EP1915288A1 - Propulseur de bateau - Google Patents

Propulseur de bateau

Info

Publication number
EP1915288A1
EP1915288A1 EP06761262A EP06761262A EP1915288A1 EP 1915288 A1 EP1915288 A1 EP 1915288A1 EP 06761262 A EP06761262 A EP 06761262A EP 06761262 A EP06761262 A EP 06761262A EP 1915288 A1 EP1915288 A1 EP 1915288A1
Authority
EP
European Patent Office
Prior art keywords
surface drive
drive
propeller
shaft
housing
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
EP06761262A
Other languages
German (de)
English (en)
Other versions
EP1915288B1 (fr
Inventor
Peter A. Muller
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP1915288A1 publication Critical patent/EP1915288A1/fr
Application granted granted Critical
Publication of EP1915288B1 publication Critical patent/EP1915288B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H1/00—Propulsive elements directly acting on water
    • B63H1/02—Propulsive elements directly acting on water of rotary type
    • B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
    • B63H1/14—Propellers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H1/00—Propulsive elements directly acting on water
    • B63H1/02—Propulsive elements directly acting on water of rotary type
    • B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
    • B63H1/14—Propellers
    • B63H1/18—Propellers with means for diminishing cavitation, e.g. supercavitation
    • B63H2001/185—Surfacing propellers, i.e. propellers specially adapted for operation at the water surface, with blades incompletely submerged, or piercing the water surface from above in the course of each revolution

