EP3864300A1 - Système hydraulique destiné à être utilisé sous l'eau, comprenant un entraînement de réglage hydraulique - Google Patents

Système hydraulique destiné à être utilisé sous l'eau, comprenant un entraînement de réglage hydraulique

Info

Publication number
EP3864300A1
EP3864300A1 EP19782999.7A EP19782999A EP3864300A1 EP 3864300 A1 EP3864300 A1 EP 3864300A1 EP 19782999 A EP19782999 A EP 19782999A EP 3864300 A1 EP3864300 A1 EP 3864300A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
cylinder
hydraulic cylinder
machine
chambers
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19782999.7A
Other languages
German (de)
English (en)
Other versions
EP3864300B1 (fr
Inventor
Alexandre ORTH
Gottfried Hendrix
Simone Karl
Oliver GERHARD
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3864300A1 publication Critical patent/EP3864300A1/fr
Application granted granted Critical
Publication of EP3864300B1 publication Critical patent/EP3864300B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—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
    • F15B15/1404—Characterised by the construction of the motor unit of the straight-cylinder type in clusters, e.g. multiple cylinders in one block
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B33/00—Sealing or packing boreholes or wells
    • E21B33/02—Surface sealing or packing
    • E21B33/03—Well heads; Setting-up thereof
    • E21B33/06—Blow-out preventers, i.e. apparatus closing around a drill pipe, e.g. annular blow-out preventers
    • 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
    • F15B15/18—Combined units comprising both motor and pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/004—Fluid pressure supply 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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
    • F15B2211/80—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

  • Hydraulic system for use under water with a hydraulic
  • the invention relates to a hydraulic system for use under water, in particular at great water depths, with a hydraulic actuator.
  • the hydraulic actuator is used in particular to operate underwater fittings.
  • the system preferably comprises a container which has an interior space which is provided to form a volume which is closed off from the surroundings and is intended to hold a hydraulic pressure fluid.
  • the system further comprises a hydraulic cylinder and at least one hydraulic machine, which are arranged inside the container.
  • the hydraulic system for use under water is particularly equipped with a redundant hydraulic actuator for manual (mechanical) actuation.
  • Such types of hydraulic systems are mainly used to move an element under water at depths of up to several thousand meters in connection with the extraction of oil and natural gas, mining, scientific inquiries, infrastructure projects or renewable energy projects.
  • process valves are located at great depths with which the volume flow of the medium to be extracted can be regulated or shut off.
  • An electrohydraulic system can be designed with an electrohydraulic actuator which comprises a container, in the interior of which a hydrostatic machine that can be operated at least as a pump and an electric machine that is mechanically coupled to the hydrostatic machine are arranged.
  • the main drive of the actuator is an electric motor that drives the pump and thus adjusts a hydraulic cylinder with a straight line movement.
  • the electric motor consumes considerable electrical energy, which, for example, must be brought in via submarine cables.
  • the actuator for example, adjusts large production valves for oil or gas wells that regulate the flow rate.
  • a process valve can also be operated manually by a robot, such as a Remote Operated Vehicle (ROV) or an Autonomous Underwater Vehicle (AUV), for example in an emergency, there is a manual interface on the container from which it starts a rod is coupled to a piston in the cylinder.
  • the rod can have a movement thread and can interact with an internally threaded and axially fixed screw nut that is rotated to actuate the process valve.
  • the disadvantage of this arrangement is the investment outlay. A large installation space is required here. In addition, the limited service life disturbs.
  • manual operation prevents frequent adjustment of a process valve during operation.
  • the mechanical arrangement is sensitive to shocks and vibrations that can be caused by the underwater vehicle.
  • a hydraulic system for use under water with a hydraulic actuator contributes to this, with a hydraulic cylinder and at least one hydraulic machine being present. At least one rotary drive device and the hydraulic machine are mechanically coupled for a common rotating movement. The hydraulic machine adjusted further at least the hydraulic cylinder.
  • the hydraulic cylinder has at least three cylinder chambers. In addition, a first hydraulic circuit and a second hydraulic circuit are available, which open into different cylinder chambers.
  • the hydraulic system presented here with the hydraulic actuator has the advantage that, in a structurally simple manner, a smaller installation space is combined with an increased service life. In particular, frequent adjustment by an underwater vehicle, for example a robot, is made possible. Finally, undesirable impacts and vibrations on the hydraulic cylinder, which can occur due to the underwater vehicle, are avoided.
