WO2011051233A2 - Moteur de gouvernail - Google Patents

Moteur de gouvernail Download PDF

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Publication number
WO2011051233A2
WO2011051233A2 PCT/EP2010/066077 EP2010066077W WO2011051233A2 WO 2011051233 A2 WO2011051233 A2 WO 2011051233A2 EP 2010066077 W EP2010066077 W EP 2010066077W WO 2011051233 A2 WO2011051233 A2 WO 2011051233A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
stator
rowing machine
machine according
seal
Prior art date
Application number
PCT/EP2010/066077
Other languages
German (de)
English (en)
Other versions
WO2011051233A3 (fr
Inventor
Eckard Dahlweg
Edwin Van Buren
Original Assignee
Van Der Velden Barkemeyer 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 Van Der Velden Barkemeyer Gmbh filed Critical Van Der Velden Barkemeyer Gmbh
Publication of WO2011051233A2 publication Critical patent/WO2011051233A2/fr
Publication of WO2011051233A3 publication Critical patent/WO2011051233A3/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
    • B63H25/14—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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/54—Other sealings for rotating shafts
    • F16J15/545—Other sealings for rotating shafts submitted to unbalanced pressure in circumference; seals for oscillating actuator
    • 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
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type

Definitions

  • the invention relates to a rowing machine for a rudder of a ship according to the preamble of claim 1.
  • Such a rowing machine comprises a stator to be fixedly mounted on a ship's hull and a rotor rotatably mounted on the stator about an axis of rotation which is connected to a rudder post and which can be rotated relative to the stator for moving the rudder post.
  • the present invention relates in particular to rowing machines in the manner of hydraulically operated rotary-wing steering machines.
  • the stator and rotor include a space in which a fluid, such as a hydraulic oil, is located.
  • a fluid such as a hydraulic oil
  • wings are arranged which divide the space into at least two subspaces, wherein for driving the steering machine, the hydraulic fluid is conveyed from one subspace to another subspace.
  • Embodiments of such rotary-wing rowing machines are known, for example, from DE-PS 1 176 514 and DE-OS 25 44 679.
  • these rowing machines several vanes are respectively arranged on the stator and on the rotor, which divide a space formed between the stator and the rotor into a plurality of spaces filled with a fluid.
  • the fluid may be delivered between the subspaces to generate a torque on the rotor by changing the pressure ratios in the subspaces.
  • the seals for generating a contact pressure via a supply line can be connected to one or more of the subspaces such that the seals are acted upon by the fluid in the subspaces at a predetermined pressure of, for example, 100 bar and in this way against the assigned wall are pressed.
  • the fluid pressure in the sub-chambers thus acts via the supply lines to the seals for generating a contact pressure.
  • Object of the present invention is to provide a rowing machine for a rudder of a ship that reliably seals the fluid-filled subspaces against each other even if the pressure conditions in one or more of the subspaces change spontaneously, for example due to a pressure drop.
  • a check valve is arranged in the supply line, which is designed and provided to maintain the contact pressure of the seal at a pressure drop in at least one of the subspaces.
  • the present invention is based on an arrangement in which a seal is connected to a wing for sealing two subspaces against each other via a supply line with one or more of the subspaces and is acted upon by the fluid located in the sub-chambers with a contact pressure. About the contact pressure a sealing transition between the wing and associated wall and thus a seal of the subspaces against each other is created.
  • the idea of the present invention is to arrange in the supply line, via which the seal communicates with one or more compartments, a check valve which maintains the contact pressure of the seal if, in one or all subspaces, the pressure of the fluid suddenly drops.
  • the check valve thus provides a security measure available, which even if it comes to a pressure drop in the subspaces of the rowing machine, still guaranteed a sealing transition between the subspaces.
  • the check valve prevents the contact pressure of the seal from being reduced if the pressure in the partial spaces is reduced, for example, as a result of a leak.