Definitions

  • the invention relates to a surface drive for watercraft, which is attached to the stern of a watercraft, according to the preamble of the first claim.
  • the propeller thrust is taken in Z-drives in an underwater part of thrust bearing and partly forwarded via trim cylinder and partly on the upper water part of the vessel, as described in US Patent 3,589,204, while in surface drives the propeller thrust, with rigid drives directly and with swiveling Drives over joints, practically straightforward effect on the stern of the vessel, as described, inter alia in US Pat. No. 4,645,463.
  • the propeller requires a surface drive a corresponding distance from the stern of the water, as the propeller efficiency drops when reversing, the closer the propeller is placed at the stern of the vessel, since a pitch of the propeller circumference leads the thrust of the propeller directly to the rear wall and thus generates a flow loss.
  • a related technical solution can be found in US Patent 4,371,350.
  • the introduction of a variable pitch propeller is problematic, because the space is not as generous as in Z-drives as described in US Patent 6,250,979 or by a hollow shaft design as it is known for shaft drives in the large ship, see WO 8602901, which causes high costs.
  • the load changes on the adjustment mechanism when entering and exiting the wings at each propeller rotation by the changing sogelspindel whobardlich respectable and require a very solid construction, as well as a high safety standard with respect to the sash position in case of hydraulic failure.
  • the invention has for its object to integrate at a surface drive for water vehicles of the type mentioned a self-locking or autohemmenden adjustment for a variable pitch with odometer to experience in a sudden Wirkzylinderhydraulikausfall no uncontrolled Propellersteistrs Sung or trim and the shaft housing, as well as the side thereof fastened flaps, as hydrodynamic lift elements and for water spray channeling, as well as to improve the maneuverability of a watercraft. Furthermore, with the swiveling surface drive, the engine exhaust gases are to flow directly into the propeller blades in every pivoting position.
  • the core of the invention is that the self- or autohemmende adjustment mechanism for the variable pitch is integrated in a tower-like container on the shaft housing, that the engine exhaust guide for the propeller ventilation is housed on the shaft housing, that the shaft housing can produce a defined buoyancy component and lying laterally from the shaft housing flaps Vehicle floor extension, propeller tunnel and as a flow deflector when reversing and for lateral opening and closing a transverse thruster tunnel, mounted laterally mounted transverse thrusters.
  • Fig. 1 is a schematic lateral cross-section through a marine propulsion, in particular a surface drive with integrated exhaust guide, which is pivotable in all directions and has a double joint system, which is connected to a suggestively sketched drive motor and drives a variable pitch propeller at the opposite end of the ship propulsion with a spacial separation lead, which is placed in the ship propulsion
  • Fig. 2 is a schematic plan view of the ship propulsion and propeller with the swivel cylinder and the bogie for the swivel device
  • FIG. 3 shows a schematic cross section through the adjuster with propeller shaft passage and with a displacement measuring means attached to the adjustment thread or on the effective adjustment means or on the adjusting gear wheel
  • Fig. 4 is a schematic, viewed from the rear of the cross section through the ship propulsion with flanged hydrodynamic lift surfaces a) for port, b) for
  • Fig. 5 is a schematic side cross-section through a marine propulsion, which is located in an additional rear part, which is connected to the stern of the boat by elastic vibration and or damping means and the
  • FIG. 6 is a schematic side cross-sectional view of a marine propulsion located in an auxiliary tail, wherein during a reverse maneuver, the engine exhaust and cooling water outlets are routed through lateral openings in the drive housing or between the watercraft body and the auxiliary tail
  • Fig. 7 is a schematic representation of the flap system in lowered and in the raised state
  • Fig. 8 is a three-quarter view of an additional tail with integrated transverse thruster and the flap system for closing the Querstrahlrudertunnel matgangs when not in use.
  • Fig. 9 is a schematic, viewed from behind cross section through the tunnel flap system
  • Fig. 9a is a schematic plan view of the tunnel flap system
  • Fig. 10 is a schematic, viewed from the rear of the cross section through the baffle system
  • Fig. 10a is a schematic plan view of the baffle system
  • FIG. 11 is a schematic lateral cross section through a lockable active cylinder with integrated displacement measuring means
  • Fig. 1 shows a schematic lateral cross section through a ship propulsion, in particular a surface drive 1 consisting of a shaft housing
  • the container 3 is an easy-to-open, service-friendly part and when closed, completely waterproof and firmly connected to the shaft housing 2. It is formed as streamlined as possible, so that the engine exhaust and coolant discharge A can flow through the channel 6 of the channel housing 6a unhindered.
  • the engine exhaust and coolant removal A are introduced in the pivotable surface drive 2 with corresponding flexing room reserves or via a flexible coupling, not shown, and by the Abgaskrümmrohrs 7, 8 from the engine in the channel 6.
  • Surface drive 1 are attached to the upper attachment 10 and to the lateral attachment 11 on the one hand and on the other side to the stern 12 of the vessel at the attachments 13a, 13b.