  • Two hydraulic circuits with several cylinder chambers of a hydraulic cylinder are advantageously combined. Because the hydraulic cylinder has at least three cylinder chambers, two independent hydraulic circuits are assigned to the one hydraulic cylinder in a structurally elegant manner, so that different functions of the two circuits can be implemented by the same hydraulic cylinder.
  • the first hydraulic circuit preferably comprises the hydraulic cylinder and a first hydraulic machine and the independent second hydraulic circuit comprises the hydraulic cylinder and a second hydraulic machine, the hydraulic cylinder and the at least one hydraulic machine each being part of a hydrostatic transmission.
  • the hydrostatic transmission works on the displacement principle. As a rule, a driven hydraulic pump and the hydraulic cylinder are available.
  • the first hydraulic circuit with at least one cylinder chamber in the hydraulic cylinder is preferably set up as a normal working actuator and the second hydraulic circuit with two further cylinder chambers in the hydraulic cylinder as an emergency actuator.
  • the rotary drive device can be used both for the mechanical emergency adjustment of the hydraulic cylinder and for the permanent adjustment of the hydraulic cylinder in normal working operation.
  • one or the same piston of the hydraulic cylinder can be moved and moved along its travel axis with each hydraulic circuit.
  • the execution is in particular such that in the event that a (first) hydraulic circuit does not work (correctly), the other (second or further) hydraulic circuit can implement the movement.
  • the hydraulic cylinder expediently has at least four or five cylinder chambers.
  • a (first) hydraulic circuit with (first) two cylinder chambers and a (second) hydraulic circuit with (second) two cylinder chambers cooperate and also a pretensioning or resetting unit for the piston rod of the hydraulic cylinder in the fifth cylinder chamber is arranged.
  • Two cylinder chambers are preferably uncoupled from the working movement of the piston rod or the hydraulic cylinder. In this way, the wear of seals is reduced.
  • the hydraulic cylinder is advantageously a differential cylinder or a synchronous cylinder.
  • the two pressurized active surfaces on the piston are of different sizes. This results in different forces when moving in and out at the same operating pressure as well as different speeds with a constant volume flow.
  • Differential cylinders are inexpensive and have a high power density, which results from the high achievable forces and the large strokes in relation to the size of the cylinders.
  • the hydraulic cylinder is expediently designed with a longitudinally displaceable piston for adjusting a process valve.
  • the hydraulic cylinder preferably comprises a compression spring, for example a helical compression spring, for resetting the hydraulic cylinder.
  • the compression spring is supported at one end on the cylinder head and at the other end on the first piston or on a displaceable piston element.
  • the hydraulic cylinder is designed as a tandem cylinder.
  • the hydraulic cylinder is designed in such a way that two cylinders are connected to one another in such a way that the piston rod of one cylinder acts on the piston surface through the base of the second cylinder.
  • a container is preferably provided, in the interior of which the hydraulic cylinder and the at least one hydraulic machine are arranged. The container is in particular set up so that it is tight and durable against sea water even at great depth.
  • the rotary drive device is advantageously arranged outside the container and is set up for coupling to the hydraulic machine and for uncoupling from the hydraulic machine.
  • Two rotary drive devices are expediently arranged outside the container, the second rotary drive device being provided for the normal actuation of the hydraulic cylinder and the first rotary drive device for the emergency actuation (bridging) of the hydraulic cylinder.
  • a remote-controlled underwater vehicle advantageously includes the rotary drive device.
  • the rotary drive device is preferably a torque tool of an underwater robot.
  • the rotary drive device expediently comprises an electric motor.
  • the electric motor can be provided outside the container (in the seawater area). It is possible to provide a separate electric motor within the container as a working drive.
  • a coupling device is preferably provided between the rotary drive device and the hydraulic machine.
  • the mechanically driven, hydraulic emergency actuator is advantageously integrated into a 3-chamber or 5-chamber cylinder.
  • the 3-chamber or 5-chamber cylinder has at least one hydraulic safety release function (three chambers) and possibly a hydrostatic drive (five chambers).
  • two chambers are provided for the hydraulic emergency actuator, which can be operated mechanically from the outside.
  • a device for arrangement under water and for controlling a conveyable volume flow of a gaseous or liquid medium is proposed, which is designed with a process valve.
