) * 1986-02-04 1987-08-19 TRINOVA S.p.A. Système de contrôle hydraulique pour éléments de travail de machines de terrassement ayant un système centralisé de freinage pour les dispositifs d'entraînement

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1401412A (fr) * 1964-04-23 1965-06-04 Faucheux Ets Dispositif de correction par procédé hydraulique du mouvement d'un organe mécanique, par exemple d'une benne, à l'extrémité d'un bras de levage
US3467126A (en) * 1966-03-21 1969-09-16 Hydranamic Systems Corp Hydraulic load compensating directional control valve
US4364304A (en) * 1976-01-21 1982-12-21 Danfoss A/S Arrangement for influencing the operating quantity of a servomotor
US4216702A (en) * 1978-05-01 1980-08-12 Eaton Yale Ltd. Pressure sensing regenerative hydraulic system
US4383412A (en) * 1979-10-17 1983-05-17 Cross Manufacturing, Inc. Multiple pump load sensing system
DE3245288A1 (de) * 1982-12-03 1984-06-14 O & K Orenstein & Koppel Ag, 1000 Berlin Verfahren zur einsparung von energie beim stellen eines ausruestungszylinders an einem hydraulikbagger durch eine hydraulikschaltung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0191275A1 (fr) * 1985-02-14 1986-08-20 TRINOVA S.p.A. Système d'anti-saturation des circuits hydrauliques de commande pour les outils d'engins de terrassement
EP0232683A1 (fr) * 1986-02-04 1987-08-19 TRINOVA S.p.A. Système de contrôle hydraulique pour éléments de travail de machines de terrassement ayant un système centralisé de freinage pour les dispositifs d'entraînement

Also Published As

Publication number Publication date
IT8667731A0 (it) 1986-09-24
IT1195178B (it) 1988-10-12
EP0262098A1 (fr) 1988-03-30
JPS6383808A (ja) 1988-04-14
JP2564308B2 (ja) 1996-12-18
GR3000479T3 (en) 1991-06-28
ES2015967B3 (es) 1990-09-16
DE3762639D1 (de) 1990-06-13
ATE52560T1 (de) 1990-05-15

Similar Documents

Publication Publication Date Title
EP0262098B1 (fr) Système hydraulique de régénération pour des circuits hydrauliques avec pompes et soupapes distributrices à compensation de pression pour les outils d'engins de terrassement
EP0232683B1 (fr) Système de contrôle hydraulique pour éléments de travail de machines de terrassement ayant un système centralisé de freinage pour les dispositifs d'entraînement
US4030623A (en) Hydraulic circuitry for an excavator
US9206821B2 (en) Hydraulic switching mechanism for mobile hydraulics, mobile hydraulic machine and valve unit
US5490384A (en) Hydraulic flow priority system
US4724673A (en) Power transmission
US5447094A (en) Hydraulic system for bucket self-leveling during raising and lowering of boom
DE112006000783T5 (de) Elektrohydraulisches Lenkungssteuersystem
US4569272A (en) Power transmission
CA2179818A1 (fr) Systeme de regulation par priorite d'ecoulement hydraulique
JP2618680B2 (ja) 土工機械の作業部材を作動させるためのブースター回路を備える液体圧回路
EP0041199A1 (fr) Transmission de la force
EP0191275B1 (fr) Système d'anti-saturation des circuits hydrauliques de commande pour les outils d'engins de terrassement
US5063739A (en) Load sensing hydraulic control system
US3878679A (en) Compensated multi-function hydraulic system
EP3492661B1 (fr) Excavatrice et soupape de commande pour excavatrice
US5680759A (en) Straight travelling apparatus for heavy construction equipment
CN114207225B (zh) 液压控制***
EP2910796B9 (fr) Assemblage avec un dispositif de vanne de commande à position flottante
DE10047631A1 (de) Hydrauliksystem für ein Flurförderzeug
US4770083A (en) Independently actuated pressure relief system
WO2023104331A1 (fr) Système de commande hydraulique pour engin de chantier
FI66466C (fi) Anordning foer att begraensa en hydraulkolvs hastighet i aendlaegena.
DE3901207A1 (de) Ventilanordnung fuer mehrere hydraulische antriebe, insbesondere fuer die antriebe eines krans
JPS61151333A (ja) 建設機械の液圧回路装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE ES FR GB GR IT LI LU NL SE

17P Request for examination filed

Effective date: 19880421

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: TRINOVA S.P.A.

17Q First examination report despatched

Effective date: 19890706

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE ES FR GB GR IT LI LU NL SE

REF Corresponds to:

Ref document number: 52560

Country of ref document: AT

Date of ref document: 19900515

Kind code of ref document: T

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

REF Corresponds to:

Ref document number: 3762639

Country of ref document: DE

Date of ref document: 19900613

ET Fr: translation filed
REG Reference to a national code

Ref country code: GR

Ref legal event code: FG4A

Free format text: 3000479

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19931213

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 19931216

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19931217

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GR

Payment date: 19931223

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19931227

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19940114

Year of fee payment: 8

EPTA Lu: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19940131

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19950119

Ref country code: AT

Effective date: 19950119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19950120

EAL Se: european patent in force in sweden

Ref document number: 87830015.1

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19950131

Ref country code: CH

Effective date: 19950131

Ref country code: BE

Effective date: 19950131

BERE Be: lapsed

Owner name: TRINOVA S.P.A.

Effective date: 19950131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19950731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19950801

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: GR

Ref legal event code: MM2A

Free format text: 3000479

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19950801

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990301

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20030131

Year of fee payment: 17

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040803

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20041210

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20050105

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20050107

Year of fee payment: 19

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060120

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060131

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20060119

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20060929