  • each of the wings in the rowing machine, for example, three wings each can be arranged on the stator and the rudder, which divide the space in total into six subspaces. This allows a rudder, with a rudder at a maximum (due to the width of the wings a little less) than +/- 60 ° can be made, for example, in a real version by +/- 45 °.
  • Each of the wings in this case has a seal, which ensures that the transitions between the individual compartments are sealed and a fluid can pass only in predetermined ways, for example via a pump from one compartment to another, but not between the wing and the associated wall therethrough.
  • Conceivable in this context are also rowing machines, which are provided on the stator and rotor per one or two wings. Such rowing machines allow a correspondingly larger angle of the rudder. In a rowing machine with two wings on the rotor and stator, for example, an adjustment angle of +/- 65 ° (due to the wing width) may be possible. In an advantageous embodiment, four blades can be provided on the stator and four blades rotor. Since the power that can be generated by the rower on the rotor increases due to the increase in the total vane area with the number of vanes, a four-rotor rudder on the rotor and stator can provide a higher force. At the same time, the achievable setting angle is reduced to ideally +/- 45 ° and realistically, including the finite wing widths, to approx. +/- 35 °.
  • a seal on a wing of the stator is pressed, for example, radially inwardly against the associated wall of the rotor for sealing engagement.
  • a seal on a blade of the rotor is pressed radially outwardly against an associated wall of the stator. In each case, it is ensured by the contact pressure that the transition between the wing and the associated wall is sealed.
  • an additional seal can be arranged on the at least one wing, which is pressed by the contact pressure axially to the rotation axis sealing against an associated portion.
  • This axially movable arranged on the wing of the rotor seal serves to seal against a bottom plate and / or ceiling plate of the stator in the axial direction, so that the wings on the rotor in all directions sealingly along the associated portions of the stator along.
  • two seals may be arranged, which are parallel to each other and are each acted upon via one and the same supply line or via different supply lines with a contact pressure. It is also conceivable to provide three or more seals in order to increase the tightness of the transition between the wing and the associated wall.
  • the seal is designed as a self-compensating seal such that when worn on the seal, the seal is tracked in the direction of the contact pressure and is pressed with constant contact pressure to an associated section.
  • the seal when abrasion due to friction of the seal at an associated portion of the rotor or stator is formed, the seal is pushed in the direction of the associated portion, ie in the radial or axial direction (depending on which direction Seal against the rotor or stator is pressed) is pressed towards the associated portion, so that the contact pressure with which the seal rests sealingly against the associated portion is constant.
  • the seal is mounted for this purpose radially or axially displaceable on the wing, so that they can be tracked according to abrasion.
  • the seals may be made of plastic, in particular polyethylene, for example the so-called UHMW-PE ("Ultrahigh-Molecular Weight Polyethylene”) .UHMW-PE is a durable and abrasion-resistant thermoplastic material.
  • the supply line via which the seal is in communication with the fluid located in the sub-chambers and is pressurized, may for example be formed as a channel on both sides of each radially inwardly from the stator inwardly or radially outwardly of the rotor in a wing Outlet opens and is in this way with two adjacent to a wing subspaces in contact.
  • a check valve may be arranged, which causes a fluid from the subspace can enter the supply line, conversely, a fluid from the supply lines but can not flow into the subspaces. In this way, the check valves also prevent a direct fluid exchange between the adjoining the wing subspaces.
  • the stator may comprise a housing pot, a bottom plate and a ceiling plate, which together with a rotor body of the rotor enclose the fluid-filled space.
  • the rotor can with his Rotor body be mounted between the bottom plate and the top plate of the stator, with suitable seals to seal the transition between the rotor body and bottom plate or rotor body and ceiling plate are provided.
  • the rotor is mounted on the base plate and / or the ceiling plate of the stator via a bearing ring arranged between the rotor and the stator and serving as an axial bearing.
  • the bearing ring is composed of individual, circumferentially successive segments, which can be connected to the bottom plate, for example, bolted to the bottom plate and realize a Rudertraglager over which the rudder is held in the axial direction of the rudder stock on the hull.
