EP3770445B1 - Arrangement with a pneumatic or hydraulic piston rod cylinder - Google Patents

Arrangement with a pneumatic or hydraulic piston rod cylinder 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)
French (fr)
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EP3770445A1 (en
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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Application filed by Beumer Group GmbH and Co KG filed Critical Beumer Group GmbH and Co KG
Priority to ES19187881T priority Critical patent/ES2919566T3/en
Priority to EP19187881.8A priority patent/EP3770445B1/en
Priority to PCT/DE2020/100590 priority patent/WO2021013295A1/en
Publication of EP3770445A1 publication Critical patent/EP3770445A1/en
Application granted granted Critical
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    • 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)

Description

Die Erfindung geht aus von einer Anordnung mit einem pneumatischen oder hydraulischenThe invention is based on an arrangement with a pneumatic or hydraulic

Kolbenstangenzylinder, wobei der pneumatische oder hydraulische Kolbenstangenzylinder einen Zylinder und einen darin in dessen Längsrichtung verstellbaren Kolben aufweist, der mit einer aus dem Zylinder herausragenden Kolbenstange gekoppelt ist und ein in dem Zylinder aufgenommenes Volumen in eine erste Druckkammer, durch die sich die Kolbenstange erstreckt, und eine zweite Druckkammer unterteilt, wobei die Druckkammern über einen Bypass fluidisch miteinander verbunden sind und jeweils einen Druckanschluss aufweisen, der gegebenenfalls auch in einer Zylinderwandung des Zylinders ausgebildet sein kann und über den die Druckkammern mit einem Fluid beaufschlagbar sind, und wobei eine erste Seite des Kolbens die erste Druckkammer und eine der ersten Seite gegenüber angeordnete zweite Seite, die eine im Vergleich zu der ersten Seite größere Fläche aufweist, die zweite Druckkammer begrenzt, wobei die erste und die zweite Druckkammer über eine an die Druckanschlüsse der Druckkammern angeschlossene Bypassleitung des Bypasses fluidisch miteinander verbunden sind wobei der Kolben eine untere Anschlagposition aufweist, in der die Kolbenstange um eine maximale Länge aus dem Zylinder herausragt und ein Dichtumfang des Kolbens, über den der Kolben dichtend am Innenumfang des Zylinders anliegt, einen Druckanschluss der ersten Druckkammer verschließt oder diesen überfährt, über den die Bypassleitung an die erste Druckkammer angeschlossen ist, wobei in der Anschlagposition die erste Druckkammer ein minimales Volumen aufweist, in welches ein weiterer Druckanschluss in die erste Druckkammer mündet. Ein derartiger Kolbenstangenzylinder ist aus der DE 1 941 785 A1 bekannt. Ähnliche Kolbenstangenzylinder beschreiben auch die WO 2013/174121 A1 , die DE 10 2011 009 302 A1 , die DE 2 061 883 A , die DE 10 2006 041 707 B4 und die DE 10 2012 007 170 B3 .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 the piston, via which the piston rests sealingly on the inner circumference of the cylinder, a pressure connection of the first pressure chamber closes or runs over it, via which the bypass line is connected to the first pressure chamber, the first pressure chamber having a minimum volume in the stop position, into which another pressure connection opens into the first pressure chamber. 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 .

Die bekannten Kolbenstangenzylinder haben den Nachteil, dass die Ausbildung des Bypasses konstruktiv aufwendig gestaltet ist, beispielsweise indem der Bypass durch eine Aussparung im Zylinder gewährleistet ist. Dabei kann beispielsweise der Bohrungsdurchmesser des Zylinders abschnittsweise größer als der Durchmesser des Kolbens ausgebildet werden, so dass das Fluid den Kolben in diesem Abschnitt umströmen kann. Diese Bauform hat weiterhin den Nachteil, dass der Einbau zusätzlicher funktionaler Bauteile, beispielsweise der Einbau von Ventilen in den Bypass unmöglich ist. Des Weiteren sind Lösungen bekannt, bei denen der Bypass innerhalb der Kolbenstange ausgebildet ist, so dass die Anschlussstellen für den Bypass mit dem Kolben mitbewegt werden und durch ein Herausfahren einer Anschlussstelle aus der komprimierten Druckkammer in eine weitere Kammer des Bypasses unterbrochen wird. Auch diese Bauform ist konstruktiv aufwendig.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. For example, 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. Furthermore, 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.

Demgegenüber ist es somit die Aufgabe der Erfindung, eine Anordnung mit einem Kolbenstangenzylinder der zuvor beschriebenen Art vorzuschlagen, bei dem der Bypass mit einfachen technischen Mitteln bereitgestellt ist und damit nicht nur kostengünstig hergestellt werden kann, sondern darüber hinaus eine zuverlässige Betriebsweise aufweist.In contrast, it is therefore the object of the invention to propose an arrangement with a piston rod cylinder of the type described above, in which the bypass is provided with simple technical means and can therefore not only be produced inexpensively, but also has reliable operation.

Diese Aufgabe wird durch eine Anordnung mit einem Kolbenstangenzylinder mit den Merkmalen des Anspruchs 1 gelöst. Die abhängigen Ansprüche betreffen jeweils vorteilhafte Ausführungsformen der Erfindung.This object is achieved by an arrangement with a piston rod cylinder having the features of claim 1. The dependent claims each relate to advantageous embodiments of the invention.

