WO2011051233A2

WO2011051233A2 - Rudder engine

Info

Publication number: WO2011051233A2
Application number: PCT/EP2010/066077
Authority: WO
Inventors: Eckard Dahlweg; Edwin Van Buren
Original assignee: Van Der Velden Barkemeyer Gmbh
Priority date: 2009-10-27
Filing date: 2010-10-25
Publication date: 2011-05-05
Also published as: WO2011051233A3; DE202009014799U1

Abstract

The invention relates to a rudder engine for a rudder of a ship, having a stationary stator to be mounted on a hull, a rotor disposed rotatably about a rotational axis, a chamber formed between the stator and the rotor having a fluid present therein, at least one vane disposed on the rotor or on the stator and dividing the chamber into at least two sub-chambers, wherein the fluid can be delivered from one sub-chamber into the other for driving the rudder engine, and a seal disposed on the vane, on which the fluid present in the sub-chambers can exert contact pressure by means of an feed line, for sealing two sub-chambers by the fluid present in the sub-chambers. According to the invention, a check valve (51, 52) is provided in the feed line (50, 501), designed and provided for maintaining the contact pressure on the seal (5, 5R) in case of a pressure loss in at least one of the sub-chambers (W1, W2).

Description

rowing machine

description

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. In such rowing machines, the stator and rotor include a space in which a fluid, such as a hydraulic oil, is located. At the rotor and / or stator in this case 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. By conveying the fluid, the pressure conditions in the sub-chambers change, so that a torque is generated by the pressure change and transmitted to the rotor.

Embodiments of such rotary-wing rowing machines are known, for example, from DE-PS 1 176 514 and DE-OS 25 44 679. In 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.

In such rowing machines is a prerequisite for effective torque generation that the subspaces are sealed against each other. By Conveying the fluid between the subspaces creates a negative pressure in some subspaces and in other subspaces an overpressure such that the rotor is set into a rotary motion. To seal it is necessary that the wings on the rotor and stator sealingly abut the respective associated walls - the wings on the stator so on the associated wall of the rotor and the blades on the rotor on the associated wall of the stator. For this purpose, seals are respectively provided on the wings, which produce a tight transition and effect a sealing of the subspaces against each other. For a tight transition is required that the seals abut with a sufficient contact pressure on the respective associated walls. In order to produce a sufficient contact pressure, it is known, for example, to arrange springs in the form of leaf or coil springs on the seals such that they are pressed against their associated walls. Disadvantage of such springs is that they have a relatively short life and can break during operation of the rowing machine.

Instead of using springs, 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. Applying the seal with the already existing fluid pressure in the subspaces has the advantage that no additional force-generating means such as springs or the like are required for generating the 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.

This object is achieved by an article having the features of claim 1. In this case, 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.

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 °.

In principle, in each case more than four blades can be arranged on the rotor and stator, if large adjustment forces are required, but a small adjustment angle can be accepted.

Advantageously, the seal on a wing by the contact pressure in the radial direction to the rotational axis sealingly against an associated portion, ie an associated wall, pressed. A seal on a wing of the stator is pressed, for example, radially inwardly against the associated wall of the rotor for sealing engagement. Conversely, 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.

In principle, it is possible to pressurize only the seals on the blades of the rotor through the fluid located in the compartments, but to act on the seals on the blades of the stator by a separate, provided externally and independently of the fluid in the sub-chambers pressure. This is easily possible, since the stator can be accessed from the outside and the stator is immovable during operation of the steering machine. The seals on the rotor, however, are acted upon by the fluid pressure of the subspaces, since the provision of an external pressure for acting on the blades on the rotor is not readily possible.

In a further embodiment, 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. On each wing, 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.

In an advantageous embodiment, 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. By this is meant that 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. At each outlet opening then 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. In a preferred embodiment, 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. Preferably, 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. However, 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.

The provision of a bearing ring made up of segments between rotor and stator also constitutes a separate aspect of the invention within the meaning of claim 12. 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. In such a rowing machine, 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. The provision of such a bearing ring makes the construction of the steering machine, in particular the storage of the rotor on the stator very easy. Conventionally, a bronze 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. Turning away from this, 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.

It is conceivable to attach the individual segments to the rotor or to arrange loosely between the rotor and the stator, without being firmly connected to the rotor or stator.

Depending serving as 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 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.

In a preferred embodiment, the bearing ring is made of a metal-plastic composite material, in particular a composition containing steel, sintered bronze and polyoxymethylene (so-called POM).