  • the segments can also, in an advantageous embodiment, be arranged loosely between the rotor and the stator. Loose here is to be understood that the bearing ring is not firmly connected to either the rotor or the stator, so not bolted to the rotor or the stator, for example, is screwed.
  • Such a rowing machine for a rudder of a ship has a stator fixedly mounted on a ship's hull and a rotor rotatably mounted on the stator about a rotation axis on.
  • at least one bearing ring which is arranged between the rotor and the stator and serves as an axial bearing, is provided which is composed of individual segments which follow one another in the circumferential direction.
  • a lower bearing ring between the bottom plate of the stator and the rotor then forms the Rudertraglager over which the rudder is held in the axial direction of the rudder shaft on the hull.
  • a bearing ring is bolted as a support to the bottom plate of the stator for axially supporting the rotor, which supports the rotor in the axial direction in stock.
  • the bronze ring is thus firmly connected to the stator.
  • a bearing ring consisting of individual segments is used here, which form the bearing ring when they are arranged on the bottom plate. It is not necessary in this case for the segments to adjoin one another without a gap. Between the segments can also be a (Small) distance, without affecting the storage effect is impaired.
  • a thrust bearing ring can be arranged between the rotor and the top plate and rotor and bottom plate of the stator.
  • the bearing ring may be coated for advantageous storage with a sliding material having PTFE (polytetrafluoroethylene) or consists of PTFE.
  • PTFE polytetrafluoroethylene
  • PTFE has in a conventional manner advantageous frictional properties and ensures a low-friction bearing of the rotor on the stator. In principle, however, other sliding materials with advantageous friction properties can be used.
  • the bearing ring can also be made of copper or a copper alloy or contain copper or a copper alloy.
  • the bearing ring is made of a metal-plastic composite material, in particular a composition containing steel, sintered bronze and polyoxymethylene (so-called POM).
  • the bearing ring depressions for example in the form of countersinks or blind holes, have on its surface, receive the lubricant and are designed such that an advantageous distribution of a lubricant is reached over the surface of the bearing ring.
  • a thrust bearing bearing ring can also be provided between the rotor and the stator as a radial bearing, for example, loosely arranged bearing ring, which supports the rotor in the radial direction relative to the stator as a radial sliding bearing.
  • two such bearing rings can be used, one of which supports the rotor relative to the ceiling plate and the other the rotor relative to the bottom plate of the stator.
  • the radial bearing rings may be formed of the same material as the bearing serving as a thrust bearing.
  • the rotor is rotated to drive a rudder shaft connected to the rotor and to provide a rudder blade connected to the rudder post.
  • the rudder stock is in this case advantageously non-rotatably connected to the rotor, wherein the rudder shaft is frictionally secured, for example via provided on an inner bore of the rotor clamping segments on the rotor.
  • the rudder stock can also be held by way of a conical end section in a bore of the rotor which is adapted to this end section, wherein the connection between rudder stock and rotor can be produced in a manner known per se using a so-called run-down train, in which a hydraulic oil is inserted into a groove the bore of the rotor is introduced to slightly widen the bore and to draw the end portion of the rudder stock by placing a nut on a threaded end of the rudder stock and applying the nut with a hydraulic oil in the bore.
  • run-down train in which a hydraulic oil is inserted into a groove the bore of the rotor is introduced to slightly widen the bore and to draw the end portion of the rudder stock by placing a nut on a threaded end of the rudder stock and applying the nut with a hydraulic oil in the bore.
  • FIG. 1 is a schematic side view of a rudder of a ship
  • Fig. 2 is a partially cutaway view of a rowing machine for
  • Fig. 3 is a partially cutaway view of the arrangement of Figure 2, but without rudder stock.