Demgemäß ist vorgesehen, dass die Bypassleitung ein unidirektional durchlässiges Ventil, vorzugsweise ein Rückschlagventil, aufweist, das in Fluidströmungsrichtung von der zweiten Druckkammer zur ersten Druckkammer durchlässig ist.Accordingly, it is provided that 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.

Dabei kann vorgesehen sein, dass die Bypassleitung zumindest über einen Teil ihrer Länge und vorzugsweise über ihre gesamte Länge außerhalb des Zylinders angeordnet und/oder geführt ist.Provision can be made for the bypass line to be arranged and/or routed outside the cylinder at least over part of its length and preferably over its entire length.

Die Bypassleitung und/oder das unidirektional durchlässige Ventil können zumindest anteilig und vorzugsweise vollständig in einer Wandung des Zylinders ausgebildet sein. Insbesondere muss der Druckanschluss nicht zwingend nach außen geführt sein.The bypass line and/or the unidirectionally permeable valve can be formed at least partially and preferably completely in a wall of the cylinder. In particular, the pressure connection does not necessarily have to be routed to the outside.

Die Bypassleitung kann über den Druckanschluss der zweiten Druckkammer an die zweite Druckkammer angeschlossen sein. Alternativ oder zusätzlich kann die Bypassleitung über den Druckanschluss der ersten Druckkammer an die erste Druckkammer angeschlossen sein.The bypass line can be connected to the second pressure chamber via the pressure connection of the second pressure chamber. Alternatively or additionally, the bypass line can be connected to the first pressure chamber via the pressure connection of the first pressure chamber.

Der weitere Druckanschluss kann dazu vorgesehen sein, um nach dem Erreichen der Anschlagposition durch Druckbeaufschlagung der ersten Druckkammer den Kolben aus der Anschlagposition zu bewegen, so dass sich das Volumen der ersten Druckkammer vergrößert und das Volumen der zweiten Druckkammer verkleinert.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.

Der Dichtumfang des Kolbens kann den in die erste Druckkammer mündenden Druckanschluss der Bypassleitung ununterbrochen um einen in der Anschlagposition endenden und der Anschlagposition somit unmittelbar vorgelagerten Verstellweg des Kolbens verschließen. Dieser Verstellweg kann beispielsweise bis zu 10 mm, vorzugsweise bis zu 8 mm und besonders bevorzugt bis zu oder genau 4 mm betragen und durch die Abmessung des Dichtumfangs in der Längsrichtung bestimmt oder kleiner als diese Abmessung sein.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.

Die Bypassleitung kann mindestens zwei parallel zueinander verschaltete Teilleitungen aufweisen, die jeweils ein unidirektional durchlässiges Ventil, vorzugsweise ein Rückschlagventil, aufweisen, die in Richtung von der zweiten Druckkammer zu der ersten Druckkammer durchlässig sind.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.

Die Fläche der zweiten Seite kann der Querschnittsfläche des Zylinders senkrecht zur Längsrichtung entsprechen, wobei die Fläche der ersten Seite um eine Querschnittsfläche der Kolbenstange geringer als die Fläche der zweiten Seite ist.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.

Der Flächenunterschied der beiden Seiten des Kolbens kann bei einem gegebenen Druck eine auf den Kolben wirkende Kraft von maximal 150 N und besonders bevorzugt von maximal 135 N verursachen.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.

Es wird somit ein Kolbenstangenzylinder beschrieben, der pneumatisch oder hydraulisch angetrieben ist und einen Zylinder in zwei Druckkammern unterteilt, die jeweils einen Druckanschluss aufweisen. Darüber hinaus weist die erste Druckkammer einen weiteren Druckanschluss auf, um den aus dem Zylinder maximal oder teilweise ausgefahrenen Kolben wieder in den Zylinder einzufahren. Da die beiden Druckkammern über die Bypassleitung fluidisch miteinander verbunden sind, liegt in ihnen im Wesentlichen derselbe Druck vor. Da in der ersten Druckkammer die Kolbenstange angeordnet ist, ist die druckbeaufschlagte Fläche des Kolbens auf Seiten der ersten Druckkammer kleiner als auf Seiten der zweiten Druckkammer. Dadurch wird der Kolben bei gleichem Druck in der ersten und der zweiten Druckkammer derart verlagert, dass sich das Volumen der ersten Druckkammer verkleinert und das der zweiten Druckkammer vergrößert.A piston rod cylinder is thus described which is driven pneumatically or hydraulically and which divides a cylinder into two pressure chambers, each of which has a pressure connection. In addition, 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.

