DE2105956A1 - Adjustable propeller - Google Patents

Description

Adjustable base screw

The invention relates to a blade adjustment device for a ship's propeller, which is attached to a stern shaft of a Ship is attached without this stern shaft having to be significantly modified.

An adjustable propeller is understood to mean a propeller, the propeller blades of which are about a longitudinal axis of the blade are rotatable to change the pitch angle. The invention relates to a mechanism that such the Causes pitch changing rotation, the screw blades themselves are known embodiments.

The advantages of adjustable propellers in certain ships are known and will not be discussed further here will.

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Conventional propellers of this type require one hollow stern shaft for the supply of a hydraulic medium under high pressure to the lifting mechanism for the slope change to operate. In addition, this high pressure, for example 70 kg / cm ^, must be maintained, regardless of whether the slope is changed or not. To install a propeller of this type in an existing ship, either a hollow drive shaft can be installed or an existing shaft can be drilled out. Both are hate-taking costly and, moreover, only very highly specialized systems have drilling machines that are able to provide the necessary To carry out work.

The object of the invention is to provide a device for adjusting to create of ship's propellers, which has a hub, which allows installation in existing stern shafts without that the latter must be changed significantly. The invention eliminates costly high waves, both in new facilities and in facilities of already finished ships, since a hollow one Drive shaft is not used. Furthermore, in the construction of the present invention, the above-mentioned high pressure is only required to achieve the change in slope.

The invention is particularly useful for barges and fish steamers from 150 - 1500 hp provided, where the savings in material costs compared to the costs of already existing adjustable propellers is considerable.

The adjusting device according to the invention for ship propellers is also simple, stable and relatively light to manufacture.

The adjustment device itself is inside a hub constructed, which is provided with a flange, one of which

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Section is fitted into a rotatable sealing arrangement, which in turn is attached to the ship. The paddock has a conical inner bore that complements a represents the corresponding conicity on the stern shaft of the ship.

The property is provided with an inner hollow shaft on which a piston is attached. It also has a cross head with a groove into which a screw blade root stop intervenes. The groove is designed as an angle, so that the translational movement of the cross head while the stop runs in the groove, the blade root rotates and the pitch of the propeller changes

In all of the illustrated exemplary embodiments, an element that can slide within the hollow shaft, namely a coil, held stationary by counterbalancing forces acting on opposite ends of the coil. In the In the equilibrium position, hydraulic medium fills the cylinder spaces on both sides of the piston, which in this way is effectively locked. At the same time, the cross head is also held so that the propeller has a constant Blade pitch retains. According to the invention, measures are taken to vary the force acting on one end of the spool so that the spool is moved axially. These Axial movement opens a passage so that the pressurized medium can act on one side of the piston. Through this the piston, hollow shaft and cross head are moved axially in order to change the pitch of the propeller.

The wave follows the coil, so that the latter again ' reaches an equilibrium position in which the flow of the flow medium from and to the cylinder chambers is interrupted and the screw blade is locked at a certain pitch.

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In one embodiment of the coil is a measuring or metering bore intended. A change in the flow rate through this metering hole disturbs the equilibrium so that the coil starts to move axially. In this embodiment, a separate supply of the hydraulic medium provided under drive pressure to get into a cylinder space and the piston as already described to move. Here is the flow speed or the throughput through the metering bore for a constant pitch constant and the pitch change is - as explained - caused by a change in the throughput through the metering bore.

In a further embodiment, equal forces are applied to opposite ends of the coil by opposite ones Pressure spring devices applied. In the equilibrium position, these spring devices exert the same forces on the opposite ends of the coil so that it remains stationary with respect to the bore. An axial return movement takes place through a hydraulic pressure medium that acts on one end of the spool. This movement offers one of the Compression springs create a resistance so that equilibrium is restored after a certain distance of movement. The forward movement is accordingly brought about by the flow medium on the opposite end of the coil is directed.

In another embodiment, the flow medium conducted under pressure into the hollow shaft is selectively against one the opposite ends of the coil are directed so that in this way an unbalanced force shuts the coil moved axially. As previously described, this movement allows flow medium to enter a cylinder chamber under pressure, causing the piston to move and the pitch changed

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will. In this embodiment, the flow medium that causes the imbalance also moves the piston.

