EP1580437A1 - Vérin hydraulique pour outil hydraulique - Google Patents

Vérin hydraulique pour outil hydraulique Download PDF

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Publication number
EP1580437A1
EP1580437A1 EP05075591A EP05075591A EP1580437A1 EP 1580437 A1 EP1580437 A1 EP 1580437A1 EP 05075591 A EP05075591 A EP 05075591A EP 05075591 A EP05075591 A EP 05075591A EP 1580437 A1 EP1580437 A1 EP 1580437A1
Authority
EP
European Patent Office
Prior art keywords
piston rod
cylinder
pressure
piston
cylinder chamber
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
EP05075591A
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German (de)
English (en)
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EP1580437B1 (fr
Inventor
Gertrudis Maria Gerardus De Gier
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.)
Demolition and Recycling Equipment BV
Original Assignee
Demolition and Recycling Equipment BV
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Priority to PL05075591T priority Critical patent/PL1580437T3/pl
Publication of EP1580437A1 publication Critical patent/EP1580437A1/fr
Application granted granted Critical
Publication of EP1580437B1 publication Critical patent/EP1580437B1/fr
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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
    • F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/965—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements of metal-cutting or concrete-crushing implements
    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1466—Hollow piston sliding over a stationary rod inside the cylinder
    • 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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
    • 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
    • F15B2211/3052—Shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—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
    • F15B2211/60—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7055—Linear output members having more than two chambers