Der Druckanschluss der ersten Druckkammer kann etwas oberhalb des Bewegungsendpunktes des Kolbens angeordnet sein, beispielsweise um 4 mm. Wenn der Kolben den Druckanschluss der Bypassleitung der ersten Druckkammer passiert und dabei verschließt, sind die beiden Druckkammern nicht mehr über die Bypassleitung miteinander verbunden, so dass eine Druckbeaufschlagung für den Druckanschluss der ersten Druckkammer entfällt. Dadurch erhöht sich die auf den Kolben effektiv wirkende Kraft und der Kolben wird in Richtung der ersten Druckkammer gedrückt. Um den Kolben wieder in Richtung der zweiten Druckkammer zu bewegen, kann die erste Druckkammer über einen weiteren Druckanschluss mit Druck beaufschlagt werden, der außerhalb des Bewegungsbereiches des Kolbens im Zylinder angeordnet ist, beispielsweise noch unterhalb oder oberhalb des Bewegungsendpunktes des Kolbens.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. When the piston passes the pressure port of the bypass line of the first pressure chamber and thereby closes it, 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. In order to move the piston back in the direction of the second 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.

Dadurch wird erreicht, dass der Kolben in einem ersten Bewegungsabschnitt mit einer geringen Zustellkraft bewegt werden kann, so dass keine Verletzungsgefahr beispielsweise durch Einklemmen eines Fingers besteht und in einem zweiten Bewegungsabschnitt mit einer erhöhten Zustellkraft. Entsprechend angetriebene Kolbenstangenzylinder können zum Beispiel bei Sackhaltezylindern oder Schweißzangen für das Ultraschallschweißen eingesetzt werden. Bei einem geringen Abstand zwischen dem Druckanschluss der ersten Druckkammer und dem Bewegungsendpunkt des Kolbens kann der Abstand zwischen einem Kontakt-Halteelement des Kolbens und einem entsprechenden Gegenhalteelement zu dem Zeitpunkt, zu dem die Antriebskraft des Kolbens erhöht wird, mithin der Dichtumfang des Kolbens den Druckanschluss passiert, bereits so klein sein, dass eine Person keinen Finger mehr zwischen den Kolben und das Gegenhalteelement bringen kann. So kann verhindert werden, dass ein Finger einer Person zwischen Kolbenstange und Gegenhalteelement mit hoher Kraft eingeklemmt wird.As a result, 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. With a small distance between the pressure port of the first pressure chamber and the movement end point of the piston, the distance between a contact holding element of the piston and a corresponding counter-holding element at the time when the driving force of the piston is increased, thus the sealing circumference of the piston can pass the pressure port , already be so small that a person can no longer put a finger between the piston and the counter-holding element. It can thus be prevented that a person's finger is pinched between the piston rod and the counter-retaining element with great force.

Weitere Einzelheiten der Erfindung werden anhand der nachstehenden Figuren erläutert. Dabei zeigt:

Figur 1
eine erste Ausführungsform einer erfindungsgemäßen Anordnung mit einem pneumatischen oder hydraulischen Kolbenstangenzylinder in schematischer Darstellung; und
Figur 2
eine zweite nicht zur Erfindung gehörende Ausführungsform eines pneumatischen oder hydraulischen Kolbenstangenzylinders in schematischer Darstellung.
Further details of the invention are explained with reference to the figures below. It shows:
figure 1
a first embodiment of an arrangement according to the invention with a pneumatic or hydraulic piston rod cylinder in a schematic representation; and
figure 2
a second embodiment of a pneumatic or hydraulic piston rod cylinder, which does not belong to the invention, in a schematic representation.

Die Figur 1 zeigt in schematischer Darstellung eine erste Ausführungsform einer erfindungsgemäßen Anordnung mit einem Kolbenstangenzylinder 1. Der Kolbenstangenzylinder 1 weist einen Zylinder 2 auf, der über seine gesamte Höhe einen im Wesentlichen konstanten Querschnitt aufweist und daher einfach und kostengünstig in der Bereitstellung ist. In dem Zylinder 2 ist ein Kolben 3 in der Längsrichtung des Zylinders 2 verstellbar angeordnet, wobei der Kolben 3 mit seinem Dichtumfang 12 fluidisch dichtend am Innenumfang 13 des Zylinders 2 anliegt und dadurch das Volumen im Inneren des Zylinders 2 in zwei fluidisch voneinander separierte Druckkammern 5, 6 unterteilt. Von einer der gegenüberliegenden Seiten 8, 9 des Kolbens 3, nämlich von der ersten Seite 8, erstreckt sich die Kolbenstange 4 von den Kolben 3 über die gesamte Länge der ersten Druckkammer 5 aus der ersten Druckkammer 5 heraus.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. From one of the opposite sides 8, 9 of the piston 3, namely from the first side 8, the piston rod 4 extends from the piston 3 over the entire length of the first pressure chamber 5 out of the first pressure chamber 5.

Über ein erstes Ventil 17, eine erste Druckanschlussleitung 19 und einen Druckanschluss 16 ist die erste Druckkammer 5 mit einem Fluiddruck beaufschlagt oder wahlweise entlüftet. Ebenso ist über ein zweites Ventil 18, eine zweite Druckanschlussleitung 20 sowie Druckanschlüsse 15 eine Druckbeaufschlagung sowohl der ersten Druckkammer 5 als auch der zweiten Druckkammer 6 bereitgestellt. Der unterste Druckanschluss 16, der über das erste Ventil 17 angeschlossen ist, ist unterhalb von einer unteren Anschlagposition des Kolbendichtumfangs 12 angeordnet, so dass auch in dieser unteren Anschlagposition der Kolbendichtumfang 12 den Druckanschluss 16 nicht verschließt und somit für die Druckbeaufschlagung der ersten Druckkammer 5 zur Verfügung steht. Demgegenüber verschließt der Kolben 3 mit seinem Dichtumfang 12 in der unteren Anschlagposition und um einen vorgelagerten Verstellweg x, hier 4 mm, den unteren Druckanschluss 15, der über die Druckleitung 20 an das zweite Ventil 18 angeschlossen ist.Via a first valve 17, a first pressure connection line 19 and a pressure connection 16, the first pressure chamber 5 is subjected to a fluid pressure or optionally vented. Likewise, 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. In contrast, 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.

