EP3770445B1 - Arrangement avec un vérin pneumatique ou hydraulique - Google Patents

Arrangement avec un vérin pneumatique ou hydraulique Download PDF

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Publication number
EP3770445B1
EP3770445B1 EP19187881.8A EP19187881A EP3770445B1 EP 3770445 B1 EP3770445 B1 EP 3770445B1 EP 19187881 A EP19187881 A EP 19187881A EP 3770445 B1 EP3770445 B1 EP 3770445B1
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EP
European Patent Office
Prior art keywords
pressure
pressure chamber
piston
cylinder
piston rod
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.)
Active
Application number
EP19187881.8A
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German (de)
English (en)
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EP3770445A1 (fr
Inventor
Marc Tellen
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Beumer Group GmbH and Co KG
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Beumer Group GmbH and Co KG
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Priority to ES19187881T priority Critical patent/ES2919566T3/es
Priority to EP19187881.8A priority patent/EP3770445B1/fr
Priority to PCT/DE2020/100590 priority patent/WO2021013295A1/fr
Publication of EP3770445A1 publication Critical patent/EP3770445A1/fr
Application granted granted Critical
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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
    • F15B11/024—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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • 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
    • F15B11/0365—Tandem constructions
    • 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
    • F15B15/17—Characterised by the construction of the motor unit of the straight-cylinder type of differential-piston type
    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—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
    • F15B2211/3057—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 two valves, one for each port of a double-acting 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
    • F15B2211/305—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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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
    • F15B2211/7053—Double-acting 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7055—Linear output members having more than two chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—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
    • F15B2211/7056—Tandem cylinders
    • 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
    • F15B2211/76—Control of force or torque of the 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press
    • 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
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8643—Control during or prevention of abnormal conditions the abnormal condition being a human failure
    • 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
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8757—Control measures for coping with failures using redundant components or assemblies