  • Fig. 4 is a separate view of the rotor of the rowing machine of FIG. 2 and
  • Fig. 5 is a partially cutaway view of another embodiment of a rowing machine for moving a rudder stock
  • FIG. 6 shows a partially cutaway view of the arrangement according to FIG. 5, but without rudder stock
  • Fig. 7 is a separate view of the rotor of the rowing machine of FIG. 5 and
  • Fig. 8A is a side view of a rotor
  • Fig. 8B is a cross-sectional view of a rotor in a stator
  • FIG. 9A is a detail view of a wing with seals arranged thereon;
  • Fig. 9B is a cross-sectional view through a wing with arranged thereon
  • Fig. 10 is a sectional view of a check valve
  • Fig. 1 1 is an exploded view of a rowing machine
  • Fig. 12 is a schematic sectional view illustrating the storage of the rotor on
  • Fig. 13 is a schematic view of a composite of segments
  • Fig. 14 is an enlarged view of the composite of individual segments bearing ring on the bottom plate of the stator.
  • Fig. 1 shows a rudder 1 of a ship, in which a rudder blade 10 is rotatably mounted on a hull 2.
  • the rudder blade 10 is in this case (seen in advance direction of the ship) behind a rotatably mounted about a propeller shaft P on a propeller shaft 30 propeller 3 and is rotatably connected to a rudder stock 1 1, via a rowing machine 4 at the upper end of the rudder stock 1 1 for Make the rudder blade 10 about a rotation axis D is rotatable.
  • Fig. 2 to 4 and Fig. 5 to 7 show two embodiments of a rowing machine 4 in the form of a rotary wing rudder, which is operated hydraulically for rotating the rudder stock 1 1.
  • the principle of such rotary-wing rowing machines is known per se, for example, from DE-OS 25 44 679 and DE-PS 1 176 514.
  • a rotor 41 is rotatably arranged on a stator 40, wherein the rotor 41 is mounted with a rotor body 410 between a bottom plate 402 and a ceiling plate 401 of the stator 40.
  • the bottom plate 402 and the ceiling plate 401 are connected to each other via a housing pot 400, wherein the housing pot 400 may be made of steel, for example, and is rigidly connected via bolts 403 to the bottom plate 402 on the one hand and the top plate 401 on the other hand.
  • the stator 40 is arranged on the bottom plate 402 fixed to a hull 2 and thus stationary and rotationally fixed.
  • the rotor 41 is rotated and thus the rotatably connected to the rotor 41 rudder shaft 1 1 moves to set the rudder blade 10.
  • FIGS. 2 to 4 on the one hand and FIGS. 5 to 7 on the other hand differ in the connection of the rudder stock 11 to the rotor 41. Since the operation of the rowing machine 4 according to FIGS. 2 to 4 and according to FIGS. 5 to 7 is otherwise identical, the same reference numerals have been used in both embodiments for components having the same function.
  • the rudder stock 1 1 is frictionally connected to the rotor 41 via three clamping segments 412 arranged annularly on an inner bore 418 of the rotor 41. At its upper end, the rudder stock 1 1 a threaded end 1 10, on which a nut for axial securing of the rudder stock 1 1 can be placed.
  • the rudder stock 1 1 is inserted with a conical end portion 1 1 1 into a correspondingly adapted bore 418 on the rotor 41 and is connected to a threaded end 1 10 of the rudder stock 1 1 patch nut press-connected to the rotor 41.
  • a groove 417 is formed on the inside of the bore 418, which serves to connect the rudder stock 11 to the rotor 41 using a so-called oil train.
  • a hydraulic oil can be introduced into the groove 417 for mounting the rudder stock 1 1 on the rotor 41, over which the bore 418 of the rotor 41 can be widened slightly (for example, by a few tenths of a millimeter).
  • a nut By placing a nut on the threaded end 1 10 of the rudder stock 1 1 and hydraulic pressurization of the nut can then the rudder stock 1 1 with its end portion 1 1 1 in controlled manner in the bore 418 for producing a press bond be retracted.
  • the advantage of this compound is its high strength. The connection can also be resolved at any time and then restored in a reproducible manner.