Über eine die Druckanschlüsse 15 miteinander verbindende Bypassleitung 10, die außerhalb des Zylinders 2 geführt ist, ist sichergestellt, dass in der ersten und der zweiten Druckkammer 5, 6 stets derselbe Druck herrscht, wenn der Kolben 3 mit seiner umlaufenden Dichtfläche zwischen den beiden Druckanschlüssen 15 angeordnet ist und insbesondere nicht den an das zweite Ventil 18 angeschlossenen unteren Druckanschluss 15 verschließt. Die Bypassleitung 10 weist zwei parallel zueinander geführte Teilleitungen 14 auf, in denen jeweils ein Rückschlagventil 11 angeordnet ist, so dass hinsichtlich der Funktion der Rückschlagventile 11 eine Redundanz hergestellt ist. Die Rückschlagventile 11 sind in Richtung von der zweiten Druckkammer 6 zur ersten Druckkammer 5 durchlässig und in der entgegengesetzten Richtung sperrend. Der Druckanschluss 16, über welchen die erste Druckanschlussleitung 19 an die erste Druckkammer angeschlossen ist, ist um einen Verstellweg x unterhalb des in die erste Druckkammer 5 mündenden Druckanschlusses 15 der zweiten Druckanschlussleitung 20 angeordnet. Der Verstellweg x beträgt vorzugsweise 4 mm.About a pressure ports 15 interconnecting bypass line 10, which is guided outside of the cylinder 2, it is ensured that in the first and the The second pressure chamber 5, 6 always has the same pressure when the piston 3 is arranged with its circumferential sealing surface between the two pressure connections 15 and in particular does not close the lower pressure connection 15 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.

Um den Kolben 3 der Kolbenstange 4 aus dem Zylinder 2 aus einer eingefahrenen Position, wie sie beispielsweise in Figur 1 dargestellt ist, in eine ausgefahrene Position zu überführen, in welcher, ausgehend von der Darstellung gemäß Figur 1 der Kolben 3 im Zylinder 2 vertikal weiter nach unten verlagert ist, wird über die beiden Ventile 17, 18 jeweils ein gleicher oder im Wesentlichen gleicher Fluiddruck bereitgestellt, mit welchem die erste und die zweite Druckkammer 5, 6 über die Druckanschlussleitungen 19, 20 und die Druckanschlüsse 15, beaufschlagt werden. Da in der ersten Druckkammer 5 die Querschnittsfläche 8 des Kolbens 3, auf welche der Fluiddruck wirkt um die Querschnittsfläche der Kolbenstange 4 geringer als die Querschnittsfläche 9 des Kolbens 3 in der zweiten Druckkammer 6 ist, wirkt in der zweiten Druckkammer 6 ein im Vergleich zur ersten Druckkammer 5 höherer Druck auf den Kolben 3, so dass der Kolben 3 eine effektive Kraftbeaufschlagung in Vertikalrichtung nach unten erfährt, wodurch der Kolben 3 samt Kolbenstange 4 vertikal nach unten verlagert wird.In order to move the piston 3 of the piston rod 4 out of the cylinder 2 from a retracted position, as is the case, for example, in figure 1 is shown to be converted into an extended position in which, based on the representation according to figure 1 the piston 3 in the cylinder 2 is shifted further vertically downwards, the two valves 17, 18 provide the same or substantially the same fluid pressure, with which the first and the second pressure chamber 5, 6 via the pressure connection lines 19, 20 and the Pressure connections 15 are applied. Since in the first pressure chamber 5 the cross-sectional area 8 of the piston 3 on which the fluid pressure acts is smaller by the cross-sectional area of the piston rod 4 than the cross-sectional area 9 of the piston 3 in the second pressure chamber 6, a pressure acts in the second pressure chamber 6 compared to the first Pressure chamber 5 higher pressure on the piston 3, so that the piston 3 experiences an effective application of force in the vertical direction downwards, as a result of which the piston 3 together with the piston rod 4 is displaced vertically downwards.

Über den Durchmesser der Kolbenstange 4 kann somit gerade die Kraft eingestellt werden, welche bei gegebenem Luftdruck auf den Kolben 3 und damit auf die Kolbenstange 4 wirkt. Ist es beispielsweise das Ziel, die auf den Kolben 3 einwirkende Kraft derart gering zu halten, dass das Einklemmen von Fingern vermieden wird, kann beispielsweise bei einem gegebenen Systemdruck von 6 Bar, welcher über die Druckanschlüsse 15, auf die beiden Kammern 5, 6 gegeben wird, ein maximaler Kolbenstangendurchmesser von 16,9 mm bestimmt werden, um noch "erträgliche" 135 N Klemmkraft sicherzustellen.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.