  • the swivel cylinder 9a is used for trimming the surface drive 1 and allows, in particular by the immersion depth variation of the propeller blades 17a in the water, the corresponding variation of
  • the engine drive power is delivered via the gear 14 either directly to the propeller shaft 15, or by means of a second drive shaft 16 to the propeller 17.
  • the propeller shaft 15 is in the shaft housing 2 - not shown - stored and the thrust forces of the propeller 17 are packaged over the axial bearing
  • the thrust forces of the propeller 17 are introduced as shown in FIG 2 via the bearing pin 29 and pivot 30 into the housing 22 and transmitted via elastic damping elements 46 to the stern 12 of the watercraft.
  • the drive shaft 16 has a length compensation element 19, as well as a second cardan or homokinetic joint 21 and serves for further vibration damping of the drive, as well as for spatial, freer positioning and or for softer mounting of the motor. 8
  • the shaft housing 2 has a propeller protection 23, as well as a hydrodynamic lift surface 24 so that it acts like a trim flap when approaching the watercraft and helps to lower the nose of a launching vehicle as quickly as possible, finally the vehicle in a flat and favorable travel angle convert.
  • a propeller cover 25 is provided on the duct housing 6a. This can be arcuate designed as a tunnel or a simple T or similar. In the case of the channel housing 6a made of plastic material, the propeller cover 25 can also directly over the Anflanschelement
  • 25a be attached to the container 3, or be as an integral part of the cover 55 of the side flap 50.
  • Fig. 2 shows a schematic plan view of the surface drive 1, the
  • the first gimbal or homokinetic joint 20 is centric to the rotary and lifting frame 28 and the bearing pin 29 and pivot 30 which are housed in the housing 22 and is used for low-friction Swiveling of the surface drive 1.
  • FIG. 3 shows a schematic cross section through the adjuster 4 integrated in the shaft housing 2.
  • An effective adjustment means 31 which is a hydraulic or electric motor or a linear drive activated via an angle drive can be with rack or the like, drives a gear 33, which is connected via a connecting shaft 34 with the eccentric 35, so that at this over the change in height in the rotation of the eccentric, the distance between the eccentric 35 and the Wegmessstoff 36 are electrically detected can.
  • the displacement measuring means can be, for example, an inductive measuring sensor,
  • the gear 33 drives the Verstelltechnikrad 37, which is connected to a self-locking Verstellgewinde 38, at the end of which Verstellaxiallager 39 is located and which directs the stationary axial forces in the rotating axial forces, which takes over the axial housing 40 and thus the mechanical connection via the connecting elements 41 to the adjustment mechanism 5 of the variable pitch 17 secures.
  • the parts 37,38,39 have a Kem trimlass so that the propeller shaft 15 without contact, or stored accordingly, can rotate.
  • the gear 33 is mounted axially as possible without play, while the Verstelliererad 37 together with the self-locking thread 38 and the Verstellaxiallager 39, and the axial housing 40 and connecting element 41 moves axially, as indicated by the arrows.
  • the measuring cone 42 also with a Kem trimlass, which is designed as a measuring ramp to measure at this point the Verstellhub, instead of the eccentric
  • the displacement measuring means 36 may be installed laterally of the Verstelliererades 37 in the shaft housing 2.
  • the Verstellhubteil serves to slope identification of the propeller blades 17a. Allen in common with respect to the position of the position measuring means 36 is that they are laterally from the propeller shaft 15.
  • the container 3 which includes parts of the adjuster 4, also serves for the supply and discharge 32 of the Wirkverstellschs 31, and for carrying the Wegmessvons 43 and or as Anflanschelement 25a for the propeller cover 25.
  • the core of the adjuster 4 is the adjustment of the propeller blades 17a and Self- or
  • Fig. 4 shows a schematic, viewed from the rear of the cross section through the shaft housing 2 with various flanged hydrodynamic lift surfaces 24, so with one and the same shaft housing design, this completed for a) port, b) for starboard and c) for single drive by means of hydrodynamic lift surfaces can be.
  • the surfaces can thus be quickly and inexpensively configured for the various types of vessels and operations, i. with narrower or wider areas, shorter or longer versions.
  • the hydraulic lift surface 24 allows the vessel to maintain a more stable position in the swell, as well as in the acceleration phase of the vehicle from a standstill, to reduce the lift of the bow.
  • Fig. 5 shows a schematic lateral cross section through the surface drive 1, which is located in an additional rear portion 44 which is connected to the watercraft stern 12 by elastic vibration and damping means 45, wherein the pivot cylinder trim 9a, and the pivot cylinder steering 9b, not shown on Additional rear part 44 is attached.
  • the vibration and damping means 45 By installing the entire surface drive 1 in an additional rear portion 44, is practically achieved by the vibration and damping means 45, between the stern 9 of the watercraft and the additional tail 44 a decoupling of the mechanical vibrations on the vessel, especially when using a second joint 21 and related drive shaft 16, so that the engine 8 can be stored according to comfort.
  • a possible deflection of the drive shaft 16 can be achieved by means of a suitable sealing element 47, such as e.g. a bellows and a conventional shaft seal, are included.