Definitions

  • the invention relates to a hydraulic cylinder, for example for use in a hydraulic tool, comprising a hollow cylinder body accommodating a first piston, which first piston is composed of a hollow first piston rod, which extends from the cylinder body, and a first piston body connected thereto, said cylinder body and said first piston body defining a first cylinder chamber and said cylinder body, said first piston body and said first piston rod defining a second cylinder chamber, as well as a second piston accommodated in the hollow first piston rod, which second piston is composed of a second piston rod, which extends through the first piston body and which is connected to the cylinder body, and a second piston body connected thereto, said first piston rod and said second piston body defining a third cylinder chamber and said first piston rod, said second piston rod and said second piston body defining a fourth cylinder chamber, wherein second piston rod is at least provided with a bore that terminates in the third cylinder chamber, and wherein the cylinder chambers can be connected to a first and a second supply line, respectively, for
  • a hydraulic tool that is operated by means of a hydraulic cylinder as described above is known, for example from European patent No. 0 641 618 B1.
  • Said patent discloses a frame that can be coupled to a jib of an excavating machine or the like, to which frame an assembly of two jaws can be coupled. One of the jaws can be pivoted with respect to the other jaw by means of a hydraulic setting cylinder.
  • a setting cylinder of such a tool is controlled or energized by the hydraulics of the machine in question, whose construction more or less determines the available operating pressure of the fluid as well as the flow of the fluid to be supplied.
  • a large bore diameter of the cylinder body enables high cylinder forces, to be true, but it requires high fluid flows through the hydraulic circuit, which in turn leads to unnecessarily long cycle times.
  • a hydraulic cylinder as referred to in the introduction is known from, for example, German patent publication No. 1,021,612.
  • the current setting cylinders are characterized by low cycle times, low return fluid flows and high cylinder forces only during the outward stroke of the piston rod; the known cylinders in particular lack high cylinder forces during the inward stroke, however.
  • the cylinder is to that end characterized in that at least one pressure control valve is provided, which controls the supply of pressurised fluid to the various cylinder chambers in dependence on the pressure difference between the first supply line and the second supply line.
  • the cylinder according to the invention provides a very functional cylinder chamber, thus making it possible to place the various cylinder chambers in communication with the supply lines for pressurised fluid in dependence on the operating conditions.
  • the pressure control valve controls a pressure-controlled valve on the basis of the pressure difference between the first supply line and the second supply line, in such a manner that when the pressure caused by the load resistance during the outward/inward stroke of the first piston rod is lower than the predetermined pressure level, the pressure-controlled valve will take up a first/second extreme position, and when the pressure caused by the load resistance is higher than the predetermined pressure level, the pressure-controlled valve will take up a central position.
  • the pressure-controlled valve in the central position thereof, places the first and the third cylinder chamber into communication with the first supply line and the third and the fourth cylinder chamber with the second supply line, whilst in the first and the second extreme position the first, second, third and fourth cylinder chambers can be placed into communication with the first and/or the second supply line.
  • the pressure-controlled valve In its first extreme position, the pressure-controlled valve can place the second, third and fourth cylinder chamber into communication with the second supply line, whilst in its second extreme position the pressure-controlled valve places the third cylinder chamber and at least the second cylinder chamber into communication with the second supply line.
  • the pressure-controlled valve places the fourth cylinder chamber into communication with the second supply line in the second extreme position thereof.
  • the second cylinder chamber and the fourth cylinder chamber are in communication with each other; in a first embodiment, said second cylinder chamber and said fourth cylinder chamber are in communication with each other via at least one opening formed in the first piston rod.
  • the second piston rod is provided with a further bore that terminates in the fourth cylinder chamber, which further bore connects the fourth cylinder chamber to a fourth supply line for the pressurised fluid.
  • the second and the third cylinder chamber are each in communication with a storage vessel for the fluid via a non-return valve.
  • the non-return valve for the third cylinder chamber may be a pressure-controlled non-return valve, in particular a non-return valve that is controlled by the pressure control valve.