Erst wenn der Kolben 3 soweit in dem Zylinder 2 nach unten verlagert worden ist, dass er mit seinem Dichtumfang 12 den Druckanschluss 15 verschließt und damit der Druckausgleich über die Bypassleitung 10 unterbrochen ist, kann durch erhöhte Druckbeaufschlagung der zweiten Kammer 6 über das zweite Ventil 18 und die zweite Druckleitung 20 eine erhöhte Kraft auf den Kolben 3 und die Kolbenstange 4 ausgeübt werden, wie sie je nach Anwendungsfall erforderlich sein könnte.Only when the piston 3 has been displaced so far down in the cylinder 2 that it closes the pressure connection 15 with its sealing circumference 12 and thus the pressure equalization via the bypass line 10 is interrupted, can the increased pressurization of the second chamber 6 via the second valve 18 and the second pressure line 20, an increased force can be exerted on the piston 3 and the piston rod 4, as may be required depending on the application.

Der Druckanschluss 15 der Bypassleitung 10 an die erste Druckkammer 5 kann dazu so niedrig und kurz oberhalb eines unteren Anschlagpunktes des Kolbens 3 angeordnet sein, dass beispielsweise ein Einklemmen von Fingern nicht mehr möglich ist. Beispielsweise kann dieser letzte Verstellweg x, über welchen bei verschlossener Druckanschlussleitung 15 an der Seite der ersten Druckkammer 5 ein erhöhter Druck aufgebaut werden kann, lediglich 4 mm oder dergleichen betragen.For this purpose, 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. For example, 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.

Um den Kolben 3 aus der unteren Position wieder in die in Figur 1 dargestellte eingefahrene oder teilweise eingefahrene Position zu überführen, kann über das erste Ventil 17 und die erste Druckleitung 19 ein Fluiddruck bereitgestellt werden, während das zweite Ventil 18, welches über die zweite Druckanschlussleitung und den Druckanschluss 15 an die zweite Druckkammer 6 angeschlossen ist, freigeschaltet ist, so dass beim Verlagern des Kolbens 3 in Vertikalrichtung nach oben, wobei das Volumen der zweiten Druckkammer 6 verkleinert wird, ein Druckausgleich durch Fluidabführung über die zweite Druckanschlussleitung 20 und das zweite Ventil 18 bereitgestellt werden kann.In order to return the piston 3 from the lower position to the in figure 1 To convert the retracted or partially retracted position shown, 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 .

Eine nicht zur Erfindung gehörende Ausführungsform ist in Figur 2 gezeigt. Bei dieser ist in dem Zylinder 2 neben einem ersten Kolben 3.1 von diesem beabstandet ein zweiter Kolben 3.2 entlang derselben Kolbenstange 4 angeordnet. Die Kolben 3.1, 3.2 liegen wiederum analog zu der Ausführungsform gemäß Figur 1 entlang ihres jeweiligen Außenumfangs dichtend am Innenumfang des Zylinders 2 an, so dass sie das im Inneren des Zylinders 2 aufgenommene Fluidvolumen unterteilen. Der in der Darstellung gemäß Figur 2 untere Kolben 3.1 trennt eine erste Druckkammer 5 von einer zweiten Druckkammer 6 ab, während der zweite Kolben 3.2 eine dritte Druckkammer 21 von einer vierten Druckkammer 22 separiert. Die dritte Druckkammer 21 ist über ein Trennelement 23 von der zweiten Druckkammer 6 fluiddicht separiert. Die Kolbenstange 4 erstreckt sich über die gesamte Länge der ersten Druckkammer 5 durch die erste Druckkammer 5 hindurch und über diese aus dem Zylinder 2 heraus. Im Bereich der zweiten Druckkammer 6 weist die Kolbenstange 4 einen Durchmesser auf, der größer als der Durchmesser der Kolbenstange 4 im Bereich der ersten Druckkammer ist. Im Bereich von der zweiten bis zur vierten Druckkammer 6, 21, 22 ist der Durchmesser der Kolbenstange 4 im Wesentlichen konstant, er kann jedoch auch in seiner Längsrichtung einen zwischen der zweiten Druckkammer 6 und der vierten Druckkammer 22 variierenden Durchmesser aufweisen. Für die Ausführungsform gemäß Figur 2 ist jedoch wesentlich, dass die Kolbenstange 4 einen abweichenden Durchmesser im Vergleich von erster und zweiter Druckkammer 5, 6 aufweist, wobei der Durchmesser der Kolbenstange 4 in der zweiten Druckkammer 6 größer als der Durchmesser der Kolbenstange 4 in der ersten Druckkammer 5 ist.An embodiment not belonging to the invention is in figure 2 shown. In this case, 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. According to the representation figure 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. In the area of the second pressure chamber 6, 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. In the area from the second to the fourth pressure chamber 6, 21, 22, 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. For the embodiment according to figure 2 However, it is essential that 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.

