EP2981458B1 - Machine à gouvernail - Google Patents

Machine à gouvernail Download PDF

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Publication number
EP2981458B1
EP2981458B1 EP14712692.4A EP14712692A EP2981458B1 EP 2981458 B1 EP2981458 B1 EP 2981458B1 EP 14712692 A EP14712692 A EP 14712692A EP 2981458 B1 EP2981458 B1 EP 2981458B1
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EP
European Patent Office
Prior art keywords
hydraulic
pump
rudder system
rudder
mechanical
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
EP14712692.4A
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German (de)
English (en)
Other versions
EP2981458A1 (fr
Inventor
Roland Körner
Ulrich Stäuble
Swen Jörissen
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.)
ThyssenKrupp Marine Systems GmbH
Original Assignee
ThyssenKrupp Marine Systems 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 ThyssenKrupp Marine Systems GmbH filed Critical ThyssenKrupp Marine Systems GmbH
Publication of EP2981458A1 publication Critical patent/EP2981458A1/fr
Application granted granted Critical
Publication of EP2981458B1 publication Critical patent/EP2981458B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
    • B63H25/06—Steering by rudders
    • B63H25/08—Steering gear
    • B63H25/12—Steering gear with fluid transmission
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H20/00—Outboard propulsion units, e.g. outboard motors or Z-drives; Arrangements thereof on vessels
    • B63H20/08—Means enabling movement of the position of the propulsion element, e.g. for trim, tilt or steering; Control of trim or tilt
    • B63H20/12—Means enabling steering
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
    • B63H25/06—Steering by rudders
    • B63H25/08—Steering gear
    • B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
    • B63H25/18—Transmitting of movement of initiating means to steering engine
    • B63H25/22—Transmitting of movement of initiating means to steering engine by fluid means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
    • B63H25/06—Steering by rudders
    • B63H25/08—Steering gear
    • B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
    • B63H25/26—Steering engines
    • B63H25/28—Steering engines of fluid type
    • B63H25/30—Steering engines of fluid type hydraulic
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/025—Installations or systems with accumulators used for thermal compensation, e.g. to collect expanded fluid and to return it to the system as the system fluid cools down
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/045—Compensating for variations in viscosity or temperature
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F15B2211/50527—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves using cross-pressure relief 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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
    • F15B2211/7054—Having equal piston areas
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input

