EP3770444B1 - Ensemble avec un vérin pneumatique ou hydraulique - Google Patents

Ensemble avec un vérin pneumatique ou hydraulique Download PDF

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Publication number
EP3770444B1
EP3770444B1 EP19187867.7A EP19187867A EP3770444B1 EP 3770444 B1 EP3770444 B1 EP 3770444B1 EP 19187867 A EP19187867 A EP 19187867A EP 3770444 B1 EP3770444 B1 EP 3770444B1
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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.)
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Application number
EP19187867.7A
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German (de)
English (en)
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EP3770444A1 (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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Application filed by Beumer Group GmbH and Co KG filed Critical Beumer Group GmbH and Co KG
Priority to ES19187867T priority Critical patent/ES2929764T3/es
Priority to EP19187867.7A priority patent/EP3770444B1/fr
Priority to PCT/DE2020/100591 priority patent/WO2021013296A1/fr
Publication of EP3770444A1 publication Critical patent/EP3770444A1/fr
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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 first valve and a pneumatic or hydraulic piston rod cylinder with a cylinder and a first piston therein which can be adjusted in its longitudinal direction, which is coupled to at least one piston rod protruding from the cylinder and converts a volume accommodated in the cylinder into a first pressure chamber, through which the piston rod extends out of the cylinder, and a second pressure chamber, wherein the first and the second pressure chamber are fluidically connected to one another via a bypass and each have a pressure connection which is completely or at least partially in a cylinder wall of the cylinder can be formed, and via which the pressure chambers can be subjected to a fluid pressure by means of the first valve connected to a first pressure connection line, and wherein a first side of the first piston contains the first pressure chamber and a second side arranged opposite the first Side of the first piston, which has a smaller area compared to the first side, depending on the desired direction of movement of the piston, delimits the second pressure chamber, with the piston rod extending from the first
  • Such a piston rod cylinder is from DE 10 2011 009 302 A1 known. Similar piston rod cylinders also describe the DE 2 061 883 A , the DE 19 41 785 A1 , 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 can be made larger in sections 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 it is impossible to install additional functional components, for example the installation of valves in the bypass.
  • 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 interrupted by moving a connection point out of the compressed pressure chamber into another chamber of the bypass becomes. This design is also complex in terms of construction and is therefore correspondingly expensive to provide.
  • a further pressure connection is arranged one piston adjustment path vertically above the pressure connection of the second pressure chamber, via which a second pressure connection, connected to the further pressure connection valve and a second pressure connection line, pressurization of the second pressure chamber is provided independently of the first valve wherein the piston rod extends from the first piston through a separating element which fluidly separates the second pressure chamber from a third pressure chamber of the cylinder, into the third pressure chamber and has at its end a second piston which separates the third pressure chamber from a fourth pressure chamber of the cylinder is fluidically separated, the fourth pressure chamber being connected via a further pressure connection and an additional pressure connection line to a third valve, via which an excess fluid pressure can be provided in the fourth pressure chamber, so that one on the second Piston acting force the piston together with the piston rod and the first piston can be displaced vertically downwards.
  • the first piston can thus in particular not be attached to the end of the piston rod, as is the case with the arrangements known from the prior art. Rather, the piston rod can extend in the longitudinal direction of the cylinder on both sides of the piston through both of the pressure chambers, which are fluidically separated from one another by the piston, over their entire length in the longitudinal direction. Due to the different cross-section of the piston rod in relation to the two sides of the piston, the two opposite sides of the piston have a difference in area, which is just the difference in cross-sectional area of the Piston rod in the two pressure chambers corresponds.
  • the third pressure chamber can have ambient pressure and can be aerated and/or vented to the surroundings of the piston rod cylinder for this purpose via a preferably soundproofed valve.
  • the separating element can be designed as a double seal, with a first and a second seal which are arranged at a distance from one another in the longitudinal direction of the piston and enclose the piston rod.
  • the bypass of the piston rod cylinder can be designed and guided entirely outside of the cylinder.
  • the first and the second pressure chamber are fluidly connected to one another via a bypass line of the bypass connected to pressure connections of the first and the second pressure chamber.