Die erste Druckanschlussleitung 19 ist von einem ersten Ventil 17 mit einem Fluiddruck beaufschlagt und mündet in die beiden Druckanschlüsse 15 der ersten und der zweiten Druckkammer 5, 6, welche wiederum über eine Bypassleitung 10 miteinander verbunden sind, um einen konstanten Druck in den beiden Kammern 5, 6 sicherzustellen, wenn die Bypassleitung nicht über den Außenumfang des ersten Kolbenelements 3.1 blockiert ist. Um einen Kolbenverstellweg x von etwa 4 mm vertikal oberhalb von dem Druckanschluss 15 der zweiten Druckkammer 6 ist ein weiterer Druckanschluss 25 angeordnet, über welchen von einem zweiten Ventil 18 und eine zweite Druckanschlussleitung 20 eine Druckbeaufschlagung der zweiten Druckkammer 6 unabhängig von dem ersten Ventil 17 bereitgestellt werden kann.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.

Wenn nun über das erste und das zweite Ventil 17, 18 ein gleicheroder im Wesentlichen gleicher Fluiddruck in den Druckkammern 5, 6 bereitgestellt wird, führt dies bei der Ausführungsform gemäß Figur 2 dazu, dass sich der erste Kolben 3.1 und mit diesem der zweite Kolben 3.2 und die die Kolben 3.1, 3.2 miteinander verbindende Kolbenstange 4 in Vertikalrichtung nach oben verlagert werden, da aufgrund des größeren Durchmessers der Kolbenstange 4 im Bereich der zweiten Druckkammer 6 die auf die Unterseite des ersten Kolbens 3.1 in Vertikalrichtung nach oben wirkende Kraft größer als die auf die Oberseite des ersten Kolbens 3.1 wirkende Kraft in Vertikalrichtung nach unten ist. Analog zu der Ausführungsform gemäß Figur 1 wird der erste Kolben 3.1. somit wiederum soweit mit einer geringen Kraft in Vertikalrichtung nach oben verlagert, bis der erste Kolben 3.1 erst mit seinem Außenumfang die in die zweite Druckkammer 6 mündende Anschlussstelle 15 der Bypassleitung 10 verschließt und dann der erste Kolben 3.1 an dem Trennelement anliegend eine obere Anschlagposition erreicht. Wenn der Kolben 3.1 die Bypassleitung 10 verschließt, kann über das erste Ventil 17 und die erste Druckanschlussleitung in der ersten Druckkammer 5 ein entsprechend hoher Überdruck bereitgestellt werden, der zu einer entsprechend höheren Kraftbeaufschlagung des ersten Kolbens 3.1 in Vertikalrichtung nach oben führt, da der Druckausgleich zu der zweiten Druckkammer 6 über die Bypassleitung 10 unterbrochen ist. Die obere Anschlagposition erreicht der Kolben 3.1 wiederum, wenn er an dem Trennelement 23 zur Anlage kommt. Mithin wird die erhöhte Kraft auf den ersten Kolben 3.1 lediglich auf den letzten Bewegungsmillimetern, im vorliegenden Fall 4 mm, bereitgestellt, die beispielsweise danach bemessen sein können, dass ein Einklemmen von Fingern analog zu der Ausführungsform gemäß Figur 1 unmöglich ist.If an equal or substantially equal fluid pressure is now provided in the pressure chambers 5, 6 via the first and the second valve 17, 18, this results in the embodiment according to FIG figure 2 to the fact that the first piston 3.1 and with it the second piston 3.2 and the piston rod 4 connecting the pistons 3.1, 3.2 to one another are shifted upwards in the vertical direction, since due to the larger diameter of the piston rod 4 in the area of the second pressure chamber 6, the Underside of the first piston 3.1 in the vertical direction upward force is greater than the force acting on the top of the first piston 3.1 in the vertical direction downward. Analogous to the embodiment according to figure 1 is the first piston 3.1. thus in turn shifted upwards with a small force in the vertical direction until the outer circumference of the first piston 3.1 closes the connection point 15 of the bypass line 10 opening into the second pressure chamber 6 and then the first piston 3.1 on the separating element fitting reaches an upper stop position. If the piston 3.1 closes the bypass line 10, a correspondingly high overpressure can be provided via the first valve 17 and the first pressure connection line in the first pressure chamber 5, which leads to a correspondingly higher force being applied to the first piston 3.1 in the vertical direction upwards, since the pressure equalization to the second pressure chamber 6 via the bypass line 10 is interrupted. The piston 3 . 1 again reaches the upper stop position when it comes to rest on the separating element 23 . Consequently, 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.

Durch das Verlagern des ersten Kolbens 3.1 unter Variation der Volumina der ersten und zweiten Druckkammern 5, 6 wird auch der zweite Kolben 3.2 am oberen Ende der Kolbenstange 4 derart verlagert, dass sich die Volumina der dritten und der vierten Druckkammer 21, 22 verändern. Während die vierte Druckkammer 22 über eine weitere Druckanschlussstelle und eine zusätzliche Druckanschlussleitung 26 mit einem dritten Ventil 27 verbunden ist, über welche durch ein Verlagern des zweiten Kolbens 3.2 nach oben ein Überdruck abgebaut werden kann, indem das dritte Ventil 27 freigeschaltet wird, weist die dritte Druckkammer 21 ein gegebenenfalls schallgedämpftes Be- und Entlüftungsventil 24 auf, so dass in der dritten Druckkammer 21 stets der Umgebungsdruck herrscht. Bei der Bewegung des zweiten Kolbens 3.2 von unten nach oben wird folglich Luft aus der Umgebung des Kolbenstangenzylinders 1 in die dritte Druckkammer eingesogen, während die Luft beim Verlagern des zweiten Kolbens 3.2 in Vertikalrichtung von oben nach unten über das Ventil 24 aus der dritten Druckkammer 21 austreten kann.By moving the first piston 3.1 while varying the volumes of the first and second pressure chambers 5, 6, 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. While 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. When the second piston 3.2 moves from bottom to top, air from the area around piston rod cylinder 1 is consequently sucked into the third pressure chamber, while when the second piston 3.2 moves in the vertical direction from top to bottom, the air escapes via valve 24 from third pressure chamber 21 can escape.