A third embodiment differs from the further embodiment in the arrangement of the passages for the hydraulic medium.

One embodiment of a rotatable sealing arrangement works together with the stern shaft, namely in one position towards · " ter an aft bearing · mouths in the rotatable sealing arrangement cooperate with grooves in the stern shaft. The latter grooves communicate with passages in the Ship's robber hub. Seals between the hanging grooves reduce leakage from the grooves, thereby reducing the flow medium can enter and exit the hub as the shaft rotates. Flow medium leaking out of the grooves is routed to the aft bearing, where it provides bearing lubrication. Then the flow medium rinsed into a storage tank.

A modified embodiment of a rotary seal arrangement is mounted in front of the stern bearing, which here is water-lubricated is. A common stuffing box is mounted between the stern bearing and the rotary seal, whereby one essentially dry stern wave is achieved. The modified rotary seal is a float assembly, with adjustment elements cooperate with radial slots that allow movement of the seal with respect to the stern shaft. To this Small eccentricities of the stern wave are recorded and leakage losses are controlled.

The invention is based on the drawings, in which some Aßfiihrizngsbeispiele are shown, explained in more detail.

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Fig. 1 is a partial view, partly in section and partly in an exploded state, of one according to the invention Ship propeller hub j

Fig. 1-A is a simplified diagram of a pitch adjusting mechanism, taken inwardly seen from the axis of rotation of a screw blade}

Fig. 2 is a simplified partial section of an aft end of the propeller hub in a plane in which the Axes of rotation of the hub and a screw blade lie;

Fig. 3 is a simplified partial sectional view showing the The continuation of the section directed forwards from FIG. 2 shows}

Figure 4 is a simplified fragmentary sectional view of a Back end of a modified embodiment of a marine propeller hub, in the plane shown the axes of rotation of the screw blade and the hub can be seen}

Fig. 5 is a simplified partial view in section showing the The continuation of the section directed forwards from FIG. 4 shows}

Fig. 6 is a partial view in section on a center line of a front portion of a stern shaft having a Figure 9 shows a rotating float seal assembly;

Fig. 7 is a partial view in section of a center line of a Stern wave, which is directed aftward from that of FIG Section shows}

Fig. 8 is a simplified partial view in section of a End of a further embodiment of the hub, wherein a plane can be seen in which the axes of rotation of a screw blade and the hub are arranged |

9 is a simplified sectional view showing the forward continuation of the view of FIG. 8th

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Fig. 10 is a simplified partial diagram of a portion of an eight-vessel (Hecke), which illustrates the propeller associated hydraulic components \

Fig. 11 is a section of a modified rotating float seal » which is used together with a stuffing box) where the section shows a plane in which is the axis of rotation of the stern shaft;

Fig. 12 is a partial section of a portion of the tail shaft and rotary seal assembly, taken along line 12-12 in Fig. 11;

13 is a detailed view of a portion of a piston ring seal; along line 13-13 in Figure 12, where Parts of the stern shaft and the sealing arrangement are omitted;

Fig. 14 is a simplified partial section of the forward end of the hub, as shown in Fig. 8, wherein the hub comprises means for displaying the Blattete FINISH \

Fig. 15 is a schematic representation of a hydraulic circuit associated with the means for indicating the pitch is connected; and

FIG. 16 is a partial cross-sectional view of another embodiment of a rotating float seal similar to that of FIG 11, which shows a plane in which the axis of rotation of the stern shaft is arranged, with the piston sealing rings 11 are omitted.

The adjusting device for the pitch of the propeller consists of a hollow hub 10, (Fig. 1), whose Eight part 11 is fastened by screws to a hollow central section 12, the inner wall of which is designated by 12.1 is. At the front end of the hub, a screw flange 13 is attached, of which a front portion in a

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rotatable sealing arrangement 14 is fitted. This sealing arrangement 14 is attached to a ship (Fig. 10). The flange 13 is provided with a conical bore which a conical section 15 at the stern end of a stern shaft

16 added. This conical section 15 borders on Aft bearing 17 of a shaft outlet pipe 17 · 1 of the ship. This VTe 11 enaus exits tube is shown in dashed lines and is attached to the seal assembly 14.