  • the stored fluid is delivered to the hydraulic circuit again during the outward stroke of the piston rod. This results in a further reduction of the pump losses, resistance losses, etc.
  • Figs. 1a and 1b are two views of a hydraulic tool that is driven or energized by a hydraulic setting cylinder.
  • the illustrated prior art tool comprises a frame 1 including a first frame part 2, which frame part 2 is coupled to a second frame part 3 by means of a turntable 2'.
  • the two frame parts 2 and 3 are rotatable with respect to each other by means not shown, for example hydraulically operated setting means, which are known per se.
  • the frame part 2 is fitted with coupling means 4, 4' that are known per se, by which the device 1 can be coupled to the end of an arm of an excavator or a similar earthmoving machine, for example.
  • a first jaw 12 is connected to the frame part 3 of the frame 1 by means of a pivot pin 10 and a pin 11.
  • the two pins 10 and 11 are accommodated in corresponding openings or bores (not shown) formed in the frame part 3.
  • a second movable jaw 13 can be pivoted about the pivot pin 10.
  • the second movable jaw 13 is pivotable with respect to the first jaw 12 by the setting cylinder 8, to which purpose the end 14a of a piston rod 14 of the setting cylinder 8 is coupled to one end of the pivotable jaw 13 by means of a pin 15.
  • the setting cylinder 8 is pivoted in the frame part 3 about pivot point 9 so as to enable outward movement of the piston rod 14.
  • Fig. 1a shows the hydraulic tool in the operating situation in which the piston rod 14 is fully retracted (inward stroke), whilst Fig. 1b shows the outward stroke of the piston rod 14, by which the jaw 13 has been moved into contact with the jaw 12.
  • Such a hydraulic tool can be used for carrying out demolition, crushing or cutting operations, during which operations large cylinder forces can be transmitted to the jaws 12 and 13.
  • hydraulic demolition tools such as scrap cutters and the like
  • iron occasionally gets wedged between the jaws 12 and 13 (in particular between the cutting edges 16, 16' and 17), which iron will not come loose unless large cylinder forces are exerted during the inward stroke of the piston rod 14.
  • a hydraulic setting cylinder 14 which is characterized by high piston rod speeds and consequently short cycle times, low return fluid flows and high cylinder forces not only during the outward stroke of the piston rod 14, but which is capable of generating highest cylinder forces also during the inward stroke (from the position that is shown in Fig. 1b to the position that is shown in Fig. 1a).
  • Figs. 2a-2d show various operating situations of a basic embodiment of such a hydraulic setting cylinder according to the invention.
  • the hydraulic setting cylinder comprises a hollow cylinder body 8 accommodating a first piston, which piston is composed of a hollow first piston rod 14 extending from the cylinder body 8 and a first piston body 20 that is connected thereto.
  • the external dimension of the first piston body 20 corresponds to the internal dimension of the hollow cylinder body 8.
  • the hollow cylinder body 8 and the first piston body 20 define a first cylinder chamber 21, whilst the hollow cylinder body 8, the first piston rod 14 and the first piston body 20 define a second cylinder chamber 22 that surrounds the first piston rod 14.
  • the end 14a of the first piston rod 14 is to be connected by means of a pin 15 to, for example, the pivotable jaw 13 of the cutting and/or crushing tool that is shown in Figs. 1a and 1b.
  • a second piston Accommodated in the hollow first piston rod 14 is a second piston composed of a second piston rod, which extends through the first piston body 20 and which is connected to the hollow cylinder body 8, and a second piston body 25 connected thereto.
  • the external dimension of the second piston body 25 corresponds to the internal dimension of the hollow first piston rod 14.
  • the hydraulic circuit is partially built up of a pressure-controlled valve 31, which is provided with a first supply line P1, which can be placed into communication with the first cylinder chamber 21.
  • a pressurized fluid e.g. oil
  • the piston rod 14 will extend (the outward stroke) under the influence of the pressure increase in the cylinder chamber 21.
  • a flange B1 is provided in the cylinder body 8, to which the first supply line P1 can be connected.
  • the second cylinder chamber 22 is provided with a connecting flange S1, which connecting flange can be connected inter alia to the second supply line P2 via a supply line and the pressure-controlled valve 31.
  • the second supply line P2 in particular functions to supply pressurised fluid for retracting the first piston rod 14 (inward stroke).
  • the second piston rod 26 is provided with a first through bore 27, which connects the third cylinder chamber 23 to a connecting flange B2, which is in turn connected to the pressure-controlled valve 31 via a fluid line.