  • Fig. 6 shows a schematic side cross-section through the surface drive 1, which is located in an additional rear portion 44, wherein during reverse maneuvers, the engine exhaust and coolant discharge A via lateral openings 26 in the channel housing 6a, due to the adjustable by means of Wirkverstellstoffs 31 Umlenkklappe 27, are deflected or and that the engine exhaust and coolant discharge A between the stern 9 and the additional stern 44 are guided by means of an outlet guide 48.
  • the deflecting flap 27 is connected via the not shown coupling of the propeller reversing or reversing gear.
  • the exhaust guide 48 may also be useful during normal driving, since it ventilates the underwater part of the auxiliary rear part 44 and thus reduces its frictional resistance in the water. Furthermore, it can also be used to achieve the Venturi effect and to help dissipate the engine exhaust gases more effectively.
  • Fig. 7 shows a schematic representation of the side flap 50 with the cover 55 in the flat and thus travel and rest position, as well as in the raised position R as used for the reverse drive. This can be as
  • Transverse-jet tunnel 77 and the side flap 50 which has the cover 54 and the tunnel flap part 50a.
  • the tunnel flap portion 50a prevents the passage of water through the transverse jet tunnel 77 during travel and protects the transverse jet propeller from any spray caused by the propeller blades 17a.
  • the side flap 50 is raised and clears the path for the flow through the transverse thruster tunnel.
  • FIG. 9 shows a schematic cross-section viewed from the rear through a one-part side flap 50, which has a tunnel-shaped cover 55 as a water spray protection and has an overlap 54 of the shaft housing 2 for connection to the rotary elements 51.
  • a possible position of the flap holder 53 is listed. It is understandable that the overlap 54 also by a corresponding
  • 9a shows a schematic plan view of a one-piece side flap 50 with the
  • Fig. 10 shows a schematic, viewed from the rear of the cross section through the two-part variant of the side flap 50, which as a water spray protection a
  • Side cover 56 wherein the upper water spray cover by the propeller cover 25 in the form of e.g. a simple T, or arcuate to the side cover 56 can be formed.
  • 10 a shows a schematic plan view of the two-part side flap 50 with the side cover 56, the flap holder 53 and rotary elements 51.
  • FIG. 11 shows a schematic lateral cross section through an effective cylinder 57, which functions for the swivel cylinder 9a, 9b, effective displacement means 31, FIG. Lifting means 52 is transferable.
  • the working cylinder comprises the cylinder 57 a, the locking means 57 b and the displacement measuring means 36.
  • the cylinder 57a comprises at least the fluid cylinder housing 58, reciprocating piston 59 and piston rod 60.
  • a fluid cylinder housing 58 is a reciprocating piston 59 with a hollow bored, non-rotating piston rod 60 and a recessed spindle nut 61 mounted thereon.
  • the locking means 57b comprises at least the hollowed-out shaft 60, spindle nut 61. Wheel 62, spindle 63, lock chuck 65, anti-rotation element 66, disengaging part 67 and spring 68.
  • the fluid cylinder housing 58 is a module part Z, in which an axially secured, freely rotating wheel 62 is located, on one side of a spindle 63 is mounted , which fits into the spindle nut 61 and practically extends to the length of the stroke of the reciprocating piston 59 in the piston rod 60 into it.
  • a spline shaft 64 is mounted which projects into a locking chuck 65 and which is guided in a module part Y.
  • a rotational locking elements 66 provided, rotationally secured disengaging part 67 which presses by means of a spring 68 against the locking chuck 65.
  • the effective cylinder 57 is closed by a fastening element 69.
  • Radially on the wheel 62 which has an eccentric shape, similar to a camshaft, there is a displacement measuring means 36.
  • a pressure medium is to be introduced through the inlet opening 70 into the chamber 71 and simultaneously via the unlocking 72 a pressure medium in the lock chamber 73, which pushes the release member 67 against the spring 68 and thus axially displaces and the connection to the lock chuck 65 releases.
  • This allows the reciprocating piston 59 and the piston rod 60 to move axially, which leads to a rotation of the guided in the spindle nut 61 spindle 63, wherein the locking chuck 65 rotates about the spline shaft 64 empty, as well as the wheel 62 rotates axially play, which by its eccentric Form one
  • Display changes in measured value at the distance measuring means 36 and forwards them to the electronics or display device.
  • pressure is simultaneously discharged from the counter chamber 74 via the outlet opening 75.
  • the displacement measuring means 36 which controls the directional control valves via a controller 76, not shown, the pressure medium in the chamber 71 is stopped, the pressure in the lock chamber 73 is released, which due to the relaxation of the spring 68, leads to an axial return of the non-rotating disengagement part 67 , Due to the mechanical connection between the release part
  • the spindle 63 can not rotate and thus the reciprocating piston 59 is fully locked via the spindle nut 61.
  • the nature of the mating surfaces of the release member 67 and the opposing barrier liner 65 may be e.g. have a sintered surface or toothing and may be flat or conical.
  • the action cylinder 57 also allows for security unlocking, e.g. at ground touch of the surface drive 1 at too hard placement and possible overloading of the propeller guard 23, the piston rod 60 of the swing cylinder 9a can be quickly unlocked mechanically, so that serious damage to the surface drive 1 can be prevented by means of a ratchet forming the connecting surfaces of the release 67 and chuck 65.
  • the spring rate may be possible as an overload protection emergency retraction of the piston 60 despite lock.