A root fits into an opening 18 in the central section 12 19 of a screw blade part 20. A similar opening 21 is shown for a second screw blade (not shown). A third screw blade (not shown) is provided for a three-bladed screw, the blades are arranged at a distance of 120 ° from each other. The axis of rotation 24 of the ship's propeller hub is coaxial with the bearing

17 attached. The propeller described is designed to be turned to the left (i.e. a turn in the counterclockwise direction, viewed from the stern and indicated by arrow 23), the blade being shown in a forward sloping position.

The opening 18 has an annular shoulder 25. the The root 19 of the screw blade is attached to a blade connecting plate 26. The plate 26 and the root delimit an annular groove 27 »in which the annular shoulder 25 engages. From the blade connecting plate 26 stands Stop 28, the longitudinal axis 29 of which is parallel to a longitudinal axis 30 of the screw blade and perpendicular to the connecting plate 26 is running. The bearing created by the annular shoulder 25 and the groove 27 allows rotation of the screw blade around the axis 30 and causes a force inhibition on the blade when the hub rotates about axis 24. The axis 30 intersects the axis 24, as does the axes of the second and third screw blades (not shown) do

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A cross head 33 can be moved along the axis 24, which with a smile 34 is provided, which is parallel to and adjacent runs on the inner surface 26.1 of the connecting plate 26. The surface 34 is perpendicular to the axis 30 and has a groove 35 that is at an angle to the axis is arranged. This angle is denoted by 36 and only shown in Fig. 1-A and is referred to below as the groove angle. The stop 28 slidingly contacts the groove 35 forming Components that respond to the movement of the crosshead to adjust the pitch. Since the stop 28 lies within the groove, takes the longitudinal movement of the cross head along the axis 24, this stop with, which then slides in the groove 35 and moved laterally, the sheet rotated about the axis 30 and the slope of the Screw blade is changed. A bearing (not shown), which is designed as a shoe, can be provided in the groove and is fitted rotatably into the groove at the stop. It can also be designed as a needle bearing to reduce wear and tear and reduce friction between the stop 28 and the groove.

In Fig. 1-A the figure-of-eight is shown in the direction of arrow 37 and the corresponding rotation of the screw blade 20 about the axis 30 takes place in the direction of the arrow 37.1. The stop 28 is located in the groove 35, which - as already executed - is inclined to the axis 24 at an angle 36. The rotation of the screw blade about the axis 30 depends on the Groove angle and the longitudinal movement of the cross head. For a given screw hub, the slot angle depends on the Requirements of the pitch adjustment.

In order to simplify the manufacture and storage of the marine propeller hubs, cross heads are used, which are only differ from each other by the groove angle. On the-

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In this way a hub fulfills several requirements of the pitch variations. The groove angle for a clockwise propeller is the mirror image of a groove angle for a counterclockwise propeller. So is a center line of a groove for a clockwise propeller shown by the dash-dotted line 56.1.

All screw blades are designed similarly and each blade has a corresponding groove in the cross head, whereby the groove angles are the same. The longitudinal movement of the cross head 33 causes an equal rotation of each screw blade, whereby an equal change in the slope of each sheet is caused. The longitudinal movement of the Crosshead is effected by the hydraulic means described in more detail below.

Fig. 2 hangs with Pig. 1 together and shows that the Cross head 33 is attached to a shaft 38, which in turn has a piston 39 approximately in its center. Of the Piston 39 »shaft 38 and crosshead 33 move as a unit. The front end portion 41 of the shaft 38 is provided with a forwardly directed bore 41.1, which via a centering shoulder 42 of the central section 12 the hub 10 fits. The rear end section 43 of the shaft 38 is provided with a bore 43.1, which has a centering shoulder 44 of the back end 11 of the hub fits. The front end portion 41 of the shaft is through a central bore 46 plugged into a stationary partition wall 45 which is attached to the inner wall 12.1.