  • the second piston rod 26 is furthermore optionally provided with a second through bore 40, which connects the fourth cylinder chamber 23 to a connecting flange S2, which is in turn connected to the pressure-controlled valve 31 via a fluid line.
  • the pressure-controlled valve 31 can take up three positions, viz. a first extreme position X (as shown in Fig. 2a), a central position (as shown in Figs. 2b and 2d) and a second extreme position Y (as shown in Fig. 2 c).
  • the pressure-controlled valve 31 is controlled by a pressure control valve 30, which is in turn controlled by a ball valve 32.
  • Fig. 2a shows an operating situation of a basic embodiment of the hydraulic cylinder according to the invention, in which an outward stroke is imposed on the piston rod 14 by the hydraulic circuit and in which the piston rod 14 encounters a load resistance (via the first and second jaws 12, 13 (not shown)), which load resistance generates a pressure in the hydraulic circuit which is lower than a predetermined pressure level.
  • the pressure control valve 30 and the pressure-controlled valve 31 are switched so that the outward stroke of the first piston rod 14 takes place at a high speed.
  • pressurised fluid is supplied via the first supply line P1, which fluid places the pressure-controlled valve 31 in its first extreme position X as shown in Fig. 2a via the pressure control valve 30.
  • the pressurised fluid is led to the various connecting flanges B1-B2-S1-S2, and consequently to the cylinder chambers 21-22-23-24, via the supply line P1 in dependence on the configuration of the valve position X.
  • the configuration of the first extreme valve position X results in a particular cylinder behaviour during the outward stroke.
  • the fluid pressure in the supply line P1 can set the pressure control valve 30 to its other position.
  • This causes the pressure-controlled valve 31 to take up its central position, as shown in Fig. 2b.
  • the valve configuration of the pressure-controlled valve 31 int the central position thereof is such that the first and the third cylinder chamber 21, 23, respectively, are jointly connected to the first supply line P1 via the connecting flanges B1 and B2.
  • Both the third and the first cylinder chamber 23, 21, respectively, are thus fed with the pressurised fluid that is being supplied from the main supply line P1.
  • the second and the fourth cylinder chamber 22, 24, are in communication with the second supply line P2 via the connecting flanges S1 and S2, respectively.
  • the second and the fourth cylinder chamber 22, 24 are pressureless and the fluid that is present in said chambers is forced out of the cylinder body 8 in the direction of the supply line P2 during the outward stroke of the piston rod 14.
  • the first and the third cylinder chamber 21, 23 are pressurised via the fluid that is supplied through the main supply line P1.
  • the setting cylinder 8 is capable of exerting large forces on a hydraulic tool, for example the crushing and cutting tool of Figs. 1a and 1b, via the piston rod 14.
  • Figs. 2c and 2d show two operating situations of the basic embodiment of the hydraulic cylinder according to the invention during the inward stroke of the piston rod 14.
  • the second supply line P2 is in principle used for supplying pressurised fluid.
  • the pressure created in the hydraulic circuit as a result of the load resistance experienced by the piston rod 14 is lower than a predetermined pressure.
  • the pressure control valve 30 and the ball valve 32 are switched so that the pressurised fluid supplied via the second supply line P2 sets the pressure-controlled valve 31 to its second extreme position Y.
  • the supply of pressurized fluid via the supply line P2 to the cylinder chambers 21-22-23-24 is determined by the valve configuration in the extreme position Y.
  • the piston rod 14 is preferably capable of transmitting large forces during the inward stroke as well, so as to move the jaws 12 and 13 apart.
  • FIG. 2d This operating situation is shown in Fig. 2d, in which situation the piston rod 14 experiences such a high load resistance that the pressure that is thus generated in the hydraulic circuit exceeds a predetermined pressure as set by the pressure control valve 30.
  • the increased fluid pressure in the second supply line P2 caused by the increased load resistance switches over the ball valve 32, and consequently also the pressure control valve 30.
  • the pressure-controlled valve 31 takes up its central position (Fig. 2d), thus connecting the second and the fourth cylinder chamber 22, 24 to the second supply line P2 via the connecting flanges S1 and S2, respectively.
  • the first and the third cylinder chamber 21, 23, which are likewise in communication with each other, are pressureless and the fluid that is present in said chambers is forced out of the cylinder body 8 in the direction of the first supply line P1 during the inward stroke of the piston rod 14.
  • Fig. 3 shows various possible configurations of the pressure-controlled valve 31, in which the four cylinder chambers 21-22-23-24 (B1-B2-S1-S2) can be placed into communication with the first and the second supply line P1, P2 in various ways both during the outward stroke (position X) and during the inward stroke (position Y) of the piston rod 14.