In order to provide an advantageous lubrication of the bearing ring and thus to further improve the friction and bearing properties, 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. In addition to serving as 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. Also, 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. In operation, 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. Alternatively, 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. The advantage of this connection using an open-circuit cable is its high strength and the fact that the connection can be released again at any time and restored in a reproducible manner.

The idea underlying the invention will be explained in more detail with reference to the embodiments illustrated in the figures. 1 is a schematic side view of a rudder of a ship;

Fig. 2 is a partially cutaway view of a rowing machine for

Moving a rudder stock;

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

3;

Fig. 5 is a partially cutaway view of another embodiment of a rowing machine for moving a rudder stock;

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

6;

Fig. 8A is a side view of a rotor;

Fig. 8B is a cross-sectional view of a rotor in a stator;

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

seals;

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

Stator; Fig. 13 is a schematic view of a composite of segments

Bearing rings and

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. In the rowing machine 4 illustrated in FIGS. 2 to 4, 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. During operation of the rowing machine 4, 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. The embodiments according to 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.

In the embodiment according to FIGS. 2 to 4, 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.

In the embodiment according to FIGS. 5 to 7, in contrast to the embodiment according to FIGS. 2 to 4, 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. As can be seen in particular from FIG. 6, in this case 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. In the context of the oil train 41, 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). 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 (see Fig. 5 to 7) is preferably applied to be transmitted torques greater than, for example, 630 kNm. For torques of less than 630 kNm, the rudder shaft 1 1 can be connected to the rotor using the clamping segments 412 (see FIGS. 2 to 4).

The mode of operation of the rowing machine 4 according to FIGS. 2 to 4 and FIGS. 5 to 7 is identical. As is apparent from FIGS. 4 and 7 in conjunction with FIG. 8B, 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.

It is also conceivable that the 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.

In principle, it is also conceivable to manufacture the wings 414a, 414b, 414c and the rotor body 410 in one piece. However, this is technically complex, since the parts are preferably made of wrought iron.

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. For example, as shown in FIGS. 2 and 5, 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). By generating a negative pressure in one subspace W1, W2 in this way and a negative pressure in the other, adjacent subspace W2, W1, a torque is exerted on the blades 414a, 414b, 414c of the rotor 41 and the rotor 41 for moving of the rudder stock 1 1 set in motion. In the three subspaces W1 and also in the three subspaces W2, the pressure ratios are equal in each case, while between the subspaces W1 on the one hand and W2 on the other hand, a pressure difference is generated, which causes a torque on the rotor 41. Due to the angular pitch of the wings 404a, 404b, 404c, 414a, 414b, 414c on the stator 40 and the rotor 41, 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.

In an advantageous embodiment, four 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).

If in each case only two wings are used, the result is a maximum setting angle of, for example, approximately +/- 65 °, due to the wing width.

If smaller adjustment angles can be accepted, more than four blades can in principle also be attached to the rotor 41 and stator 40. In this form, the device described can be used, for example, for adjusting heavy loads in general engineering.

As shown in dashed lines in FIG. 8A, 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.

In order for the wings 404a, 404b, 404c, 414a, 414b, 414c to effectively divide the space W into the individual subspaces W1, W2, the transitions between the wings 404a, 404b, 404c, 414a, 414b, 414c and the respective associated walls (FIGS. Thus, the rotor body 410 and the housing pot 400) to be sealed. For this purpose, as shown schematically in Fig. 8B, at the radial end faces of the wings 404a, 404b, 404c, 414a, 414b, 414c are 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.

In addition, 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. In this way, the seals 5 on the wings 404a, 404b, 404c on the stator 40 radially inwardly against the rotor body 410 and the seals 5 on the wings 414 a, 414 b, 414 c on the rotor 41 radially outward Shen against the housing pot 400 of the stator 40 is pressed.

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.

In the same way, 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.

As a result of the fact that the seals 5, 5R are subjected to the fluid pressure in the subspaces W1, W2, no additional force-generating measures, in particular no additional mechanical springs or the like, are required for generating a contact pressure. The result is a simple arrangement that ensures a long life with a secure seal. In order to prevent the contact pressure on the seals 5, 5R being reduced in the case of a pressure drop in one of the subspaces W1, W2 or in all subspaces W1, W2, check valves 51, 52 are provided in the feed line 50 in the region of the outlet openings 502, prevent the fluid from the supply line 50 can get into the subspaces W1, W2 at a lower pressure in the subspaces W1, W2. In this way, the contact pressure on the seals 5, 5R is maintained even with a pressure drop in the sub-spaces W1, W2, wherein the check valves 51, 52 by oppositely directed arrangement also prevent direct passage over the feed line 50 between the adjacent subspaces W1, W2 is created. 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.