Nachdem die Kolbenstange 4 und der Kolben 3.1, 3.2 durch gleichmäßige Druckbeaufschlagung der ersten und der zweiten Druckkammer 5, 6 in der zuvor beschriebenen Weise von einer unteren Position in eine obere Position verlagert worden sind, wie dies beispielsweise in Figur 2 gezeigt ist, kann durch Freischalten der an die erste und die zweite Druckkammer 5, 6 angeschlossenen Ventile 17,18 schließlich über das dritte Ventil 27, die zusätzliche Druckanschlussleitung 26 und den weiteren Druckanschluss ein Fluidüberdruck in der vierten Druckkammer 22 bereitgestellt werden, so dass eine auf den zweiten Kolben 3.2 wirkende Kraft den Kolben 3.2 samt der Kolbenstange 4 und dem ersten Kolben 3.1 vertikal nach unten verlagert.After the piston rod 4 and the piston 3.1, 3.2 have been displaced from a lower position to an upper position by uniform pressurization of the first and second pressure chambers 5, 6 in the manner described above, as is the case, for example, in figure 2 is shown, by releasing the valves 17,18 connected to the first and second pressure chambers 5, 6, an excess fluid pressure can finally be provided in the fourth pressure chamber 22 via the third valve 27, the additional pressure connection line 26 and the further pressure connection, so that a the force acting on the second piston 3.2 Piston 3.2 together with the piston rod 4 and the first piston 3.1 shifted vertically downwards.

Die in den Ausführungsformen gezeigten Ventile 17, 18, 27 können beispielsweise als 3-Wege-Ventile ausgebildet sein, die mit einer ersten Anschlussseite an eine Fluiddruckquelle angeschlossen sind, beispielsweise an eine Fluiddruckleitung oder an einen Kompressor. Mit einer weiteren Anschlussseite sind sie mit einem drucklosen Fluidvolumen verbunden, also beispielsweise mit der Umgebungsluft, wenn das Fluid Luft ist. Die dritte Ventilanschlussseite kann dann jeweils mit einer der Druckanschlussleitung 19, 20, 26 verbunden sein, um bedarfsweise den Fluiddruck an den entsprechenden Druckanschlüssen 15, 16, 25 bereitzustellen oder einen Druckausgleich zu realisieren.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.

BezugszeichenlisteReference List

11
Kolbenstangenzylinderpiston rod cylinder
22
Zylindercylinder
33
KolbenPistons
3.13.1
erster Kolbenfirst piston
3.23.2
zweiter Kolbensecond piston
44
Kolbenstangepiston rod
55
erste Druckkammerfirst pressure chamber
66
zweite Druckkammersecond pressure chamber
77
Bypassbypass
88th
erste Seitefirst page
99
zweite Seitesecond page
1010
Bypassleitungbypass line
1111
Rückschlagventilcheck valve
1212
Dichtumfangsealing perimeter
1313
Innenumfanginner circumference
1414
Teilleitungpartial line
1515
Druckanschluss weiterer DruckanschlussPressure connection further pressure connection
1717
erstes Ventilfirst valve
1818
zweites Ventilsecond valve
1919
erste Druckanschlussleitungfirst pressure connection line
2020
zweite Druckanschlussleitungsecond pressure connection line
2121
dritte Druckkammerthird pressure chamber
2222
vierte Druckkammerfourth pressure chamber
2323
Trennelementseparator
2424
schallgedämpftes Ventilsilenced valve
2525
zusätzlicher Druckanschlussadditional pressure connection
2626
dritte Druckanschlussleitungthird pressure connection line
2727
drittes Ventilthird valve
xx
Verstellwegadjustment range

Claims (9)