  • the valve 31 is in position X when the piston rod 14 moves out quickly and takes up its central position when the cylinder is to deliver the maximum force.
  • the valve 31 is in position Y when the piston rod 14 moves in quickly and takes up its central position again when the maximum force is to be delivered.
  • Possibilities X1 and Y1 are the same as the configuration of the valve 31 in the central position, i.e. in fact the valve does not switch.
  • valve configurations X1-X10 are so arranged that configuration X1 means the lowest speed of the cylinder 8 and the largest return fluid flow from the cylinder chambers. From configuration X1 to X10 the cylinder speed becomes higher and higher and the return fluid flow becomes lower and lower. With valve configuration X6 (first extreme position) the return fluid flow even equals zero, and with configurations X7-X10 the return fluid flow even becomes negative, i.e. fluid (water, oil, etc) needs to be sucked in.
  • Configurations Y1-Y5 are associated with the second extreme position Y. From Y1 to Y5, the speed of the inward stroke of the piston becomes higher and higher and consequently the return fluid flow becomes lower and lower.
  • Figs. 4a-4d show operating situations of an embodiment of a hydraulic cylinder according to the invention in which the valve configuration of the pressure-controlled valve 31 in the first extreme position X thereof is the configuration that is indicated X6 in Fig. 3 and the valve configuration of the pressure-controlled valve 31 in the second extreme position Y thereof is the configuration that is indicated Y3 in Fig. 3.
  • Fig. 4a shows the operating situation of the hydraulic cylinder according to the invention, in which an outward stroke is imposed on the piston rod 14 by the hydraulic circuit and in which the piston rod 14 experiences a load resistance (via the first and the second jaw 12, 13 (not shown)), which load resistance generates a pressure in the hydraulic circuit which is lower than a predetermined pressure level.
  • the pressure control valve 30 and the pressure-controlled valve 31 are switched so that the outward stroke of the first piston rod 14 takes place at a high speed.
  • pressurised fluid is supplied via the first supply line P1, which fluid is branched off via the pressure control valve 30, thus setting the pressure-controlled valve 31 to its first extreme position as shown in Fig. 4a.
  • the pressurised fluid is directly introduced into the first cylinder chamber 21 via the first supply line P1 and the connecting flange B1.
  • pressurised fluid is passed on via the first valve supply line 33a and the pressure-controlled valve 31 to the first and the second valve discharge line 34a, 34b, which connect to the connecting flanges B2 of the bore 27 and the third cylinder chamber 23 and the connecting flange S of the second cylinder chamber 22 , respectively.
  • the piston rod 14 is provided with one or more openings 28, via which the second cylinder chamber 22 is in fluid communication with the fourth cylinder chamber 24.
  • the fluid that is supplied under pressure via the second valve discharge line 34b is introduced both into the second cylinder chamber 22 and into the fourth cylinder chamber 24 via the connecting flange S.
  • the fluid pressure in the supply line P1 can set the pressure control valve 30 to its other position.
  • This causes the pressure-controlled valve 31 to take up its central position, as a result of which the third cylinder chamber 23 is connected to the first valve supply line 33a and the first supply line P1 via the bore 27, the connecting flange B2 and the first valve discharge line 34a.
  • Both the third cylinder chamber 23 and the first cylinder chamber 21 are thus fed with the pressurized fluid that is supplied from the main supply line P1.
  • the second cylinder chamber 22 and the fourth cylinder chamber 24 are in communication with the second valve supply line 33b and the second supply line P2 via the connecting flange S and the second valve discharge line 34b.
  • the second and the fourth cylinder chamber 22, 24 are pressureless and the fluid that is present in said chambers is forced out of the cylinder body 8 in the direction of the supply line P2 as indicated by the arrow during the outward stroke of the piston rod 14.
  • the first and the third cylinder chamber are furthermore pressurised via the fluid that is supplied by the main supply line P1.
  • the setting cylinder 8 is capable of exerting large forces on a hydraulic tool, for example the crushing and cutting tool from Figs. 1a and 1b, via the piston rod 14.
  • Figs. 4c and 4d show two operating situations during the inward stroke of the piston rod 14.
  • the second supply line P2 is in principle utilised for supplying pressurised fluid.
  • the pressure created in the hydraulic circuit as a result of the load resistance experienced by the piston rod 14 is lower than a predetermined pressure.
  • the pressure control valve 30 and the ball valve 32 are switched in such a manner that the pressurised fluid supplied via the second supply line P2 sets the pressure-controlled valve 31 to a second extreme position.