If a pressure force F acts on the closing portion 512 in the direction 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.

Correspondingly, 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.

However, if the pressure in the sub-spaces W1, W2 drops, 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. For this purpose, the seals 5, 5R are displaceably arranged in the radial or axial direction on the respective vanes 404a, 404b, 404c, 414a, 414b, 414c, so that the seals 5, 5R are automatically guided by the fluid pressure. By the check valves 51, 52, the fluid pressure is maintained, so that even with a pressure drop in the sub-spaces W1, W2, the contact pressure of the seals 5, 5R does not fall. Fig. 1 1 shows an embodiment of a rowing machine 4 in an exploded view. As already described above, in the steering machine 4, the rotor 41 is rotatably mounted between the ceiling plate 401 and the bottom plate 402 of the stator 40. For axial mounting of the rotor 41 on the stator 40 are between rotor 41 and bottom plate 402 of the stator 40 on the one hand and between the rotor 41 and cover plate 401 of the stator 40 on the other hand depending on a bearing ring 61, 62 disposed between the rotor 41 and stator 40 and annular is formed of individual segments 610.

As shown in the enlarged view of FIG. 14, 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.

In the embodiment shown in FIG. 14, twelve segments 610 have been used to form the bearing ring 61. In principle, however, a lot more or much less segments 610 can be used.

It is basically conceivable to fasten the segments 610 to the rotor 41 or to the bottom plate 402 or the cover plate 401 of the stator 40. In principle, it is also possible to arrange the segments 610 loosely between the rotor 41 and the stator 40.

It 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.

A schematic view of an annular bearing ring 61, 62 composed of segments 610 is shown in FIG. As can be seen in FIG. 13, 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. For example, 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. For example, it is also possible to use very many depressions 612 with a very small diameter, which are arranged regularly or irregularly on the bearing ring 61, 62. As can be seen further from FIGS. 11 and 12, 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. In order to seal the transition between the rotor 41 and the stator 40 in such a way that the fluid located between the rotor 41 and the stator 40 in the subspaces W1, W2 can not escape, 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.

In this context, it should be noted that the storage of the rotor 41 on the stator 40 shown in FIGS. 11 to 13 represent an independent aspect of the invention can, but is advantageously combined with the described measures for sealing.

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. In particular, 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.

In principle, it is conceivable arrangements of the type described not only as a rowing machine, but in other hydraulic turntables, for example, in mechanical engineering or in other areas where large torques are required to move heavy components to use.

LIST OF REFERENCE NUMBERS

1 oar

10 rudder blade

1 1 rudder stock

1 10 threaded end

1 1 1 Cone-shaped end section

2 ship hull

3 propellers

30 propeller shaft

4 rowing machine

40 stator

400 housing pot

401 ceiling plate

402 base plate

403 bolts

404a-c wing

405 pump connections

41 rotor

410 rotor body

41 1 collar

412 clamping segments

413 pressure compensation lines

414a-c wings

417 groove

418 bore

5, 5R seal

50, 501 supply line

502 outlet opening

51, 52 Check valve

510 housing

51 1 closing element

512 closing section

513 spring

514, 515 opening

61, 62 Axial bearing ring 610 segments

611 pods

612 wells

71, 72 Radial bearing ring

81, 82 sealing ring

D rotation axis

F compressive force

S printing direction

P propeller axis w space

W1, W2 subspace

Claims

claims

1 . Rowing machine for a rudder of a ship, with

a stator fixedly mounted on a ship's hull,

a rotor arranged rotatable about an axis of rotation on the stator,

a space formed between the stator and the rotor, in which there is a fluid,

at least one rotor or stator arranged on the wing, which divides the space into at least two subspaces, wherein for driving the

Steering machine, the fluid is conveyed from one subspace to another subspace, and

a arranged on the wing seal, which is acted upon for sealing two partial spaces by the fluid located in the compartments via a supply line with a contact pressure, characterized by a in the supply line (50, 501) arranged check valve (51, 52) formed and is provided, at a pressure drop in at least one of

Partial spaces (W1, W2) to maintain the contact pressure of the seal (5, 5R).