  • the process valve has a process valve housing and a process valve slide with which the volume can be controlled.
  • a hydraulic cylinder is also provided, which is assigned to the process valve housing and is movable with the process valve slide.
  • the device also has a hydraulic system with a hydraulic actuator, a rotary drive device being arranged on a remote-controlled underwater vehicle, which drives a hydraulic pump which adjusts the hydraulic cylinder.
  • the hydraulic cylinder has at least three cylinder chambers, a first hydraulic circuit and a second hydraulic circuit being present, which open into different cylinder chambers.
  • FIG. 1 shows a side view of the device with the process valve closed, with a hydraulic cylinder with three cylinder chambers, one cylinder chamber being assigned to a displaceable piston and two cylinder chambers being assigned to a stationary piston;
  • FIG. 2 enlarges the hydraulic cylinder according to FIG. 1 in detail
  • 3 shows an embodiment of the hydraulic cylinder with five cylinder chambers, wherein two cylinder chambers are assigned to a first displaceable piston, one cylinder chamber to a displaceable piston element and two cylinder chambers to a stationary piston
  • Fig. 4 an embodiment like Figure 3, but two
  • Cylinder chambers are assigned to a second displaceable piston
  • Fig. 5 an embodiment like Figure 3, but two
  • Cylinder chambers are assigned to a displaceable piston element
  • Fig. 6 an embodiment like Figure 3, but two
  • Cylinder chambers are each assigned a displaceable sealing sleeve
  • Fig. 7 an embodiment like Figure 3, but two
  • Cylinder chambers are each assigned to a sliding sealing washer
  • Fig. 8 an embodiment like Figure 3, but two
  • Cylinder chambers are assigned to a third displaceable piston
  • the exemplary embodiments of a hydraulic system shown in the figures have a process valve 1 with a process valve housing 2, through which a process valve channel 3 passes, which is continued at its mouths through pipes (not shown) and in which a gaseous or liquid medium flows from the sea floor a part of a drilling tower protruding from the sea or to a drilling ship.
  • the direction of flow is indicated by arrow 4.
  • a cavity is formed in the process valve housing 2, which crosses the process valve channel 3 and in which a process valve slide 5 with a flow opening 6 can be moved transversely to the longitudinal direction of the process valve channel 3.
  • the process valve channel 3 and the flow opening 6 in the process valve slide 5 do not overlap. Process valve 1 is therefore closed.
  • Process valve 1 In a state (not shown), the flow opening 6 and the process valve channel 3 largely overlap. Process valve 1 is almost completely open.
  • a process valve of the type shown and the use described should, on the one hand, be able to be operated in a controlled manner and, on the other hand, should also contribute to safety by quickly and reliably assuming a position in the event of a fault which corresponds to a safe state. In the present case, this safe state is a closed process valve.
  • the process valve 1 is actuated by a compact hydraulic system 7, which is arranged under water directly on the process valve 1. It is sufficient that only one electrical cable 8 leads from the hydraulic system 7, for example to the surface of the sea or another higher-level electrical control system located under water.
  • the hydraulic system 7 shown as an exemplary embodiment has a container 9 which is attached to the process valve housing 2 on an open side, so that there is an interior space 10 which is closed off from the surroundings and is filled with a hydraulic pressure fluid as the working medium.
  • the container 9 has on its open side an inner flange with which it is screwed to the process valve housing 2.
  • a circumferential seal 11, which is inserted into a circumferential groove of the process valve housing 2, is arranged radially outside the screw connections between the inner flange of the container 9 and the process valve housing 2.
  • the container 9 is pressure-compensated for the ambient pressure prevailing under water (sea water region 12).
  • a diaphragm 14 is tightly clamped in a pressure compensator 13 in an opening in the container wall.
  • There are holes in the lid so that the space between membrane 14 and lid is part of the environment and is filled with sea water.
  • the interior 10 is therefore sealed off from the surroundings by the membrane 14.
  • the membrane 14 is on its first surface facing the interior 10 by the pressure in the interior 10 and on its second surface facing the cover, which is approximately the same size as the first surface, by the pressure in the Environment prevails, acts upon and always seeks to adopt a position and form in which the sum of all the forces acting on it is zero.