  1. An arrangement with a pneumatic or hydraulic piston rod cylinder (1), wherein the pneumatic or hydraulic piston rod cylinder (1) comprises a cylinder (2) and a piston (3) which is adjustable therein in the longitudinal direction thereof and which is coupled to a piston rod (4) projecting from the cylinder (2) and divides a volume received in the cylinder (2) into a first pressure chamber (5), through which the piston rod (4) extends, and a second pressure chamber (6), wherein the pressure chambers (5, 6) being fluidically connected to one another via a bypass (7) and each having a pressure port (15) which can be formed in a cylinder wall of the cylinder (2) and via which the pressure chambers (5, 6) can be pressurized by a fluid, and a first side (8) of the piston (3) delimiting the first pressure chamber (5) and a second side (9), which is arranged opposite the first side (8) and has a larger surface area than the first side (8), delimiting the second pressure chamber (6), wherein the first and the second pressure chambers (5, 6) are fluidically connected to each other via a bypass line (10, 14) of the bypass (7) connected to the pressure ports (15) of the pressure chambers (5, 6), wherein the piston (3) has a lower stop position in which the piston rod (4) projects out of the cylinder (2) by a maximum length, and a sealing circumference (12) of the piston (3), via which the piston (3) bears in a sealing manner against the inner circumference (13) of the cylinder (2), closes off a pressure port (15) of the first pressure chamber (5) or passes over it, so that the bypass line (10, 14) is connected to the first pressure chamber (5), wherein in the stop position the first pressure chamber (5) has a minimum volume into which a further pressure port (16) opens into the first pressure chamber (5), characterized in that the bypass line (10, 14) has a unidirectionally permeable valve (11), preferably a non-return valve, which is permeable in the fluid flow direction from the second pressure chamber (6) to the first pressure chamber (5).
  2. The arrangement according to claim 1, wherein the bypass line (10, 14) is arranged outside the cylinder (2) over at least part of its length and preferably over its entire length.
  3. An arrangement according to any one of the preceding claims, wherein the bypass line (10, 14) is connected to the second pressure chamber (6) via the pressure port (15) of the second pressure chamber (6).
  4. An arrangement according to any one of the preceding claims, wherein the bypass line (10, 14) is connected to the first pressure chamber (6) via the pressure port (15) of the first pressure chamber (5).
  5. An arrangement according to claim 1, in which the sealing circumference (12) of the piston (3) closes or passes over the pressure port (15) of the bypass line (10, 14) opening into the first pressure chamber (5) without interruption over an adjustment path (x) of the piston (3) ending in the stop position.
  6. An arrangement according to claim 5, wherein the adjustment travel (x) is up to 10 mm, preferably up to 8 mm and particularly preferably up to or exactly 4 mm and/or is determined by the dimension of the seal circumference (12) in the longitudinal direction.
  7. An arrangement according to any one of the preceding claims, in which the bypass line (10, 14) has at least two partial lines (14) connected in parallel with one another, each of which has a unidirectional permeable valve (11), preferably a check valve, which are permeable in the direction from the second pressure chamber (6) to the first pressure chamber (5).
  8. An arrangement according to any one of the preceding claims, wherein the area of the second side (9) corresponds to the cross-sectional area of the cylinder (2) perpendicular to the longitudinal direction and the area of the first side (8) is less than the area of the second side (9) by a cross-sectional area of the piston rod (4).
  9. An arrangement according to any one of the preceding claims, in which the difference in area of the two sides (8, 9) of the piston (3) at a given pressure causes a force acting on the piston (3) of at most 150 N and particularly preferably at most 135 N.
EP19187881.8A 2019-07-23 2019-07-23 Arrangement with a pneumatic or hydraulic piston rod cylinder Active EP3770445B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES19187881T ES2919566T3 (en) 2019-07-23 2019-07-23 Arrangement with pneumatic or hydraulic piston rod cylinder
EP19187881.8A EP3770445B1 (en) 2019-07-23 2019-07-23 Arrangement with a pneumatic or hydraulic piston rod cylinder
PCT/DE2020/100590 WO2021013295A1 (en) 2019-07-23 2020-07-03 Pneumatic or hydraulic piston rod cylinder

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19187881.8A EP3770445B1 (en) 2019-07-23 2019-07-23 Arrangement with a pneumatic or hydraulic piston rod cylinder

Publications (2)

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

Family

ID=67438636

Family Applications (1)

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EP19187881.8A Active EP3770445B1 (en) 2019-07-23 2019-07-23 Arrangement with a pneumatic or hydraulic piston rod cylinder

Country Status (3)

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

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1941785A1 (en) * 1969-08-16 1971-03-04 Metrawatt Ag Fabrik Elek Scher Pneumatic or hydraulically driven working stroke cylinder
DE2061883C3 (en) 1970-12-16 1974-03-14 Aviat Gmbh Hydraulic or pneumatic working cylinder
DE102006041707B4 (en) 2006-05-10 2009-01-02 Tünkers Maschinenbau Gmbh Piston-cylinder unit (working cylinder) for clamping, and / or pressing, and / or joining, and / or punching, and / or embossing, and / or punching and / or welding, for example, with the interposition of a toggle joint arrangement
DE102011009302A1 (en) * 2011-01-24 2012-07-26 Helmut Steinhilber Fluid cylinder for press device, has aperture in cylindrical tube that is exposed and opened into cylindrical space during basic stroke of piston while aperture is covered or opened into other cylindrical space during power stroke
DE102012007170B3 (en) 2012-04-07 2013-08-08 Festo Ag & Co. Kg Drive device for controlling actuating force of fluid-pressure actuators, has fluid-actuated working cylinder with housing, where front drive chamber is separated from additional chamber through front end panel in fluid-tight manner
CN103423235B (en) * 2012-05-23 2015-11-25 中联重科股份有限公司 Hydraulic cylinder buffer control method, buffer type hydraulic cylinder control system and hydraulic equipment

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EP3770445A1 (en) 2021-01-27
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