2. rowing machine according to claim 1, characterized in that on the stator (40) and the rotor (41) in each case at least one wing (404a, 404b, 404c, 414a, 414b, 414c) is arranged, but preferably three wings (404a, 404b , 404c, 414a, 414b,

414c) which divide the space (W) into six subspaces (W1, W2) or four wings (404a, 404b, 404c, 414a, 414b, 414c) which divide the space into eight subspaces (W1, W2).

3. Rowing machine according to claim 1 or 2, characterized in that the seal (5) on the at least one wing (404a, 404b, 404c, 414a, 414b, 414c) by the contact pressure radially to the rotational axis (D) sealingly against an associated portion (400, 410) is pressed.

4. Rowing machine according to claim 3, characterized in that an additional seal (5R) on the at least one wing (404a, 404b, 404c, 414a, 414b, 414c) by the contact pressure axially to the rotational axis (D) sealingly against an associated portion (401, 402) is pressed.

5. rowing machine according to one of the preceding claims, characterized in that on the at least one wing (404 a, 404 b, 404 c, 414 a,

414b, 414c) two mutually parallel seals (5, 5R) are arranged, which in each case via the supply line (50, 501) can be acted upon by a contact pressure.

6. Rowing machine according to one of the preceding claims, characterized in that the seal (5, 5R) is designed as a self-compensating seal such that when worn on the seal (5, 5R), the seal (5, 5R) tracked in the direction of the contact pressure is pressed and with constant contact pressure to an associated portion (400, 410).

7. rowing machine according to one of the preceding claims, characterized in that the feed line (50) as a channel in the at least one wing (404a, 404b, 404c, 414a, 414b, 414c) is formed, wherein the feed line (50) each having a Outlet opening (502) in the wing (404a, 404b, 404c, 414a, 414b, 414c) associated, on each side of the wing (404a, 404b, 404c, 414a, 414b,

414c) arranged subspaces (W1, W2) opens.

8. rowing machine according to claim 7, characterized in that at each outlet opening (502) of the supply line (50) a check valve (51, 52) is arranged.

9. rowing machine according to one of the preceding claims, characterized in that the stator (40) has a housing pot (400), a bottom plate (402) and a cover plate (401), which together with a rotor body (410) of the rotor (41) surround the room (W).

10. rowing machine according to claim 9, characterized in that the rotor (41) with the rotor body (410) between the bottom plate (402) and the cover plate (401) of the stator (40) is mounted.

1 1. Rowing machine according to one of the preceding claims, characterized by at least one between the rotor (41) and the stator (40) arranged, serving as a thrust bearing bearing ring (61, 62) which is composed of individual, circumferentially successive segments (610).

12. Rowing machine for a rudder of a ship, with

a stator to be fixedly mounted on a ship's hull and a rotor arranged rotatably about a rotation axis on the stator, characterized by at least one bearing ring (61, 62) arranged between the rotor (41) and the stator (40) and consisting of individual bearings , in the circumferential direction successive segments (610) is composed.

13. rowing machine according to claim 1 1 or 12, characterized in that the segments (610) are arranged loosely between the rotor (41) and the stator (40).

14. rowing machine according to one of claims 1 1 to 13, characterized in that the bearing ring (6) is coated with a sliding material.

15. rowing machine according to claim 14, characterized in that the sliding material comprises PTFE or consists of PTFE.

16. Rowing machine according to one of claims 1 1 to 15, characterized in that the bearing ring (6) is made of copper or a copper alloy or contains copper or a copper alloy.

17. Rowing machine according to one of claims 1 1 to 15, characterized in that the bearing ring (6) is made of a metal-plastic composite material, in particular a composition containing steel, sintered bronze and polyoxymethylene.

18. Rowing machine according to one of claims 1 1 to 17, characterized in that the bearing ring (6) recesses (612) for receiving and / or distribution of a lubricant.

19. Rowing machine according to one of claims 11 to 18, characterized in that between the rotor (41) and the stator (40) additionally serving as a radial bearing bearing ring (71, 72) is provided.

20. Rowing machine according to one of the preceding claims, characterized in that a rudder stock (11) is non-rotatably connected to the rotor (41).

21. Rowing machine according to claim 20, characterized in that the rudder stock (11) via clamping segments (412) with the rotor (41) is connected.

22 rowing machine according to claim 21, characterized in that the rudder stock (11) has a conical end portion (111) which is press-held in a bore (418) of the rotor (41).