  • a hydraulic cylinder 15 with a cylinder housing 16, which is closed at the end by a cylinder bottom 17 and a cylinder head 18, with a piston which can be displaced in the longitudinal direction of the cylinder housing 16 inside the cylinder housing 16, as shown in FIG. 2 19 and with a first displaceable piston rod 24 which is fixedly connected to the piston 19 and projects on one side away from the piston 19 and which passes through the cylinder head 18 in a sealed manner and in a manner not shown.
  • the gap between the piston rod 24 and the cylinder head 18 is sealed by two seals (not shown) arranged in the cylinder head 18 at an axial distance from one another.
  • the process valve slide 5 is attached to the free end of the piston rod 24.
  • a second displaceable piston rod 25 which is fixedly connected to the piston 19 and projects to the other side from the piston 19 and which is guided in a sealed manner and passes through a first cylinder inner wall 39.1 and through a second cylinder inner wall 39.2.
  • the piston 19 divides the interior of the cylinder housing 16 into a first cylinder chamber 32 on the cylinder bottom and a spring chamber 37 on the cylinder head, the volume of which depends on the position of the piston 19. 19.1 denotes a first end face of the piston 19 and 19.2 denotes a second end face of the piston 19. 23.1 denotes a first end face of the piston rod 23 and 23.2 denotes a second end face of the piston rod 23.
  • a compression spring 38 is housed, which coaxially surrounds the piston rod 24 and is clamped between the cylinder head 18 and the piston 19, thus acting on the piston 19 in a direction into which the piston rod 24 is inserted and the process valve slide 5 for closing the Process valve 1 is moved.
  • the end region 25.1 of the second displaceable piston rod 25 facing the cylinder base 17 is (partially) designed as a hollow cylinder with a hollow cylinder wall 25.2 and a hollow cylinder base 25.3, which is opposed by a closing first cover element 42 with an annular cross section.
  • a stationary piston 22 (connected to the cylinder housing 16), from the first end face 22.1 of which there is a stationary piston rod 28 starting and penetrating the opening of the cover element 42, extends to the cylinder base 17.
  • With 65 a first cylinder interior cavity and with 66 a second cylinder interior cavity is designated.
  • the hydraulic cylinder 15 has three cylinder chambers, namely a first cylinder chamber 32, a fourth cylinder chamber 35 and a fifth cylinder chamber 36.
  • the two cylinder chambers 35 and 36 are part of a hydraulic lock-up arrangement for an emergency, while the cylinder chamber 32 is responsible for the normal operation of the hydraulic cylinder 15 serves. In this way, an emergency actuator is integrated in a 3-chamber cylinder.
  • the two cylinder chambers 35 and 36 which are additional to the cylinder chamber 32, are provided for the hydraulic emergency actuator which can be actuated mechanically from the outside. With 44 and 45 channels in the fixed piston rod 28 are designated, which convey hydraulic fluid into and out of the cylinder chambers 35 and 36, respectively.
  • a and B directional arrows for the directions of movement of the piston rod 23 are designated.
  • the directions of movement A and B apply in the same way to the displaceable piston 19 which is fixedly connected to the piston rod 23 and to the end region 25.1 which is fixedly connected to the piston rod 23.
  • a hydraulic machine 48 which can be operated as a pump with two delivery directions.
  • the hydraulic machine 48 has a first pressure or suction connection 52 and a second pressure or suction connection 53.
  • hydraulic fluid drawn in by the hydraulic machine 48 can be conveyed via the pressure connection 52 to the cylinder chambers.
  • pressure fluid can be sucked out of the cylinder chambers via the hydraulic machine 48 (see FIG. 9 in this regard).
  • a rotary drive device 54 is mechanically coupled to the hydraulic machine 48 for a common rotary movement, for example via a shaft 56.
  • the shaft 56 transmits a torque from the rotary drive device 28 to the hydraulic machine 48.
  • the rotary drive device 54 is located outside the container 9. It is for example by a remote-controlled underwater vehicle 72 (ROV) or a robot and preferably has an electric motor as the rotary drive device 54. So that the process valve 1 can be actuated by a robot, such as an ROV, an interface 57 is provided on the container 9, from which the shaft 56 is coupled to the hydraulic machine 48 in the interior 10.
  • ROV remote-controlled underwater vehicle 72
  • the second independent hydraulic circuit 69 shown in detail in FIG. 9 is shown in simplified form in FIG. 1 as an emergency actuator.