  • the bypass line may be located outside the cylinder over at least part of its length and preferably over its entire length.
  • the bypass line like the pressure connections it connects, can be completely or essentially completely integrated into a wall of the cylinder.
  • the bypass line may have a unidirectionally permeable valve, preferably a check valve, which is permeable in the direction of fluid flow from the second pressure chamber to the first pressure chamber and impermeable in the opposite direction.
  • the bypass line can be connected to the second pressure chamber via the pressure connection of the second pressure chamber. Additionally or alternatively, the bypass line can be connected to the first pressure chamber at its opposite end via the pressure connection of the first pressure chamber.
  • the first piston can have a stop position in which the piston rod projects into the cylinder by a maximum length and a sealing circumference of the first piston, via which the first piston rests sealingly on the inner circumference of the cylinder, closes or runs over a pressure connection to the second pressure chamber, via which the bypass line is connected to the second pressure chamber.
  • the fourth pressure chamber can have a minimal volume into which another pressure connection opens.
  • the sealing circumference of the first piston can continuously close or overrun the pressure connection of the bypass line that opens into the second pressure chamber via the piston adjustment path of the first piston ending in the stop position, so that via the piston adjustment path due to the closed bypass line in the first pressure chamber significant overpressure built up compared to the second pressure chamber and accordingly a high force can be exerted on the first piston, so that it can move with corresponding force on the piston adjustment path in the direction of the second pressure chamber, the volume of which is further reduced.
  • the piston adjustment path can, for example, be up to 10 mm, preferably up to 8 mm and particularly preferably up to or exactly 4 mm and/or be determined by the dimension of the sealing circumference in the longitudinal direction.
  • the piston adjustment path can be selected precisely thereafter in order to avoid accidentally pinching a finger.
  • the bypass line can have at least two partial lines connected in parallel, each having a unidirectionally permeable valve, preferably a check valve, which is permeable in the direction from the second pressure chamber to the first pressure chamber and impermeable in the opposite direction.
  • the difference in area between the two sides of the first piston can, at a given pressure, cause a force acting on the first piston of at most 150 N and more preferably at most 135 N.
  • the upward movement of the piston can be controlled in that pressure is applied to a lower and a middle pressure chamber via pressure connection points, for example via valves. This can be vented via a pressure connection point of the uppermost pressure chamber. Since the middle and the lower pressure chamber are connected to each other via a bypass, the same pressure prevails in the lower and the middle pressure chamber.
  • an unpressurized chamber is separated from the central pressure chamber by a separating element. The unpressurized chamber can be connected to the environment through an opening, a vent valve or a silencer, so that essentially ambient pressure prevails in this chamber.
  • the uppermost chamber of the cylinder can be pressurized with fluid pressure via its pressure connection point by switching a connected valve, while the valves connected to the lower and middle pressure chambers are switched to the rest position so that they are vented.
  • the figure 1 shows a schematic representation of an embodiment of a piston rod cylinder 1 that does not belong to the invention 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 to the second valve 18 via the pressure line 20 .
  • a bypass line 10 which connects the pressure connections 15 to one another and is routed outside of the cylinder 2, ensures that the same pressure always prevails in the first and second pressure chambers 5, 6 when the piston 3 is positioned with its circumferential sealing surface between the two pressure connections 15 is arranged 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 an adjustment path x below that in the first Pressure chamber 5 opening pressure connection 15 of the second pressure connection line 20 is arranged.
  • 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 goal is to keep the force acting on the piston 3 so low that fingers are prevented from being trapped, for example, at a given system pressure of 6 bar, which is applied via the pressure connections 15, 16 to the two chambers 5, 6 is given, a maximum piston rod diameter of 16.9 mm can be determined in order to ensure a "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 of 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 in turn 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 the first pressure chamber 5 and out of the cylinder 2 via this.
  • the piston rod 4 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.
  • the diameter of the piston rod 4 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.
  • 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 displacement 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 16 and an additional pressure connection line 26 to a third valve 27, via which an overpressure 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)