Definitions

  • the invention is based on an arrangement with a pneumatic or hydraulic
  • Piston rod cylinder the pneumatic or hydraulic piston rod cylinder having a cylinder and a piston therein which can be adjusted in its longitudinal direction, which is coupled to a piston rod protruding from the cylinder and a volume accommodated in the cylinder into a first pressure chamber through which the piston rod extends, and a second pressure chamber, wherein the pressure chambers are fluidically connected to one another via a bypass and each have a pressure connection, which can optionally also be formed in a cylinder wall of the cylinder and via which the pressure chambers can be pressurized with a fluid, and wherein a first side of the piston the first pressure chamber and a second side arranged opposite the first side, which has a larger area compared to the first side, delimits the second pressure chamber, the first and the second pressure chamber being connected to the pressure connections of the pressure chambers via a whose bypass line of the bypass is fluidically connected to one another, the piston having a lower stop position in which the piston rod projects out of the cylinder by a maximum length and a sealing circumference of
  • Such a piston rod cylinder is from DE 1 941 785 A1 known. Similar piston rod cylinders also describe the WO 2013/174121 A1 , the DE 10 2011 009 302 A1 , the DE 2 061 883 A , the DE 10 2006 041 707 B4 and the DE 10 2012 007 170 B3 .
  • the known piston rod cylinders have the disadvantage that the design of the bypass is complex in terms of construction, for example in that the bypass is ensured by a recess in the cylinder.
  • the Bore diameter of the cylinder are formed in sections larger than the diameter of the piston, so that the fluid can flow around the piston in this section.
  • This design also has the disadvantage that the installation of additional functional components, such as the installation of valves in the bypass is impossible.
  • solutions are known in which the bypass is formed within the piston rod so that the connection points for the bypass are moved with the piston and is interrupted by moving a connection point out of the compressed pressure chamber into another chamber of the bypass. This design is also complex in terms of construction.
  • the bypass line has a unidirectionally permeable valve, preferably a check valve, which is permeable in the fluid flow direction from the second pressure chamber to the first pressure chamber.
  • bypass line can be arranged and/or routed outside the cylinder at least over part of its length and preferably over its entire length.
  • bypass line and/or the unidirectionally permeable valve can be formed at least partially and preferably completely in a wall of the cylinder.
  • the pressure connection does not necessarily have to be routed to the outside.
  • the bypass line can be connected to the second pressure chamber via the pressure connection of the second pressure chamber.
  • the bypass line can be connected to the first pressure chamber via the pressure connection of the first pressure chamber.
  • the further pressure connection can be provided to move the piston out of the stop position after the stop position has been reached by pressurizing the first pressure chamber, so that the volume of the first pressure chamber increases and the volume of the second pressure chamber decreases.
  • the sealing circumference of the piston can continuously close the pressure connection of the bypass line, which opens into the first pressure chamber, by an adjustment path of the piston that ends in the stop position and is therefore immediately upstream of the stop position.
  • This adjustment path can be, for example, up to 10 mm, preferably up to 8 mm and particularly preferably up to or exactly 4 mm and can be determined by the dimension of the sealing circumference in the longitudinal direction or be smaller than this dimension.
  • the bypass line can have at least two partial lines connected parallel to one another, each of which has a unidirectionally permeable valve, preferably a check valve, which is permeable in the direction from the second pressure chamber to the first pressure chamber.
  • the area of the second side may correspond to the cross-sectional area of the cylinder perpendicular to the longitudinal direction, the area of the first side being less than the area of the second side by a cross-sectional area of the piston rod.
  • the difference in area between the two sides of the piston can, at a given pressure, cause a force on the piston of at most 150 N and more preferably at most 135 N.
  • a piston rod cylinder which is driven pneumatically or hydraulically and which divides a cylinder into two pressure chambers, each of which has a pressure connection.
  • the first pressure chamber has a further pressure connection in order to retract the piston, which is maximally or partially extended from the cylinder, back into the cylinder. Since the two pressure chambers are fluidly connected to one another via the bypass line, the pressure in them is essentially the same. Since in the first pressure chamber the Piston rod is arranged, the pressurized area of the piston is smaller on the side of the first pressure chamber than on the side of the second pressure chamber. As a result, the piston is displaced at the same pressure in the first and second pressure chambers in such a way that the volume of the first pressure chamber decreases and that of the second pressure chamber increases.
  • the pressure connection of the first pressure chamber can be arranged somewhat above the end point of movement of the piston, for example by 4 mm.
  • the two pressure chambers are no longer connected to one another via the bypass line, so that there is no pressurization for the pressure port of the first pressure chamber. This increases the effective force acting on the piston and pushes the piston in the direction of the first pressure chamber.
  • the first pressure chamber can be pressurized via a further pressure connection, which is arranged outside the range of movement of the piston in the cylinder, for example still below or above the end point of movement of the piston.
  • the piston can be moved in a first movement section with a low feed force, so that there is no risk of injury, for example by pinching a finger, and in a second movement section with an increased feed force.
  • Correspondingly driven piston rod cylinders can be used, for example, in bag holding cylinders or welding tongs for ultrasonic welding.
  • the figure 1 shows a schematic representation of a first embodiment of an arrangement according to the invention with a piston rod cylinder 1.
  • the piston rod cylinder 1 has a cylinder 2 which has a substantially constant cross section over its entire height and is therefore simple and inexpensive to provide.
  • a piston 3 is arranged in the cylinder 2 so that it can be adjusted in the longitudinal direction of the cylinder 2, the piston 3 with its sealing circumference 12 being in fluid contact with the inner circumference 13 of the cylinder 2 in a fluid-tight manner, thereby dividing the volume inside the cylinder 2 into two fluidically separate pressure chambers 5 , 6 divided.