  • a connection of the rudder stock 1 1 with the rotor 41 using an oil train is preferably applied to be transmitted torques greater than, for example, 630 kNm.
  • the rudder shaft 1 1 can be connected to the rotor using the clamping segments 412 (see FIGS. 2 to 4).
  • FIGS. 2 to 4 and FIGS. 5 to 7 The mode of operation of the rowing machine 4 according to FIGS. 2 to 4 and FIGS. 5 to 7 is identical.
  • three vanes 404a, 404b, 404c, 414a, 414b, 414c are arranged for the hydraulic actuation of the steering machine 4 on the stator 40 and on the rotor 41 conventional rotary vane rowing machines known per se - share a space W between the stator 40 and rotor 41 in six subspaces W1, W2.
  • the wings 414 a, 414 b, 414 c of the rotor 41 are screwed in the radial direction with the rotor body 410 and thus bolted to the rotor body 410.
  • wings 414a, 414b, 414c are welded to the rotor 41, wherein for better fit one or more webs on each wing 414a, 414b, 414c may be formed, which are inserted for connection in corresponding grooves on the rotor body 410 , in particular be pressed.
  • the wings 404a, 404b, 404c on the stator 40 are bolted in the illustrated embodiment over itself by bottom plate 402 and ceiling plate 401 extending bolt connections, but can also be welded or made of one piece with the housing pot 400.
  • the operation of the rowing machine 4 is effected in that a fluid located in the subspaces W1, W2, for example a hydraulic oil, from a subspace W1 or W2 is pumped into another subspace W2 or W1 and thereby the pressure conditions in the subspaces W1, W2 are changed.
  • a fluid located in the subspaces W1, W2 for example a hydraulic oil
  • pumps can be connected to the housing pot 400 of the stator 40 via pump connections 405, which pump the fluid from one subspace W1, W2 into an adjacent subspace W2, W1 (from subspace W1 to subspace W2 or vice versa).
  • the rower 4 allows the rudder blade 10 to be set at approximately 45 ° in one and the other direction due to the finite extent the wings 404a, 404b, 404c, 414a, 414b, 414c in the circumferential direction.
  • vanes may also be provided on the rotor 41 and on the stator 40.
  • Such a rowing machine can basically provide a greater force for placing a rudder, but allows a reduced setting angle of about +/- 35 ° (including the width of the wings).
  • the result is a maximum setting angle of, for example, approximately +/- 65 °, due to the wing width.
  • the device described can be used, for example, for adjusting heavy loads in general engineering.
  • the three subspaces W1 and also the three subspaces W2, in which the pressure ratios when pumping the fluid for setting the rotor 41 are identical, are connected to one another via pressure equalizing lines 413, which ensure that the subspaces W1 or in the Divisions W2 always prevail the same pressure conditions. Pressure differences can occur in this way only between the subspaces W1 and the subspaces W2.
  • the pressure equalization lines 413 are formed as tubes in the interior of the rotor body 410, as is apparent, for example, from the partially sectioned FIGS. 2 and 5.
  • the transitions between the wings 404a, 404b, 404c, 414a, 414b, 414c and the respective associated walls (FIGS.
  • the rotor body 410 and the housing pot 400) to be sealed.
  • each two seals 5 arranged in the form of sealing strips, which on the respectively associated wall of the rotor 41 and des Stators 40 abut sealing and thus ensure that upon rotation of the rotor 41 relative to the stator 40, the wings 404A, 404B, 404c, 414a, 414b, 414c sealingly run along the rotor body 410 and the housing pot 400 and thus prevent the fluid from a subspace W1, W2 between wings 404a, 404b, 404c, 414a, 414b, 414c and associated wall (rotor base body 410 or housing pot 400) can pass into the adjacent subspace W2 or W1.
  • axially movable seals 5R are provided on the axially upper end faces of the vanes 414a, 414b, 414c on the rotor 41, which bear against the ceiling plate 401 in a sealing manner.