In this way the screw hub is inside in several compartments divided, the wall 45 separating the hub into a rear cylinder and a front cylinder. Of the Piston 39 is inserted in the rear cylinder and forms

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det a rear cylinder chamber 51 behind the piston and a front cylinder space 52 in front of the piston. The crosshead 33 forms a rear crosshead space 53 behind the Crosshead and an anterior crosshead space 54 in front of the crosshead. A passage 56 leads through the cross head, which the Permits flow through the crosshead and prevents it from acting like a piston. The rear cylinder space 51 is partly through a rear face of the piston 39, part of the inner wall 12.1 and a cylindrical one Passage 11.2 is limited. The front cylinder space 52 is partially defined by a front surface of the piston 39 and a Back of the annular wall 45 limited. The rear one Crosshead space 53 is partially defined by a front of annular wall 45 and a rear face of the crosshead locked in. The anterior crosshead space 54 is partial through a front surface of the cross head 33 and one front wall 55 of the hollow central portion 12 limited.

In the space 51, a return compression spring 60 is used, which presses the piston 39 into a forward position. The feather surrounds the centering lug 44 and the section 43 and comes into action to achieve the maximum forward pitch, if the hydraulic pressure fails.

When the ship's propeller hub rotates at a slow speed, the force of this spring is sufficient to lift the pitch of the propeller blades back to the full forward position without hydraulic means, as will be described in more detail will.

The shaft 38 has a central bore 61 in which a regulating spool 62 slides, the front end 63 of which slides in a bore 64 of the centering lug 42 fits. The rear end 65 of this spool slidably fits into a bore of the centering shoulder 44.

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At the rear end the bore 66 is through a screw 68 sealed and a spring 69 is inserted into this end, hereinafter referred to as a coil spring, which between the screw 68 and the spool 62 is compressed. This spring tends to move the spool in the bore 64 into a push forward position. The spool 62 has a central bore 71 that enters a narrower metering bore 72 merges at the front end of the coil. The holes 71 and 72 consequently communicate with the bores 66 and 64 opposite ends of the coil. A passage 75 opens into the bore 64 and leads from a corresponding one Source of flow medium under control pressure.

The cylindrical outer jacket of the coil 62 is at 75 »76 and 77 undercut in such a way that two projections or ridges

78 and 79 are formed. These protrusions make one Sliding fit in the bore 61. The projection 78 has a Radial bore 81 and the projection 79 have a radial bore 82. The two radial bores connect the bore 71 with the bore 61 and they can be brought into connection with other passages, as will be explained in more detail below. A pin 83 (Fig. 1) extends between the projections 78 and

79 into the bore 61. In FIG. 2, only the longitudinal position of the pin 83 is shown in a simplified manner. The movement of the coil in With respect to the bore 61 is limited by the distance between the projections 78 and 79, since these interact with the pin 83. The pen is specially designed for quick pitch adjustments or is used - in the event that the hydraulic pressure decreases - locate the spool in relation to the passages in shaft 38.

A longitudinal passage 85 connects the bore 43.1 with the bore 41.1 in the corresponding sections of the shaft 38. A radial passage 86 connects the bore 61 with the space

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51 and a radial passage 87 connects the bore 61 with the barely 52. The radial passages are arranged lengthways at a distance, so that a radial passage (86 or 87) is aligned with a radial bore, namely 18 or 82, in the coil, when a protrusion exposes a remaining radial passage.

A longitudinal passage 91 carries flow medium under actuation pressure from the ship's propeller flange 13 (Fig. 1) into the bore 41.1, from where it passes through the passage 85 into the bore 43 · 1 reached. In this way flow medium appears under actuation pressure at each end of the central bore 61.

Seals that are not identified in more detail are arranged over the entire propeller hub, the undesired Flow, in particular via the end sections of the regulating coil within the bores 64 and 66, via the piston 39 and reduce the inner wall 12.1, as well as between the bore 46 of the wall 45 and the shaft 38. These seals are preferably O-ring seals that allow sliding movement.

Rigid seals are used between sections 11, 12 and flange 13. These seals don't have to be one withstand strong movement between the parts to be sealed.

The passages are based on FIG. 1 in conjunction with FIGS. 2 and 3 explained. The passage 91 through a radial passage 92 communicates with a passage 93 for rotatable seal assembly 14 and a pressure port 94 adjacent to the propeller flange 13. (The route of the passage 93 is shown modified in FIG. 3).