  • the first pressure chamber 5 is subjected to a fluid pressure or optionally vented.
  • a pressurization of both the first pressure chamber 5 and the second pressure chamber 6 is provided via a second valve 18 , a second pressure connection line 20 and pressure connections 15 .
  • the lowest pressure connection 16, which is connected via the first valve 17, is arranged below a lower stop position of the piston sealing circumference 12, so that the piston sealing circumference 12 does not close the pressure connection 16 even in this lower stop position and is therefore available for pressurizing the first pressure chamber 5 Available.
  • the piston 3 with its sealing circumference 12 in the lower stop position and by an upstream adjustment path x, here 4 mm, closes the lower pressure connection 15, which is connected via the pressure line 20 is connected to the second valve 18.
  • the bypass line 10 has two sub-lines 14 running parallel to one another, in each of which a check valve 11 is arranged, so that a redundancy is established with regard to the function of the check valves 11 .
  • the check valves 11 are permeable in the direction from the second pressure chamber 6 to the first pressure chamber 5 and are blocking in the opposite direction.
  • the pressure connection 16, via which the first pressure connection line 19 is connected to the first pressure chamber, is arranged by an adjustment path x below the pressure connection 15 of the second pressure connection line 20, which opens into the first pressure chamber 5.
  • the adjustment path x is preferably 4 mm.
  • the force that acts on the piston 3 and thus on the piston rod 4 at a given air pressure can thus be adjusted via the diameter of the piston rod 4 . If, for example, the aim is to keep the force acting on the piston 3 so low that fingers are prevented from getting caught, for example, at a given system pressure of 6 bar, which is applied to the two chambers 5, 6 via the pressure connections 15 a maximum piston rod diameter of 16.9 mm will be determined in order to ensure a still "tolerable" 135 N clamping force.
  • the pressure connection 15 of the bypass line 10 to the first pressure chamber 5 can be arranged so low and just above a lower stop point of the piston 3 that, for example, it is no longer possible for fingers to be pinched.
  • this last adjustment path x via which an increased pressure can be built up on the side of the first pressure chamber 5 when the pressure connection line 15 is closed, can amount to only 4 mm or the like.
  • a fluid pressure can be provided via the first valve 17 and the first pressure line 19, while the second valve 18, which is connected to the second pressure chamber 6 via the second pressure connection line and the pressure connection 15, is released , so that when the piston 3 is displaced in the vertical direction upwards, with the volume of the second pressure chamber 6 being reduced, pressure equalization can be provided by fluid discharge via the second pressure connection line 20 and the second valve 18 .
  • FIG. 2 An embodiment not belonging to the invention is in figure 2 shown.
  • a second piston 3.2 is arranged along the same piston rod 4 in the cylinder 2 next to a first piston 3.1 at a distance from this.
  • the pistons 3.1, 3.2 are again analogous to the embodiment according to FIG figure 1 along their respective outer circumference sealingly on the inner circumference of the cylinder 2, so that they subdivide the volume of fluid accommodated inside the cylinder 2.
  • Lower piston 3.1 separates a first pressure chamber 5 from a second pressure chamber 6, while the second piston 3.2 separates a third pressure chamber 21 from a fourth pressure chamber 22.
  • the third pressure chamber 21 is separated from the second pressure chamber 6 in a fluid-tight manner by a separating element 23 .
  • the piston rod 4 extends over the entire length of the first pressure chamber 5 through and out of the first pressure chamber 5 out of cylinder 2.
  • the piston rod 4 has a diameter that is larger than the diameter of the piston rod 4 in the area of the first pressure chamber.
  • the diameter of the piston rod 4 is essentially constant, but it can also have a varying diameter between the second pressure chamber 6 and the fourth pressure chamber 22 in its longitudinal direction.
  • the piston rod 4 has a different diameter compared to the first and second pressure chambers 5, 6, the diameter of the piston rod 4 in the second pressure chamber 6 being larger than the diameter of the piston rod 4 in the first pressure chamber 5.
  • the first pressure connection line 19 is subjected to a fluid pressure by a first valve 17 and opens into the two pressure connections 15 of the first and second pressure chambers 5, 6, which in turn are connected to one another via a bypass line 10 in order to maintain a constant pressure in the two chambers 5 , 6 ensure if the bypass line is not blocked on the outer circumference of the first piston element 3.1.
  • a further pressure connection 25 is arranged by a piston adjustment path x of approximately 4 mm vertically above the pressure connection 15 of the second pressure chamber 6, via which pressure is applied to the second pressure chamber 6 independently of the first valve 17 by a second valve 18 and a second pressure connection line 20 can be.
  • the increased force on the first piston 3.1 is only provided over the last millimeters of movement, in the present case 4 mm, which can be measured, for example, according to the fact that fingers cannot be pinched analogously to the embodiment according to FIG figure 1 is impossible.
  • the second piston 3.2 at the upper end of the piston rod 4 is also moved in such a way that the volumes of the third and fourth pressure chambers 21, 22 change.
  • the fourth pressure chamber 22 is connected via a further pressure connection point and an additional pressure connection line 26 to a third valve 27, via which excess pressure can be reduced by moving the second piston 3.2 upwards, in that the third valve 27 is released, the third Pressure chamber 21 an optionally soundproofed ventilation valve 24, so that in the third pressure chamber 21 there is always the ambient pressure.
  • the valves 17, 18, 27 shown in the embodiments can be designed, for example, as 3-way valves which are connected to a fluid pressure source with a first connection side, for example to a fluid pressure line or to a compressor. With a further connection side they are connected to an unpressurized volume of fluid, for example to the ambient air if the fluid is air.
  • the third valve connection side can then be connected to one of the pressure connection lines 19, 20, 26 in order to provide the fluid pressure at the corresponding pressure connections 15, 16, 25 or to realize pressure equalization as required.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Actuator (AREA)
  • Load-Engaging Elements For Cranes (AREA)
  • Forklifts And Lifting Vehicles (AREA)