  • the first hydraulic circuit 68 shown in FIG. 9 can be used as a normal working actuator.
  • the working actuator can be realized by a combination of the hydraulic pump with an additional electric motor (not shown).
  • FIGS. 3 to 8 there are five cylinder chambers each, that is to say a first cylinder chamber 32, a second cylinder chamber 33, a third cylinder chamber 34, a fourth cylinder chamber 35 and a fifth cylinder chamber 36.
  • the two cylinder chambers 35 and 36 are part of a hydraulic lock-up arrangement for an emergency, while the cylinder chambers 32, 33 and 34 are provided for the normal operation of the hydraulic cylinder 15. All variants of the five cylinder chambers can be used for hydraulic cylinders 15 with three cylinder chambers (see FIGS. 2 and 9).
  • a first cylinder chamber 32, a fourth cylinder chamber 35 and a fifth cylinder chamber 36 are present in all of the exemplary embodiments according to FIGS. 1 to 9.
  • a second cylinder chamber 33 and a third cylinder chamber 34 are additionally provided, which are used for the normal working operation of the hydraulic cylinder 15.
  • Figure 3 shows an embodiment of the hydraulic cylinder 15 with five cylinder chambers 32, 33, 34, 35, 36, two cylinder chambers 32, 33 a first displaceable piston 19, a cylinder chamber 34 a displaceable piston element 29 and two cylinder chambers 35, 36 the stationary Pistons 22 are assigned.
  • the cylinder chamber 34 is delimited by a first hollow piston 29.2 and a third cylinder inner wall 39.3.
  • the displaceable piston element 29 consists of a hollow cylinder-like composite element 29.1, at the two end regions of which a first hollow piston 29.2 or a second hollow piston 29.3 are attached, the openings of which are coaxially penetrated by the first displaceable piston rod 24.
  • the piston element 29 can be displaced in a sealed manner in the direction of the arrows C and D on the piston rod 24.
  • 24.1 is a covenant Approach to the piston rod 24, which - when moving the piston rod 24 in directions A and B - can move the piston element 29 in directions C and D by engagement with the hollow piston 29.1 and 29.2.
  • FIG. 4 illustrates an embodiment in which two cylinder chambers 35, 36 are assigned to a second displaceable piston 20.
  • a differential cylinder is formed in which the two pressurized active surfaces on the piston 20, that is to say the first end surface 20.1 and the second end surface 20.2, are of different sizes.
  • FIG. 5 illustrates an embodiment, wherein two cylinder chambers 35, 36 are assigned to the displaceable piston element 29.
  • a cylinder inner chamber partition 40 is provided, which is provided between the housing wall of the cylinder housing 16 and the composite element 29.1 and the hollow pistons 29.2 and 29.3.
  • a third inner cylinder cavity 67 is formed, which is enclosed by a cup-shaped second cover element 43.
  • FIG. 6 shows an embodiment, wherein two cylinder chambers 35 and 36 are each assigned to a sealing sleeve 30.1 or 30.2 which can be displaced in the direction of the arrows E, F.
  • the sealing sleeves 30.1 and 30.2 are arranged coaxially and sealed to the first piston rod 24 and the second piston rod 25, respectively.
  • the cylinder chambers 35 and 36 are formed between the sealing sleeves 30.1 and 30.2 and the opposite cylinder inner walls 39 and 39.2.
  • FIG. 7 shows an embodiment similar to FIG. 6, but in which - instead of the sealing sleeves 30.1 and 30.2 - there are two hollow cylindrical sealing disks 31.1 and 31.2 which can be displaced in the direction of the arrows G and H.
  • FIG. 8 illustrates an embodiment in which two cylinder chambers 35 and 36 are assigned to a third displaceable piston 21.
  • a fourth displaceable piston rod 27 extends from the piston 21 and is connected to the second hollow piston 29.3.
  • a cylinder tube 41 is arranged in the spring chamber 37, in the inner cavity of which the piston 21 together with the piston element 29 in the direction of the arrows C and D is movable. With 46 and 47 channels for the flow of hydrofluid into the cylinder chambers 35 and 36 are designated.
  • FIG. 9 illustrates a circuit diagram of a hydraulic system with the hydraulic cylinder 15 designed as a tandem cylinder and three cylinder chambers 32, 35 and 36 (see FIG. 10) and two hydraulic circuits 68 and 69.