Definitions

  • the invention relates to a steering machine with a hydraulic circuit.
  • both rowing machines are known, which are electrically driven and rowing machines, which are hydraulically driven.
  • Purely electrically operated rowing machines have an advantage in terms of energy efficiency compared to hydraulically operated rowing machines. However, they need a gear with high reduction or a drive with high torque.
  • hydraulic drives For larger actuating forces almost exclusively hydraulic drives are used.
  • an actuator for example, plunger cylinder, double-acting hydraulic cylinder or rotary cylinder are used, which are operated in an open hydraulic circuit.
  • a hydraulic pump provides the required hydraulic pressure.
  • the actuation of the actuators is usually via continuous valves.
  • the hydraulic pumps are either operated continuously, or, to save energy, temporarily turned off, in which case the required hydraulic energy is taken from previously charged storage.
  • a variable displacement pump for operation in an open hydraulic circuit of a steering gear is for example in DE 1 036 088 described.
  • the WO 2010 / 052777A1 shows a hydraulically operated steering gear, in which a hydraulic pump is driven by an electric motor.
  • the GB 365939 shows a hydraulically operated rudder system in which two hydraulic pumps are driven differently by an electric motor, and a pneumatic motor and work together.
  • the invention has the object to increase the energy efficiency in a hydraulic circuit of a rowing machine.
  • a steering machine in particular for an underwater vehicle, is provided with a hydraulic circuit in which a pump is arranged, wherein the pump is a motor-driven reversible hydraulic pump and the hydraulic circuit is a closed circuit.
  • a hydraulic pump driven by a compressed air-driven motor or a compressed-air motor as an auxiliary drive for a hydraulic pump are provided in the hydraulic circuit.
  • the steering machine according to the invention combines the advantages of the two types of drive described above, d. H. the advantages of energy efficiency that could previously be achieved with electric drives and the advantages of the high actuating forces that can be achieved with hydraulic drives.
  • a combination of electrically driven hydraulic pump in a closed hydraulic circuit is provided, which achieves an increased energy efficiency in a simple manner.
  • the energy efficiency is essentially based on the fact that a closed hydraulic circuit is used, so that hydraulic energy must be supplied only if the rudder is to be moved.
  • a compressed air motor As an auxiliary drive to use a compressed air motor is particularly advantageous because submarine side compressed air is available anyway and this is also available when other energy sources fail.
  • compressed air drives are inexpensive and easy to install, since no closed circuits and no return lines are required.
  • the basic idea of the solution according to the invention is thus, on the one hand to provide a closed hydraulic circuit to keep the energy to be minimized, on the other hand to provide a reversible pump to drive avoiding complex valve controls in two directions, that is, using the same hydraulic circuit and To be able to move the rudder in one direction and optionally also in the other direction without elaborate valve arrangements via a double-acting or two single-acting actuating cylinder.
  • the hydraulic pump acts directly on a hydraulic cylinder arrangement, in particular to a double-acting cylinder of the same piston area and with double-sided piston rod.
  • the hydraulic pump is driven by a servomotor, in particular a servomotor operable in four-quadrant operation.
  • a servomotor operable in four-quadrant operation.
  • a delivered volume of the hydraulic pump is directly proportional to the cylinder stroke of the hydraulic cylinder assembly.
  • Such a design is then the number of drive motor revolutions, which is in fixed proportion to the pivoting movement of the rudder and thus a very simple control is possible.
  • a rudder is connected via a coupling device, in particular via a connecting rod, with the hydraulic cylinder arrangement.
  • the movement of the rudder is controllable via the rotational movement of the servomotor, in particular the position of the rudder over the number of rotations of the servomotor adjustable.
  • valves for hydraulic locking of the rudder at pump standstill in the hydraulic circuit can also be provided valves for hydraulic locking of the rudder at pump standstill in the hydraulic circuit.
  • a hydraulic locking of the rotor is advantageous because then no provision must be made on the drive side in order to apply this counterforce, that is, no electrical or other energy is required at pump standstill.
  • a supply line of the hydraulic pump cooler may be arranged to dissipate heat loss.
  • Such a cooling of the hydraulic fluid in the supply line of the hydraulic pump is especially effective to prevent cavitation.
  • a second pump is provided in the hydraulic circuit, which in a second power range, in particular in a high-power range, is switchable.
  • Fig. 1 is a schematic representation of a closed hydraulic circuit 1, in which a operated by a servo motor 5 reversible hydraulic pump 4 acts directly on a double-acting cylinder 2 with double-sided piston rod 6.
  • the two-sided piston rod diameter are the same size.
  • a connecting rod, not shown here, also not shown here rudder is hinged to the piston rod 6 (see Fig. 2 ) and the rudder movement is controlled exclusively by the movement of the servomotor 5. To reverse the direction of the servo motor 5 and the hydraulic pump 4 are stopped and started again in the opposite direction.
  • the hydraulic circuit 1 of this closed system is designed for a specific system pressure. If the hydraulic fluid in the hydraulic circuit 1 expands due to temperature, the system pressure may increase and exceed permissible pressures. On the other hand, if the system pressure decreases due to temperature and / or leakage, cavitation phenomena can occur on pumps and valves and the function of the system can no longer be fulfilled.
  • a hydraulic accumulator 3 is connected to both sides of a hydraulic working cylinder 2, which is biased by the system pressure.
  • the gas volume must not be too small, otherwise there will be large system pressure fluctuations as a result of temperature fluctuations.
  • the embodiment shown here is a "soft" system. At an external load, the piston of the working cylinder 2 gives way.
  • Fig. 2 is a hydraulic circuit diagram of a rowing machine 17. As can be seen here, it is a closed hydraulic circuit 1, in which a hydraulic pump 4 acts directly on a double-acting cylinder 2 with double-sided piston rod 6, wherein the piston rod diameter are the same size. Via a coupling device 18, which is designed here as a connecting rod, a rudder 19 is coupled for movement with the working cylinder 2.
  • the hydraulic pump 4 is reversible and is driven by the servo motor 5. To reverse the direction of the servo motor 5 and the hydraulic pump 4 are stopped and started again in the opposite direction.
  • the hydraulic pump 4 is designed here as a screw pump, since it has the advantage of Pulsationsarmut.
  • the pump 4 is designed to reach the nominal torque under nominal load for starting already. In addition, small numbers of revolutions should be realized for acoustic reasons. This can be achieved by so-called torque motors, designed as permanently excited synchronous motors. These have a starting torque in the amount of the rated torque.
  • a motor controller 20 is provided, which is designed for the four-quadrant operation.
  • the rudder movement is thus controlled exclusively by the rotational movement of the servomotor 5. If no rudder adjustment required, the rudder 19 is locked in its position by holding valves 21, 21 '(check valves) hydraulically. As a result, no engine torque is applied at standstill and energy is saved. In addition to the pipe losses cause the holding valves 21, 21 'a loss. For low-loss operation, these are low-resistance in the open state.
  • pressure limiting valves 22, 22 ' are arranged in the hydraulic circuit 1 to protect the engine 5 and pump 4, which limit the oil pressure and thus the engine torque.
  • a cooler 23 is provided close to the pump 4.
  • the diving pressure In underwater vehicles, it is customary to guide the piston rod 6 of the working cylinder 2 through a pressure body 24. Thus, the diving pressure additionally acts on the piston rod 6. In order to act on the working cylinder 2 regardless of the depth no other forces than the rudder torque, the diving pressure is also performed on the opposite side 25 of the piston rod 6, whereby lower actuating forces and pump pressures and thus lower Loss of the pump 4 due to internal leakage can be realized.
  • the maximum required pump power also on two units of different capacity to be divided.
  • small rudder deflections are sufficient at low adjustment speeds.
  • a pump with higher capacity is connected in parallel. Since a smaller pump unit less leakage losses, less friction and the power controller of a smaller motor has lower electrical losses compared to a large electric motor, the steering machine 17 can be operated even more efficient. In addition, there is redundancy.
  • a pneumatic motor 26 which drives the pump 4 in the event of failure of the servomotor 5 or the control.
  • compressed air is readily and instantaneously available to an underwater vehicle from compressed air tanks 27.
  • the pneumatic motor 26 is, however, usefully only then connected to the pump 4, which is indicated by the dashed line 28 when the compressed air motor 26 is acted upon by compressed air.
  • This circuit is known from compressed air starters for diesel engines.
  • the rudder 19 is then set either manually or electrically via a 3/4-way valve 29.
  • the control of the steering machine 19 is performed as follows.
  • the desired rudder angle or the travel s of the working cylinder 2 is predetermined.
  • a controller 30 for the path specification 31 determines the deviation from the actual value and specifies the direction of rotation and rotational speed of the motor 5.
  • the controller 30 has the task of avoiding a swing around the setpoint.
  • the working cylinder 2 is equipped with a displacement sensor 32 for measuring distance.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (11)