Claims (9)

  1. Dispositif avec un cylindre à tige de piston pneumatique ou hydraulique, dans lequel le cylindre à tige de piston pneumatique ou hydraulique (1) comprend un cylindre (2) et un piston (3) mobile dans la direction longitudinale de celui-ci, qui est couplé avec une tige de piston (4) dépassant du cylindre (2) et un volume délimité par le cylindre (2) se divise en une première chambre de pression (5), à travers laquelle s'étend la tige de piston (4), et une deuxième chambre de pression (6), les chambres de pression (5, 6) étant reliées entre elles de manière fluidique par une dérivation (7) et comprenant chacune un raccord de pression (15), qui peut être réalisé dans une paroi du cylindre (2) et par l'intermédiaire desquels les chambres de pression (5, 6) peuvent être alimentées en pression de fluide, et dans lequel un premier côté (8) du piston (3) délimite la première chambre de pression (5) et un deuxième côté (9), disposé en face du premier côté (8), qui présente une surface plus grande que celle du premier côté (8), délimite la deuxième chambre de pression (6), dans lequel les première et deuxième chambres de pression (5, 6) sont reliées entre elles de manière fluidique par l'intermédiaire d'une conduite de dérivation (10, 14) de la dérivation (7), raccordée aux raccords de pression (15) des chambres de pression (5, 6), dans lequel le piston (3) présente une position de butée inférieure dans laquelle la tige de piston (4) dépasse d'une longueur maximale hors du cylindre (2) et une circonférence d'étanchéité (12) du piston (3), par l'intermédiaire de laquelle le piston (3) s'appuie de manière étanche sur la circonférence interne (13) du piston (2), obture un raccord de pression (15) de la première chambre de pression (5) ou passe par-dessus celui-ci, par l'intermédiaire de laquelle la conduite de dérivation (10, 14) est raccordée à la première chambre de pression (5), dans lequel, dans la position de butée, la première chambre de pression (5) présente un volume minimal, dans lequel un autre raccord de pression (16) débouche dans la première chambre de pression (5),
    caractérisé en ce que la conduite de dérivation (10, 14) comprend une soupape à perméabilité unidirectionnelle (11), de préférence un clapet anti-retour qui, dans la direction d'écoulement du fluide, est perméable de la deuxième chambre de pression (6) vers la première chambre de pression (5).
  2. Dispositif selon la revendication 1, dans lequel la conduite de dérivation (10, 14) est disposée, au moins sur une partie de sa longueur et, de préférence, sur toute sa longueur, à l'extérieur du cylindre (2).
  3. Dispositif selon l'une des revendications précédentes, dans lequel la conduite de dérivation (10, 14) est raccordée par l'intermédiaire du raccord de pression (15) de la deuxième chambre de pression (6) à la deuxième chambre de pression (6).
  4. Dispositif selon l'une des revendications précédentes, dans lequel la conduite de dérivation (10, 14) est raccordée par l'intermédiaire du raccord de pression (15) de la première chambre de pression (5) à la deuxième chambre de pression (6).
  5. Dispositif selon la revendication 1, dans lequel la circonférence d'étanchéité (12) du piston (3) obture ou passe par-dessus le raccord de pression (15) de la conduite de dérivation (10, 14), débouchant dans la première chambre de pression (5), sur un trajet de déplacement (x) du piston (3) se terminant dans la position de butée.
  6. Dispositif selon la revendication 5, dans lequel le trajet de déplacement (x) est jusqu'à 10 mm, de préférence jusqu'à 8 mm et plus particulièrement de préférence jusqu'à ou exactement 4 mm et/ou est déterminé par la dimension de la circonférence d'étanchéité (12) dans la direction longitudinale.
  7. Dispositif selon l'une des revendications précédentes, dans lequel la conduite de dérivation (10, 14) comprend au moins deux conduites partielles (14) branchées entre elles de manière parallèle, qui comprennent chacune une soupape à perméabilité unidirectionnelle (11), de préférence un clapet anti-retour, qui sont perméables dans la direction de la deuxième chambre de pression (6) vers la première chambre de pression (5).
  8. Dispositif selon l'une des revendications précédentes, dans lequel la surface du deuxième côté (9) correspond à la surface de section transversale du cylindre (2) perpendiculairement à la direction longitudinale et la surface du premier côté (8) est inférieure d'une surface de section transversale de la tige de piston (4) par rapport à la surface du deuxième côté (9).
  9. Dispositif selon l'une des revendications précédentes, dans lequel la différence de surface entre les deux côtés (8, 9) du piston (3) provoque, pour une pression donnée, une force exercée sur le piston (3) de 150 N maximum et de préférence de 135 N maximum.
EP19187881.8A 2019-07-23 2019-07-23 Arrangement avec un vérin pneumatique ou hydraulique Active EP3770445B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES19187881T ES2919566T3 (es) 2019-07-23 2019-07-23 Disposición con cilindro de vástago de pistón neumático o hidráulico
EP19187881.8A EP3770445B1 (fr) 2019-07-23 2019-07-23 Arrangement avec un vérin pneumatique ou hydraulique
PCT/DE2020/100590 WO2021013295A1 (fr) 2019-07-23 2020-07-03 Cylindre de tige de piston pneumatique ou hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19187881.8A EP3770445B1 (fr) 2019-07-23 2019-07-23 Arrangement avec un vérin pneumatique ou hydraulique