  • the pressurised fluid that is supplied by the pressure-controlled valve 31 via the second valve supply line 33b is led to the connecting flanges B2 and S of the third and the second (and fourth) cylinder chambers 23-22 and 24, respectively, via the first and the second valve discharge line 34a, 34b.
  • the first cylinder chamber 21 is pressureless and the fluid that is present in the first cylinder chamber 21 is returned to the hydraulic circuit via the first supply line P1.
  • the piston rod 14 must preferably be capable of exerting large forces also during the inward stroke for moving the two jaws 12 and 13 apart.
  • FIG. 4d This operating situation is shown in Fig. 4d, in which the piston rod 14 experiences such a high load resistance that the pressure thus generated in the hydraulic circuit exceeds a predetermined pressure as set by the pressure control valve 30.
  • the increased fluid pressure in the second supply line P2 as a result of the increased load resistance switches over the ball valve 32, and consequently also the pressure control valve 30.
  • the first and the third cylinder chamber 21, 23 are pressureless, and the fluid that is present in said chambers is forced out of the cylinder body 8 during the inward stroke of the piston rod 14 in the direction of the first supply line P1.
  • a double cylinder action is realised in this manner, which enables the setting cylinder 8 to realise rapid movements of the piston rod 14 during operation (both during the inward stroke and during the outward stroke) but also to generate large cylinder forces both during the inward stroke and in during the outward stroke when the pressure on the setting cylinder 8 that is generated by the load resistance exceeds a predetermined pressure level in the hydraulic circuit.
  • the setting cylinder as described herein is in principle characterized by short cycle times and high speeds of movement of the piston rod 14 both during the inward stroke and during the outward stroke.
  • the return fluid that is forced from the setting cylinder 8 is temporarily stored near the setting cylinder 8 both during the inward stroke and during the outward stroke and can be directly introduced into the hydraulic circuit again when additional fluid is needed during the outward stroke of the piston rod 14.
  • the storage vessel 35 is used for collecting return fluid from the third, the second and the fourth cylinder chamber 23, 22 and 24, respectively, with the connection B2 of the third cylinder chamber 23 to the storage vessel 35 and the connection of the second and the fourth cylinder chamber (connection S) to the storage vessel 35 being closed by ball valves 37 and 36, respectively.
  • the ball valve 37 in the fluid line between the storage vessel 35 and the third cylinder chamber 23 is configured as a pressure-controlled one-way valve (non-return valve), which non-return valve 37 is controlled by the pressure of the fluid in the second supply line P2.
  • the fluid stored in the storage vessel 35 is delivered to the circuit again via the non-return valves 36 and 37, in such a manner that said delivered fluid imparts an additional impulse to said outward stroke and that the storage vessel 35 is completely emptied for the next cycle.
  • the non-return valves 37 is controlled by the pressure control valve 30.
  • the first cylinder chamber 21 (B1) (instead of the third cylinder chamber 23) and the second cylinder chamber 22 (S1) may be connected to the storage vessel 35 via the non-return valves 36-37.
  • the third cylinder chamber 23 (B2) and the fourth cylinder chamber 24 (S2) are connected to the pressure-controlled valve 31 via their separate fluid lines B2 and S2 in that case.
  • the ball valve 37 present in the fluid line between the storage vessel 35 and the first cylinder chamber 21 is configured as a pressure-controlled one-way valve (non-return valve).
  • the non-return valve 37 can be controlled by the pressure of the fluid in the second supply line P2 and by the pressure control valve 30.
  • Characteristic of the setting cylinder 8 described herein, which is provided with four active cylinder chambers 21-24, is the fact that high speeds of movement and thus short cycle times of the piston rod 14 are realised both during the inward stroke and during the outward stroke, and that the piston rod 14 is capable of generating very large cylinder forces both during the inward stroke and during the outward stroke in dependence on the load resistance it experiences.
  • the setting cylinder 8 is characterized by a relatively low return fluid flow, so that pump losses caused by friction resistance, heat development and the like are prevented and consequently the efficiency of the basic machine that drives the hydraulic tool is enhanced.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structural Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Gripping On Spindles (AREA)
  • Medicinal Preparation (AREA)
EP05075591A 2004-03-25 2005-03-10 Vérin hydraulique pour outil hydraulique Active EP1580437B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL05075591T PL1580437T3 (pl) 2004-03-25 2005-03-10 Siłownik hydrauliczny do stosowania w narzędziach hydraulicznych