Landscapes

  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Exhaust Silencers (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Transmission Devices (AREA)
  • Gear Transmission (AREA)
  • Valve Device For Special Equipments (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

L'invention concerne un propulseur de surface (1) d'un bateau. Ce propulseur comprend un dispositif de réglage (4) autobloquant ou verrouillable dans le carter d'arbre (2). Ce propulseur comprend un boîtier à canal (6a) articulé au carter d'arbre (2) et destiné à l'évacuation des gaz d'échappement du moteur et de l'eau de refroidissement (A) devant l'hélice (17), une surface de poussée verticale (24) hydrodynamique et des volets latéraux (50) et au moins un cylindre mécanique (57) verrouillable.
EP06761262A 2005-08-05 2006-08-04 Propulseur de bateau Not-in-force EP1915288B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH13022005 2005-08-05
PCT/CH2006/000411 WO2007016804A1 (fr) 2005-08-05 2006-08-04 Propulseur de bateau

Publications (2)

Publication Number Publication Date
EP1915288A1 true EP1915288A1 (fr) 2008-04-30
EP1915288B1 EP1915288B1 (fr) 2010-10-27

Family

ID=37440834

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06761262A Not-in-force EP1915288B1 (fr) 2005-08-05 2006-08-04 Propulseur de bateau

Country Status (5)

Country Link
US (1) US8323063B2 (fr)
EP (1) EP1915288B1 (fr)
AT (1) ATE486006T1 (fr)
DE (1) DE502006008187D1 (fr)
WO (1) WO2007016804A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105059515B (zh) * 2015-08-25 2017-07-04 江龙船艇科技股份有限公司 表面桨换气***
US9849955B1 (en) * 2017-01-03 2017-12-26 Fred Kiekhaefer Marine surface propulsion device
EP3695946B1 (fr) * 2019-02-14 2022-04-13 LM Wind Power A/S Aligneur de moule pour moule de coque de pale d'éolienne
FR3096654B1 (fr) 2019-05-29 2021-06-11 Univ Savoie Mont Blanc Hélice à pas variable automatique

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2415183A (en) * 1943-03-22 1947-02-04 Brett D Law Boat propelling and steering unit
BE755521A (fr) 1969-09-08 1971-02-01 Outboard Marine Corp Dispositif de propulsion marin
US3933116A (en) * 1974-12-02 1976-01-20 Thomas F. Adams Unitary propelling and steering assembly for a power boat
DE3005682C2 (de) 1980-01-28 1982-11-11 Escher Wyss Gmbh, 7980 Ravensburg Schiffantriebsanlage
US4645463A (en) 1980-04-07 1987-02-24 Arneson Howard M Marine outdrive apparatus
US4544362A (en) * 1982-03-17 1985-10-01 Arneson Howard M Marine outdrive apparatus
DE3502964A1 (de) 1984-11-17 1986-05-28 Sulzer-Escher Wyss GmbH, 7980 Ravensburg Verfahren und vorrichtung zur einstellung der propellerfluegel eines hydraulisch betaetigten verstellpropellers
GB2167133B (en) 1984-11-19 1988-04-07 Sanden Corp Scroll-type rotary fluid-machine
US4790782A (en) * 1988-02-26 1988-12-13 Brunswick Corporation Balanced marine surfacing drive
IT1216545B (it) 1988-04-05 1990-03-08 Fabio Buzzi Dispositivo ad effetto cavitazionale per eliche di natanti con carena planante o semiplanante.
US5863230A (en) * 1996-09-26 1999-01-26 Morrison; Douglas M. Universal marine drive apparatus and uses thereof
DE19936949C1 (de) 1999-08-05 2001-01-25 Peter Mueller Bootsantrieb mit einem Verstellpropeller
WO2001047770A1 (fr) * 1999-12-28 2001-07-05 Fles Nenad Helice a pas variable partiellement submergee montee sur une traverse profilee

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007016804A1 *

Also Published As

Publication number Publication date
ATE486006T1 (de) 2010-11-15
WO2007016804A1 (fr) 2007-02-15
EP1915288B1 (fr) 2010-10-27
US20080261468A1 (en) 2008-10-23
DE502006008187D1 (de) 2010-12-09
US8323063B2 (en) 2012-12-04

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