  • Identical seals 5R are also provided on the lower axial end faces of the wings 414a, 414b, 414c, so that the rotor-side wings 414a, 414b, 414c sealingly run along the ceiling plate 401 and bottom plate 402 of the stator 40.
  • the seals 5 are arranged on the wings 404a, 404b, 404c, 414a, 414b, 414c such that they can be acted upon radially with a contact pressure against the associated wall. As shown in perspective in FIG. 9A and schematically in FIG. 9B, the seals 5 are in contact with the subspaces W1, W2 via leads 50, 501, so that in the subspaces W1, W2 with a predetermined pressure (for example 100 bar). fluid is applied to the seals 5 with a contact pressure corresponding to the fluid pressure.
  • a predetermined pressure for example 100 bar
  • the seals 5 of the wings 404a, 404b, 404c on the stator 40 can in principle also be acted upon by an external pressure which is independent of the pressure in the subspaces W1, W2. In this case, only the seals 5 are connected to the wings 414a, 414b, 414c of the rotor 41 via leads 50, 501 with the subspaces W1, W2.
  • the axially movable seals 5R are connected at the axial end faces of the wings 414a, 414b, 414c of the rotor 41 via supply lines to be provided with the subspaces W1, W2 and acted upon by the fluid of the subspaces W1, W2 with a contact pressure.
  • the fluid can act directly on the seals 5, 5R in the form of the sealing strips via the feed lines 50, 501. It is also conceivable, however, to arrange the seals 5, 5R on a base plate, which is in contact with the feed lines 50, 501 and on which the fluid acts.
  • FIG. 10 A possible embodiment of such a check valve 51, 52 is shown in Fig. 10.
  • the check valve 51, 52 has a housing 510 which receives a movable closing element 51 1 in its interior.
  • the closing element 51 1 is biased by a supported on the housing 510 spring 513 so that in a rest state, the closing element 51 1 with a closing portion 512, an opening 514 in the housing 510 closes.
  • the check valve 51, 52 is thus closed, as shown in Fig. 10.
  • the closing element 51 1 is moved in the housing 510 in such a way that the opening 514 is released and a fluid is released through the opening 514 into the housing 510 and through a rear opening 515 may flow out of the housing 510 again.
  • the check valve 51, 52 is released in this state.
  • the check valve 51, 52 is installed in the supply line 50 in the manner shown in FIG. 9A such that at an excess pressure in the partial spaces W1, W2, fluid enters the supply line 50 through the check valves 51, 52 and the seals 5, 5R applied.
  • the check valves 51, 52 close, so that the fluid in the feed lines 50 can not flow away into the sub-spaces W1, W2 and the contact pressure on the seals 5 is maintained.
  • the check valves 51, 52 thus serve as a safety measure and ensure that even with a sudden pressure drop in the sub-spaces W1, W2, the tightness between the sub-spaces W1, W2 is maintained.
  • the seals 5, 5R are advantageously arranged on the respective vanes 404a, 404b, 404c, 414a, 414b, 414c in such a way that they can be pressed against the respectively associated wall section of the rotor 41 or the stator 40 in order to reduce the material removal of the rotor To compensate for abrasion. In this way, the seals 5, 5R self-compensating such that the contact pressure of the seals 5, 5R remains constant regardless of the material removal due to abrasion.
  • Fig. 1 1 shows an embodiment of a rowing machine 4 in an exploded view.
  • the rotor 41 is rotatably mounted between the ceiling plate 401 and the bottom plate 402 of the stator 40.
  • the bearing rings 61, 62 are formed of individual circumferentially adjoining segments 610.
  • the segments are not directly adjacent to each other, but are spaced apart by a gap of narrow width.
  • the bearing ring 61, 62 is also conceivable to carry out the bearing ring 61, 62 as a one-piece, closed ring, which is arranged loosely between the rotor 41 and the bottom plate 402 or rotor 41 and cover plate 401.
  • the segments 610 of the bearing rings 61, 62 are made of a thin material, such as copper or a copper alloy or a metal-plastic composite material, in particular a composition containing steel, sintered bronze and polyoxymethylene (POM).