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL1025806A NL1025806C2 (nl) 2004-03-25 2004-03-25 Hydraulische cilinder bijvoorbeeld voor toepassing bij een hydraulisch gereedschap.
NL1025806 2004-03-25

Publications (2)

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EP1580437A1 true EP1580437A1 (fr) 2005-09-28
EP1580437B1 EP1580437B1 (fr) 2007-12-12

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EP (1) EP1580437B1 (fr)
AT (1) ATE380940T1 (fr)
DE (1) DE602005003696T2 (fr)
DK (1) DK1580437T3 (fr)
ES (1) ES2296060T3 (fr)
NL (1) NL1025806C2 (fr)
PL (1) PL1580437T3 (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012010921A1 (fr) * 2010-07-21 2012-01-26 Volvo Compact Equipment S A S Ensemble pouce amovible et appareil de pelle rétrocaveuse doté dudit ensemble
CN102678654A (zh) * 2012-06-02 2012-09-19 山西高行液压股份有限公司 变速油缸系统
CN102803746A (zh) * 2010-01-28 2012-11-28 美卓造纸机械公司 用于利用流体压力驱动的活塞缸装置控制装置位置的设备
US20130086899A1 (en) * 2011-10-05 2013-04-11 Caterpillar Inc. Hydraulic system with bi-directional regeneration
NL2010256C2 (nl) * 2013-02-06 2014-08-07 Hfx Res B V Cilindersamenstel.
CN105723100A (zh) * 2014-01-31 2016-06-29 Ｋｙｂ株式会社 工程机械的控制系统和低压选择回路
EP3064782A1 (fr) * 2015-03-06 2016-09-07 Otto Nussbaum GmbH & Co. KG Ensemble piston/cylindre
EP2722165A3 (fr) * 2012-10-22 2018-01-10 Robert Bosch Gmbh Circuit hydraulique pour un axe hydraulique et axe hydraulique
CN107630856A (zh) * 2017-11-08 2018-01-26 安徽星马专用汽车有限公司 一种顺序伸缩油缸及起重机
CN107999594A (zh) * 2017-12-20 2018-05-08 马鞍山创诚中小企业服务中心有限公司 行程精确控制冲压装置
CN108115029A (zh) * 2017-12-20 2018-06-05 马鞍山创诚中小企业服务中心有限公司 数控冲床冲压方法
CN108127953A (zh) * 2017-12-20 2018-06-08 马鞍山创诚中小企业服务中心有限公司 数控冲床
WO2018108615A1 (fr) * 2016-12-13 2018-06-21 Voith Patent Gmbh Entraînement hydraulique à course rapide et course en charge
CN108397440A (zh) * 2018-04-11 2018-08-14 江阴市军炫智能装备有限公司 一种用于中大型液压金属屑压块机的快速装置
NL2018276B1 (nl) * 2017-02-01 2018-08-22 Demolition And Recycling Equipment B V Hydraulische cilinder bijvoorbeeld voor toepassing bij een hydraulisch gereedschap.
US11131192B2 (en) 2018-02-01 2021-09-28 Vanderbilt University Cylinder actuator
EP3919757A1 (fr) * 2020-06-05 2021-12-08 Demolition and Recycling Equipment B.V. Cylindre hydraulique pour une utilisation avec un outil hydraulique par exemple

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
DE102010033840A1 (de) 2010-08-10 2012-02-16 Alpha Fluid Hydrauliksysteme Müller GmbH Hydraulische Schaltungsanordnung zum Betrieb mechanisch gekoppelter, druckmittelbetätigter Verdrängereinheiten
DE102016205973A1 (de) * 2016-04-11 2017-10-12 Sms Group Gmbh Hydraulikzylinder
DE102020112884A1 (de) 2020-05-12 2021-11-18 Ewo Fluid Power Gmbh Doppelt wirkender Hydraulikzylinder mit redundanten Druckkammern

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US5199658A (en) * 1991-02-16 1993-04-06 Krupp Maschinentechnik Gesellschaft Mit Beschrankter Haftung Dual-force hydraulic drive for a demolition tool
EP0641618A1 (fr) * 1993-09-02 1995-03-08 Methold 's-Hertogenbosch B.V. Dispositif pour concasser et couper des matériaux
DE10121612A1 (de) * 2001-05-04 2002-11-07 Bert Pohl Preßzylinder

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DE1021612B (de) 1955-09-15 1957-12-27 Rodi & Wienerberger Ag Dehnbares Gliederband
GB893592A (en) * 1959-09-04 1962-04-11 Electro Hydraulics Ltd Control system for use with hydraulically or pneumatically operated jacks
US4833971A (en) * 1988-03-09 1989-05-30 Kubik Philip A Self-regulated hydraulic control system
US5199658A (en) * 1991-02-16 1993-04-06 Krupp Maschinentechnik Gesellschaft Mit Beschrankter Haftung Dual-force hydraulic drive for a demolition tool
EP0641618A1 (fr) * 1993-09-02 1995-03-08 Methold 's-Hertogenbosch B.V. Dispositif pour concasser et couper des matériaux
DE10121612A1 (de) * 2001-05-04 2002-11-07 Bert Pohl Preßzylinder