  • the circuit 68 is an open circuit with the pump constant displacement volume of a conveying direction and a direction of rotation designed second hydraulic machine 49.
  • the pump has a pressure connection 50 and a suction connection 51.
  • 61 to 64 are directional seated valves and 70.1 and 70.2 are non-return valves with no pressure drop.
  • the circuit 69 is a closed circuit with the first hydraulic machine 48 designed as a pump with two delivery directions.
  • the pump has a first pressure or suction connection 52 and a second pressure or suction connection 53.
  • a hydraulic accumulator for example piston accumulator
  • 70.3 and 70.4 are non-return valves with no pressure drop
  • 71.1 and 71.2 are non-return valves with pressure drop.
  • a third displaceable piston rod is designated.
  • the volume flow flows from the outflow side of the hydraulic cylinder 15 to a container (not shown).
  • the volume flow from the outflow side of the hydraulic cylinder 15 is again fed directly to the suction line of the pump; the volume flow flowing back is equal to the volume flow flowing in.
  • the two circuits 68 and 69 each form a hydrostatic transmission, comprising the hydraulic cylinder and the hydraulic machines 48 and 49 designed as pumps.
  • Two rotary drive devices 54, 55 are arranged outside the container 9, the second rotary drive device 55 being set up as a normal working actuator for the hydraulic cylinder 15 and the first rotary drive device 54 as an emergency actuator for the hydraulic cylinder 15.
  • FIGS. 3 to 8 there are five cylinder chambers 32, 33, 34, 35, 36 and a spring chamber 37 with a compression spring 38.
  • three cylinder chambers 32, 35, 36 and a spring chamber 37 with a compression spring 38 are provided.
  • the spring chamber 37 is configured as a further (fourth) cylinder chamber without a compression spring 38.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Abstract

L'invention concerne un système (7) hydraulique destiné à être utilisé sous l'eau, comprenant un entraînement de réglage hydraulique. Un cylindre hydraulique (15) et au moins une machine hydraulique (48, 49) sont prévus. Au moins un dispositif d'entraînement en rotation (54, 55) et la machine hydraulique (48, 49) sont couplés mécaniquement pour un déplacement en rotation conjoint, et la machine hydraulique (48, 49) ajuste au moins le cylindre hydraulique (15). Le cylindre hydraulique (15) comporte au moins trois chambres (32, 33, 34, 35, 36) de cylindre. Un premier circuit hydraulique (68) et un deuxième circuit hydraulique (69) sont prévus. L'invention comprend par ailleurs un dispositif destiné à être agencé sous l'eau et servant à commander un flux volumique pouvant être refoulé. Le système hydraulique destiné à être utilisé sous l'eau est mis au point en particulier avec un entraînement de réglage redondant pour un actionnement manuel (mécanique).
EP19782999.7A 2018-10-08 2019-10-02 Système hydraulique à usage subaquatique avec un actionneur hydraulique Active EP3864300B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018217150.5A DE102018217150A1 (de) 2018-10-08 2018-10-08 Hydraulisches System für den Einsatz unter Wasser mit einem hydraulischen Stellantrieb
PCT/EP2019/076687 WO2020074338A1 (fr) 2018-10-08 2019-10-02 Système hydraulique destiné à être utilisé sous l'eau, comprenant un entraînement de réglage hydraulique

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EP3864300A1 true EP3864300A1 (fr) 2021-08-18
EP3864300B1 EP3864300B1 (fr) 2023-07-26

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US (1) US11448242B2 (fr)
EP (1) EP3864300B1 (fr)
CN (1) CN112789412B (fr)
BR (1) BR112021006462A2 (fr)
DE (1) DE102018217150A1 (fr)
WO (1) WO2020074338A1 (fr)

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CN114148937B (zh) * 2021-12-14 2023-03-10 新乡市新华液压机械有限公司 一种新型液压缸

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DE102018217150A1 (de) 2020-04-09
US20210381531A1 (en) 2021-12-09
CN112789412A (zh) 2021-05-11
BR112021006462A2 (pt) 2021-07-06
EP3864300B1 (fr) 2023-07-26
US11448242B2 (en) 2022-09-20
WO2020074338A1 (fr) 2020-04-16
CN112789412B (zh) 2024-03-08

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