Claims (14)

  1. Disposition avec une première soupape (17), une deuxième soupape (18), une troisième soupape (27) et un vérin à tige de piston pneumatique ou hydraulique (1) avec un cylindre (2) et un premier piston (3.1) mobile dans sa direction longitudinale, qui est couplé avec une tige de piston (4) dépassant du cylindre (2) et un volume logé dans le cylindre (2) se divise en une première chambre de pression (5), à travers laquelle la tige de piston (4) s'étend hors du cylindre (2), et une deuxième chambre de pression (6), dans laquelle les première et deuxième chambres de pression (5, 6) sont reliées de manière fluidique entre elles par l'intermédiaire d'une dérivation (7) qui fait partie d'une première conduite de raccordement de pression (19) et comprennent chacune un raccord de pression (15) qui peut être prévu dans une paroi cylindrique du cylindre (2) et par l'intermédiaire duquel les chambres de pression (5, 6) peuvent être alimentés en une pression de fluide au moyen de la première soupape (17) reliée avec la première conduite de raccordement de pression (19) et dans laquelle un premier côté (8) du premier piston (3.1) limite la première chambre de pression (5) et un deuxième côté (9), opposé au premier côté (8), du premier piston (3.1), qui présente une surface plus petite par rapport au premier côté (8), limite la deuxième chambre de pression (6), dans laquelle la tige de piston (4) s'étend à partir du premier piston (3.1) sur toute la longueur aussi bien de la première chambre de pression (5) que de la chambre de pression (6) à travers la chambre de pression (5, 6) respective, dans laquelle la tige de piston (4) présente, dans la première chambre de pression (5), un diamètre plus faible que dans la deuxième chambre de pression (6), dans laquelle, à une course de déplacement du piston (x) verticalement au-dessus du raccord de pression (15) de la deuxième chambre de pression (6), est disposé un autre raccord de pression (25) par l'intermédiaire duquel la deuxième soupape (18), reliée avec l'autre raccord de pression (25) et une deuxième conduite de raccordement de pression (20) peut mettre à disposition une sollicitation de pression de la deuxième chambre de pression (5, 6) indépendamment de la première soupape (17), dans laquelle la tige de piston (4) s'étend du premier piston (3.1) à travers un élément de séparation (23), qui sépare de manière fluidique la deuxième chambre de pression (6) d'une troisième chambre de pression (21) du cylindre (2), vers la troisième chambre de pression (21) et comprend, à son extrémité, un deuxième piston (3.2) qui sépare de manière fluidique la troisième chambre de pression (21) d'une quatrième chambre de pression (22) du cylindre (2), dans laquelle la quatrième chambre de pression (22) est reliée par l'intermédiaire d'un autre raccord de pression (16) et d'une conduite de raccordement de pression (26) supplémentaire avec la troisième soupape (27), par l'intermédiaire de laquelle une surpression de fluide peut être générée dans la quatrième chambre de pression (22), de façon à ce qu'une force exercée sur le deuxième piston (3.2) déplace le deuxième piston (3.2) avec la tige de piston (4) et le premier piston (3.1) verticalement vers le bas.
  2. Disposition selon la revendication 1, dans laquelle la chambre de pression (21) présente une pression ambiante et est pour cela ventilée et/ou purgée par l'intermédiaire d'une soupape (24), de préférence insonorisée, vers l'environnement du vérin à tige de piston (1).
  3. Disposition selon l'une des revendications 1 ou 2, dans laquelle 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) de la dérivation (7), raccordée à des raccords de pression (15) des première et deuxième chambres de pression (5, 6), qui peuvent être réalisés dans une paroi du cylindre (2).
  4. Disposition selon la revendication 3, dans laquelle la conduite de dérivation (10) est disposée, au moins sur une partie de sa longueur et de préférence sur toute sa longueur, à l'extérieur du cylindre (2).
  5. Disposition selon l'une des revendications 3 ou 4, dans laquelle la conduite de dérivation (10) comprend une soupape unidirectionnelle (11) de préférence un clapet anti-retour qui est passant dans la direction d'écoulement du fluide, de la deuxième chambre de pression (6) vers la première chambre de pression (5).