  • the segments 610 may additionally be coated with a sliding material, for example PTFE (polytetrafluoroethylene).
  • the bearing rings 61, 62 are lubricated by the fluid located in the chambers W1, W2, for example a hydraulic oil, and provide a low-friction bearing of the rotor 41 on the stator 40.
  • Sleeves 61 1 are provided and inserted into the segments 610, for example, to form receiving openings for lubricant.
  • a schematic sectional view of the mounting of the rotor 41 on the stator 40 is shown in FIG. 12.
  • FIG. 13 A schematic view of an annular bearing ring 61, 62 composed of segments 610 is shown in FIG.
  • recesses 612 are formed on the segments 610 of the bearing ring 61, 62, which serve to achieve an advantageous distribution of the lubricant on the bearing ring 61, 62, so that an advantageous lubrication of the bearing between the rotor 41 and the stator 40 is achieved.
  • the depressions 612 may be formed into the surface of the segments 610 in the manner of countersinks or blind holes of small diameter and hold the lubricant for advantageous lubrication.
  • the representation of FIG. 13 is not to be understood to scale.
  • radial bearing rings 71, 72 are additionally provided between rotor 41 and base plate 402 or ceiling plate 401, which serve for the radial mounting of the rotor 41 on the base plate 402 or the ceiling plate 401 .
  • the radial bearing rings 71, 72 may be made of the same material as the axial bearing rings 61, 62.
  • the radial bearing rings 71, 72 may for example be arranged loosely between the rotor 41 and the stator 40, that is to say not bolted to the rotor 41 or to the stator 40, for example screwed. It is also conceivable, however, that the radial bearing rings 71, 72 are fastened to the bottom plate 402 or cover plate 401.
  • sealing rings 81, 82 are provided, which on the one hand and the transition between the rotor 41 and the bottom plate 402 between the rotor 41 and ceiling plate 401 on the other hand, fluid-tight seal.
  • the idea underlying the invention is not limited to the above-described embodiments, but can in principle be realized even in completely different types of embodiments.
  • the present invention is basically in differently constructed rowing machines, for example, in rowing machines with more or less than three blades on the rotor and stator, can be used.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Sealing Devices (AREA)
  • Actuator (AREA)

Abstract

L'invention concerne un moteur pour le gouvernail d'un bateau, comportant un stator fixe à monter sur la coque du bateau; un rotor logé sur le stator de façon à tourner autour d'un axe de rotation; une chambre créée entre le stator et le rotor et contenant un fluide; au moins une ailette disposée sur le rotor ou le stator, séparant la chambre en au moins deux chambres partielles, le fluide pouvant être transporté d'une chambre partielle à l'autre pour l'entraînement du moteur de gouvernail; et un joint disposé sur l'ailette pouvant être soumis à une pression de compression au moyen d'une conduite d'alimentation pour étancher les deux chambres partielles à l'aide du fluide contenu dans les chambres partielles. Selon l'invention, un clapet antiretour (51, 52) est prévu dans la conduite d'alimentation (50, 501) et conçu pour maintenir la pression de compression du joint (5, 5R) en cas de chute de pression dans au moins une des chambres partielles (W1, W2).
PCT/EP2010/066077 2009-10-27 2010-10-25 Moteur de gouvernail WO2011051233A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202009014799.1 2009-10-27
DE200920014799 DE202009014799U1 (de) 2009-10-27 2009-10-27 Rudermaschine

Publications (2)

Publication Number Publication Date
WO2011051233A2 true WO2011051233A2 (fr) 2011-05-05
WO2011051233A3 WO2011051233A3 (fr) 2011-07-07

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PCT/EP2010/066077 WO2011051233A2 (fr) 2009-10-27 2010-10-25 Moteur de gouvernail

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CN110230700A (zh) * 2019-06-13 2019-09-13 南京中船绿洲机器有限公司 一种船用舵机的密封装配装置及方法

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