  1. Machine à gouvernail (17), en particulier pour un sous-marin, comprenant un circuit hydraulique (1) dans lequel est disposée une pompe (4), la pompe (4) étant une pompe hydraulique (4) inversable entraînée par un moteur, le circuit hydraulique (1) étant un circuit fermé, caractérisée en ce qu'un moteur à air comprimé (26) est en outre prévu dans le circuit hydraulique (1) en tant qu'entraînement auxiliaire pour la pompe hydraulique (4).
  2. Machine à gouvernail (17) selon la revendication 1, caractérisée en ce que la pompe hydraulique (4) agit directement sur un agencement de cylindre hydraulique, en particulier sur un cylindre de travail (2) à double action, de même surface de piston (16) et avec une tige de piston (6) des deux côtés.
  3. Machine à gouvernail (17) selon la revendication 1 ou 2, caractérisée en ce que la pompe hydraulique (4) est entraînée par un servomoteur (5), en particulier un servomoteur (5) pouvant fonctionner en mode à quatre quadrants.
  4. Machine à gouvernail (17) selon la revendication 2 ou 3, caractérisée en ce qu'un volume refoulé par la pompe hydraulique (4) est directement proportionnel à la course du cylindre de l'agencement de cylindre hydraulique.
  5. Machine à gouvernail (17) selon l'une quelconque des revendications 2 à 4, caractérisée en ce qu'un gouvernail (19) est connecté par le biais d'un dispositif de couplage (18), en particulier par le biais d'une bielle, à l'agencement de cylindre hydraulique.
  6. Machine à gouvernail (17) selon la revendication 5, caractérisée en ce que le mouvement du gouvernail (19) peut être commandé par le biais du mouvement de rotation du servomoteur (5), en particulier la position du gouvernail (19) peut être ajustée par le nombre de tours du servomoteur (5) .
  7. Machine à gouvernail (17) selon l'une quelconque des revendications 5 ou 6, caractérisée en ce que des soupapes (21, 21') pour le verrouillage hydraulique du gouvernail (19) lors de l'arrêt de la pompe sont prévues dans le circuit hydraulique (1) .
  8. Machine à gouvernail (17) selon l'une quelconque des revendications 1 à 7, caractérisée en ce que des soupapes de limitation de la pression (22, 22') sont prévues dans le circuit hydraulique (1).
  9. Machine à gouvernail (17) selon l'une quelconque des revendications 2 à 8, caractérisée en ce que dans le cas d'une sollicitation unilatérale d'une tige de piston (6) de l'agencement de cylindre hydraulique avec une basse pression, une extrémité éloignée opposée de la tige de piston (6) peut également être sollicitée avec une basse pression.
  10. Machine à gouvernail (17) selon l'une quelconque des revendications 1 à 9, caractérisée en ce qu'au moins un radiateur (23) pour évacuer la chaleur perdue est disposé dans une conduite d'alimentation de la pompe hydraulique (4).
  11. Machine à gouvernail (17) selon l'une quelconque des revendications 1 à 10, caractérisée en ce qu'une deuxième pompe qui peut être commutée dans une deuxième plage de puissance, en particulier dans une plage de haute puissance, est prévue dans le circuit hydraulique (1).
EP14712692.4A 2013-04-02 2014-03-27 Machine à gouvernail Active EP2981458B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013205807.1A DE102013205807A1 (de) 2013-04-02 2013-04-02 Rudermaschine
PCT/EP2014/056189 WO2014161769A1 (fr) 2013-04-02 2014-03-27 Mécanisme de gouvernail