  6. Disposition selon l'une des revendications 3 à 4, dans laquelle la conduite de dérivation (10) est raccordée à la deuxième chambre de pression (6) par l'intermédiaire du raccord de pression (15) de la deuxième chambre de pression (6).
  7. Disposition selon l'une des revendications 3 à 6, dans laquelle la conduite de dérivation (10) est raccordée à la première chambre de pression (5) par l'intermédiaire du raccord de pression (15) de la première chambre de pression (5).
  8. Disposition selon l'une des revendications 3 à 7, dans laquelle le premier piston (3.1) présente une position de butée dans laquelle la tige de piston (4) dépasse d'une longueur maximale dans le cylindre (2) et une circonférence étanche (12) du premier piston (3.1), par l'intermédiaire de laquelle le premier piston (3.1) s'appuie de manière étanche sur la circonférence interne (13) du cylindre (2), ferme ou passe par-dessus un raccord de pression (15) de la deuxième chambre de pression (6), par l'intermédiaire duquel la conduite de dérivation (10) est raccordée à la deuxième chambre de pression (5).
  9. Disposition selon la revendication 8, dans laquelle, dans la position de butée, la quatrième chambre de pression (22) présente un volume minimal dans lequel débouche l'autre raccord de pression (16).
  10. Disposition selon la revendication 8 ou 9, dans laquelle la circonférence étanche (12) du premier piston (3.1) ferme ou passe par-dessus le raccord de pression (15) de la conduite de dérivation (10) débouchant dans la deuxième chambre de pression (6) de manière ininterrompue sur la course de déplacement du piston (x), se terminant dans la position de butée, du premier piston (3.1).
  11. Disposition selon la revendication 10, dans laquelle la course de déplacement du piston (x) représente jusqu'à 10 mm, de préférence jusqu'à 8 mm et plus particulièrement de préférence jusqu'à ou exactement 4 mm et/ou est déterminée par les dimensions de la circonférence étanche (12) dans la direction longitudinale.
  12. Disposition selon l'une des revendications 3 à 11, dans laquelle la conduite de dérivation (10) comprend au moins deux conduites partielles (14) branchées parallèlement qui comprennent chacune une soupape unidirectionnelle (11), de préférence un clapet anti-retour, qui sont passantes dans la direction de la deuxième chambre de pression (6) vers la première chambre de pression (5).
  13. Disposition selon l'une des revendications précédentes, dans laquelle la différence de surface entre les deux côtés (8, 9) du premier piston (3.1) génère, à une pression donnée, une force exercée sur le premier piston (3.1) de 150 N maximum et de préférence de 135 N maximum.
  14. Disposition selon l'une des revendications précédentes, dans laquelle l'élément de séparation (23) est conçu comme un double joint d'étanchéité, avec un premier et un deuxième joints d'étanchéité qui sont disposés à une certaine distance entre eux dans la direction longitudinale du piston et qui entourent la tige de piston (4).
EP19187867.7A 2019-07-23 2019-07-23 Ensemble avec un vérin pneumatique ou hydraulique Active EP3770444B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES19187867T ES2929764T3 (es) 2019-07-23 2019-07-23 Disposición con un cilindro del vástago de pistón neumático o hidráulico
EP19187867.7A EP3770444B1 (fr) 2019-07-23 2019-07-23 Ensemble avec un vérin pneumatique ou hydraulique
PCT/DE2020/100591 WO2021013296A1 (fr) 2019-07-23 2020-07-03 Vérin pneumatique ou hydraulique de tige de piston

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19187867.7A EP3770444B1 (fr) 2019-07-23 2019-07-23 Ensemble avec un vérin pneumatique ou hydraulique

Publications (2)

Publication Number Publication Date
EP3770444A1 EP3770444A1 (fr) 2021-01-27
EP3770444B1 true EP3770444B1 (fr) 2022-08-31

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EP19187867.7A Active EP3770444B1 (fr) 2019-07-23 2019-07-23 Ensemble avec un vérin pneumatique ou hydraulique

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EP (1) EP3770444B1 (fr)
ES (1) ES2929764T3 (fr)
WO (1) WO2021013296A1 (fr)

Family Cites Families (5)

* 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

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ES2929764T3 (es) 2022-12-01
EP3770444A1 (fr) 2021-01-27
WO2021013296A1 (fr) 2021-01-28

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