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A flushing passage 97 extends from the rear end of the bore 56 and leads through the passages 98 and 99 flow medium back to room 53. The flow medium can flow from space 53 through passage 56 (Pig. 2) into space 54, from where a passage 101 leads to an annular groove (not shown) which is an orifice 103 in the rotatable sealing arrangement 14 is assigned. The mouth 103 is used to receive flow medium for lubricating the stern shaft and the medium under lubricating pressure from the mouth 103 mixes in the annular groove (as will be explained in more detail) by flow medium flushed from the hub via the passage 101. The mixture moves forward, lubricates the Stern shaft 16 and goes back to a storage tank via a passage 107 at the front end of the rear bearing 17.

A pressure port 102 in the rotatable sealing arrangement 14 supplies flow medium under control pressure to the passage 73 via a groove (only in Pig. 3) and Passages shown in phantom at 95. The leakage from the mouth 94 (discussed later) is controlled and if so If the shaft is sufficiently lubricated by this leakage, the orifice 103 is superfluous and can be omitted will.

FIG. 3 shows more in relation to FIGS. 2 and 10 Details. The propeller flange 13 has a conical Bore 104, which complements the conical section 15 of the stern end of the stern shaft 16. The tail 105 of this The end of the shaft is threaded onto which a nut 106 is attached for securing the ship's propeller hub the shaft 16 is screwed on. Corresponding keys and keyways (not shown) are provided to the Αητ to ensure drift between the shaft and the propeller hub.

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- 15 -

The mouths 94 and 102 in the rotatable sealing arrangement 14 communicate via Hingnuten (as mentioned above) with the Passages in the screw flange. The passage 93 can only be seen clearly in FIG. 3. Each of the mouths 102, 103 and 9 ^ communicates with corresponding annular grooves 108, 109 or 110 in a bore 111.1 of an inner sleeve 111 of the rotary seal. When the flange rotates, it becomes fluid into the propeller flange, then, along the shaft directed. A passage 95 (shown in phantom) connects the groove 108 (partly shown in phantom) with the Passage 73 in such a way that flow medium can flow from the mouth 102 to the passage. (The passage way is not fully shown).

Four seals 112 are provided in sleeve 111 and one seal between each annular groove to prevent leakage to control between fluid media at different pressures in adjacent grooves. A total leaked amount during the pitch adjustment of about 4-6 liters per minute from the mouth 94 is provided. With frequent pitch adjustments, this leakage quantity can be sufficient to prevent the Lubricate the stern bearings so that the amount of lubrication supplied through the muzzle 103 is superfluous.

These four seals can be piston ring seals, each of which is a spring steel ring or a snap ring with a Gap is that allows the insertion of the seal and creates a spring action similar to that of the piston rings. the The seal can be designed so that it is either inwardly onto the flange 13 or outwardly onto the bore 111.1 engages. In each of the above cases, there are fine grooves on oppositely aligned radial surfaces of each Seal provided to allow fluid to enter on each side of the seal and lubricate the surfaces

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can. This reduces the friction between the seals and the sleeve 111 and increases the service life of the seals.

Between the propeller flange and the rotary seal a low pressure seal 113 is provided to prevent water from entering the rotary seal and oil leakage the seal decreased. A passage 114 in the rotary seal allows the insertion of a threaded plug 115 » which prevents rotation of the sleeve 111 with respect to the rotary seal.

Two hydraulic lines (FIG. 10) emanating from a control device are connected to the pressure outlets 94 and 102. Valves for each line are operated by the control device. The pressure port ^W ^ 02 / is fed with hydraulic flow medium via the control device from a pump of variable volume. This orifice supplies flow medium under control pressure and the throughput is selected by an operator for a desired blade pitch. The passage 73 (FIG. 2) receives flow medium under a controlled volume and a controlled pressure, the flow determining the position of the regulating coil, which in turn - as will be explained - is responsible for the position of the piston. The pressure port 94 is fed with hydraulic flow medium under actuation pressure, which is supplied by a pressure-balanced, volume-variable pump and which serves to adjust the pitch of the propeller. The compensation causes oil to be supplied to the orifice 94 at a constant pressure and a required rate, for example 0 to 12 liters per minute. The control device is designed so that the flow medium is continuously under control pressure and one to maintain a

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certain desired blade pitch required throughput is fed. If the blade pitch is adjusted by changing the flow rate in the mouth 102, The interconnection between the valves allows the flow medium to be under actuation pressure only during the Incline adjustment flows into the mouth 94-.