Publications (2)

Publication Number Publication Date
EP2981458A1 EP2981458A1 (fr) 2016-02-10
EP2981458B1 true EP2981458B1 (fr) 2019-11-06

Family

ID=50382464

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14712692.4A Active EP2981458B1 (fr) 2013-04-02 2014-03-27 Machine à gouvernail

Country Status (4)

Country Link
EP (1) EP2981458B1 (fr)
DE (1) DE102013205807A1 (fr)
ES (1) ES2766929T3 (fr)
WO (1) WO2014161769A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3067252A1 (fr) * 2015-03-13 2016-09-14 BAE Systems PLC Système hydraulique
WO2016146969A1 (fr) * 2015-03-13 2016-09-22 Bae Systems Plc Système hydraulique
DE102019108476A1 (de) * 2019-04-01 2020-10-01 Moog Gmbh Hydrauliksystem für Stabilisatorantrieb
CN110486337A (zh) * 2019-09-11 2019-11-22 三一海洋重工有限公司 多腔油缸闭式液压系统及工程机械
CN114868005B (zh) * 2021-06-01 2023-05-23 中国矿业大学(北京) 伪三轴保压加载装置及利用其进行伪三轴保压加载实验的方法
CN113341766B (zh) * 2021-06-10 2024-04-12 哈尔滨理工大学 一种加载与消扰臂长可调的电液负载模拟器

Citations (2)

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Publication number Priority date Publication date Assignee Title
GB365939A (en) * 1931-05-22 1932-01-28 John Hastie & Company Ltd Improvements in or relating to hydraulic ships' steering gear
DE1036088B (de) * 1956-04-16 1958-08-07 Licentia Gmbh Wegabhaengig ferngesteuerte hydraulische Ruderanlage fuer Schiffe, Flugzeuge od. dgl.

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DE7511765U (de) * 1975-09-04 Wedekind K Handstelltrieb für die Ruderanlage von Segel· und Motorfahrzeugen
US2892310A (en) * 1954-02-17 1959-06-30 Mercier Jean Automatic follow-up system for successive application of power sources
US3986475A (en) * 1974-06-17 1976-10-19 Heiser Kenneth R Control arrangement
DE2923130A1 (de) * 1979-06-07 1980-12-11 Hermes Hans Steuerungstech Hydraulische ruderanlage
JPS58133999A (ja) * 1982-02-01 1983-08-09 Mitsubishi Heavy Ind Ltd 単ラム型油圧式舵取装置
US5427045A (en) * 1993-09-30 1995-06-27 Teleflex (Canada) Ltd. Steering cylinder with integral servo and valve
US5509369A (en) * 1994-10-11 1996-04-23 Nautamatic Marine Systems Small watercraft automatic steering apparatus and method
US5481871A (en) * 1995-03-02 1996-01-09 Teleflex (Canada) Ltd. Hydraulic steering system with spool pressure equalization
FR2831226B1 (fr) * 2001-10-24 2005-09-23 Snecma Moteurs Actionneur electrohydraulique autonome
US7254945B1 (en) * 2006-02-27 2007-08-14 Kayaba Industry Co., Ltd. Operate check valve and hydraulic driving unit
US8046122B1 (en) * 2008-08-04 2011-10-25 Brunswick Corporation Control system for a marine vessel hydraulic steering cylinder
WO2010052777A1 (fr) * 2008-11-06 2010-05-14 三菱重工業株式会社 Dispositif de gouvernail de bateau
US8589027B2 (en) * 2010-12-02 2013-11-19 Furuno Electric Company Limited Steering assist system and method using autopilot device
JP2012136148A (ja) * 2010-12-27 2012-07-19 Kawasaki Heavy Ind Ltd 舶用操舵装置及び舶用操舵方法

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB365939A (en) * 1931-05-22 1932-01-28 John Hastie & Company Ltd Improvements in or relating to hydraulic ships' steering gear
DE1036088B (de) * 1956-04-16 1958-08-07 Licentia Gmbh Wegabhaengig ferngesteuerte hydraulische Ruderanlage fuer Schiffe, Flugzeuge od. dgl.

Also Published As

Publication number Publication date
EP2981458A1 (fr) 2016-02-10
DE102013205807A1 (de) 2014-10-02
WO2014161769A1 (fr) 2014-10-09
ES2766929T3 (es) 2020-06-15

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