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102803746A (zh) * 2010-01-28 2012-11-28 美卓造纸机械公司 用于利用流体压力驱动的活塞缸装置控制装置位置的设备
US9777458B2 (en) 2010-07-21 2017-10-03 Volvo Compact Equipment Sas Detachable thumb assembly and backhoe digging apparatus comprising the same
WO2012010921A1 (fr) * 2010-07-21 2012-01-26 Volvo Compact Equipment S A S Ensemble pouce amovible et appareil de pelle rétrocaveuse doté dudit ensemble
US20130086899A1 (en) * 2011-10-05 2013-04-11 Caterpillar Inc. Hydraulic system with bi-directional regeneration
US9003951B2 (en) 2011-10-05 2015-04-14 Caterpillar Inc. Hydraulic system with bi-directional regeneration
CN102678654A (zh) * 2012-06-02 2012-09-19 山西高行液压股份有限公司 变速油缸系统
EP2722165A3 (fr) * 2012-10-22 2018-01-10 Robert Bosch Gmbh Circuit hydraulique pour un axe hydraulique et axe hydraulique
NL2010256C2 (nl) * 2013-02-06 2014-08-07 Hfx Res B V Cilindersamenstel.
CN105723100A (zh) * 2014-01-31 2016-06-29 Ｋｙｂ株式会社 工程机械的控制系统和低压选择回路
JP2018507371A (ja) * 2015-03-06 2018-03-15 オットー・ヌスバウム・ゲー・エム・ベー・ハー・ウント・コー・カー・ゲーＯｔｔｏ Ｎｕｓｓｂａｕｍ Ｇｅｓｅｌｌｓｃｈａｆｔ Ｍｉｔ Ｂｅｓｃｈｒａｎｋｔｅｒ Ｈａｆｔｕｎｇ ＆ Ｃｏｍｐａｇｎｉｅ Ｋｏｍｍａｎｄｉｔ Ｇｅｓｅｌｌｓｃｈａｆｔ シリンダ・ピストンユニット
EP3064782A1 (fr) * 2015-03-06 2016-09-07 Otto Nussbaum GmbH & Co. KG Ensemble piston/cylindre
WO2016142202A1 (fr) * 2015-03-06 2016-09-15 Otto Nussbaum Gmbh & Co. Kg Unité cylindre-piston
CN110062848A (zh) * 2016-12-13 2019-07-26 福伊特专利有限公司 具有快速行程和负载行程的液压驱动器
US10859100B2 (en) 2016-12-13 2020-12-08 Voith Patent Gmbh Hydraulic drive with fast stroke and load stroke
WO2018108615A1 (fr) * 2016-12-13 2018-06-21 Voith Patent Gmbh Entraînement hydraulique à course rapide et course en charge
US20190285094A1 (en) * 2016-12-13 2019-09-19 Voith Patent Gmbh Hydraulic drive with fast stroke and load stroke
NL2018276B1 (nl) * 2017-02-01 2018-08-22 Demolition And Recycling Equipment B V Hydraulische cilinder bijvoorbeeld voor toepassing bij een hydraulisch gereedschap.
CN107630856A (zh) * 2017-11-08 2018-01-26 安徽星马专用汽车有限公司 一种顺序伸缩油缸及起重机
CN107630856B (zh) * 2017-11-08 2023-11-28 安徽星马专用汽车有限公司 一种顺序伸缩油缸及起重机
CN108115029A (zh) * 2017-12-20 2018-06-05 马鞍山创诚中小企业服务中心有限公司 数控冲床冲压方法
CN108127953A (zh) * 2017-12-20 2018-06-08 马鞍山创诚中小企业服务中心有限公司 数控冲床
CN107999594A (zh) * 2017-12-20 2018-05-08 马鞍山创诚中小企业服务中心有限公司 行程精确控制冲压装置
US11131192B2 (en) 2018-02-01 2021-09-28 Vanderbilt University Cylinder actuator
CN108397440A (zh) * 2018-04-11 2018-08-14 江阴市军炫智能装备有限公司 一种用于中大型液压金属屑压块机的快速装置
EP3919757A1 (fr) * 2020-06-05 2021-12-08 Demolition and Recycling Equipment B.V. Cylindre hydraulique pour une utilisation avec un outil hydraulique par exemple
NL2025765B1 (nl) * 2020-06-05 2022-01-28 Demolition And Recycling Equipment B V Hydraulische cilinder bijvoorbeeld voor toepassing bij een hydraulisch gereedschap.
US11578474B2 (en) 2020-06-05 2023-02-14 Demolition And Recycling Equipment B.V. Hydraulic cylinder, for example for use with a hydraulic tool

Also Published As

Publication number Publication date
NL1025806C2 (nl) 2005-09-27
DE602005003696D1 (de) 2008-01-24
PL1580437T3 (pl) 2008-05-30
EP1580437B1 (fr) 2007-12-12
ATE380940T1 (de) 2007-12-15
DK1580437T3 (da) 2008-04-07
DE602005003696T2 (de) 2008-12-04
ES2296060T3 (es) 2008-04-16

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