Publications (2)

Publication Number Publication Date
EP3770445A1 EP3770445A1 (fr) 2021-01-27
EP3770445B1 true EP3770445B1 (fr) 2022-05-25

Family

ID=67438636

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19187881.8A Active EP3770445B1 (fr) 2019-07-23 2019-07-23 Arrangement avec un vérin pneumatique ou hydraulique

Country Status (3)

Country Link
EP (1) EP3770445B1 (fr)
ES (1) ES2919566T3 (fr)
WO (1) WO2021013295A1 (fr)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1941785A1 (de) * 1969-08-16 1971-03-04 Metrawatt Ag Fabrik Elek Scher Pneumatischer oder hydraulisch angetriebener Arbeitshubzylinder
DE2061883C3 (de) 1970-12-16 1974-03-14 Aviat Gmbh Hydraulik- oder Pneumatikarbeitszylinder
DE102006041707B4 (de) 2006-05-10 2009-01-02 Tünkers Maschinenbau Gmbh Kolben-Zylinder-Einheit (Arbeitszylinder) zum Spannen, und/oder Pressen, und/oder Fügen, und/oder Stanzen, und/oder Prägen, und/oder Lochen und/oder Schweißen, zum Beispiel unter Zwischenschaltung einer Kniehebelgelenkanordnung
DE102011009302A1 (de) * 2011-01-24 2012-07-26 Helmut Steinhilber Fluidzylinder und Pressvorrichtung
DE102012007170B3 (de) 2012-04-07 2013-08-08 Festo Ag & Co. Kg Antriebsvorrichtung
CN103423235B (zh) * 2012-05-23 2015-11-25 中联重科股份有限公司 液压缸缓冲控制方法、缓冲式液压缸控制系统及液压设备

Also Published As

Publication number Publication date
ES2919566T3 (es) 2022-07-27
EP3770445A1 (fr) 2021-01-27
WO2021013295A1 (fr) 2021-01-28

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