The working method is based on the jig. 2 in conjunction with FIGS. 1 and 3 clearly.

Flow medium under control pressure enters the bore 64- from the passage 73 and leaves it through the metering bore 72 of the regulating spool 62, which constricts the throughput volume before entering the central bore 71. This passage constriction in the bore 72 creates a pressure drop in the bore 72, which a force on the front End of the coil, which tends to move it astern. This stooping motion of the coil represents the compression spring acting on the back end of the coil counteracts itself. An equilibrium position of the coil is reached, when the force of the flow medium acting backwards on the front end of the coil is caused by the force of the compression spring 69 is balanced. In the equilibrium position, the passage 87 is formed by the projection 79 and the passage 86 closed by the projection 78. That in the bore 71 Incoming hydraulic medium flows into the bore 66 and is returned through space 53 via passages 97 and 98 (only shown in Figure 1). Through the passage 101 flushing medium flows out of space 54 and the shaft outlet or tail boom back. In the equilibrium position, i.e. with a constant blade pitch, (Fig. 3) while in the Mouth 102 flows medium under control pressure with constant throughput, the mouth 94- does not receive any flow medium under actuation pressure.

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To change the pitch of the propeller blades, e.g. to make the pitch smaller, the throughput is below Control pressure at the mouth 102 increased. An increase in the flow rate under control pressure increases the Force at the front end of the spool 62, thereby moving the control spool rearwardly with respect to the shaft 38, and until the pin 83 meets the projection 79. The projections 78 and 79 are moved astern in this way and give the passages 86 and 87 opposite the holes 61 and 41.1 free.

At the same time, the flow medium under actuation pressure passes through the pressure port 94- into the rotary seal and flows along the passages 93, 92 and 91 into the bore 41.1. The passage connecting the bore 41.1 with the bore 43.1 85 allows the flow medium to enter the bore 43.1 under actuating pressure, whereby at each At the end of the central bore 61 flow fluid is present under operating pressure. The one located in the bore 41.1 Flow medium enters the passage 87 and flows into the tree 52, where there is an increased pressure on the exerts front surface of the piston 39 and moves it rearward to a new position. The resulting force is greater than the maximum forward force of the Spring 60.

As soon as the passage 87 is open, the bore is aligned with the passage 86, so that flow medium out of the tree 51 can emerge when the piston 39 is moved aft. The flow medium coming from the tree 51 flows through the passage 86, through the bore 81 and into the bore 71t whereby it mixes with the flow medium from the bore 66.

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When the flow rate no longer increases under control pressure, the backward movement of the spool stops and the Wave is in equilibrium with respect to the coil, so that the passages 86 and 87 through the projections 78 or 79 are closed. The coil inevitably locks the piston 39 hydraulically in its position and in the Incline creepage can be neglected. The supply of the high-pressure medium at the mouth 94 only serves to change the slope required is stopped by interconnecting the valves in the control unit. Of the Piston 39 maintains this new position until a change in the flow rate into orifice 102 occurs.

The piston 39 follows a longitudinal movement of the control coil, so that this coil is the master and the piston 39 is the slave.

A backward movement of the shaft 38, as shown by the arrow 37 (Fig. 1-a), causes a backward movement of the Cross head 33, in turn, the rotation of the propeller blade about its axis 30 in the direction of arrow 37-1 evokes. The shaft 38 is pivoted to starboard and is inhibited by the groove angle. That way will the pitch is smaller.

Moving the cross head to a maximum rearward position causes the blade pitch to be reversed, which goes through a neutral position.

A decrease in the throughput rate under control pressure results in a drop in force at the front end of the spool. Included the force of the spring 69 then acts on the coil and pushes it forward until the projection 78 with the pin 83 comes into contact. The projection 78 moves on this Way forward and gives the passage 86 for the flow

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Free medium under actuation pressure within the bore 4-3.1 so that it can enter the space 51. The pressure on the rear surface of the piston 39 increases, so that a resultant force is generated and through the relatively small force of the spring 60 is increased. The bore 82 is brought into alignment with the passage 87, so that the flow medium from the space 52 enter the bore 71 and here with the flow medium from the bore 64- can mix. The piston moves forward until the throughput rate is constant under control pressure and the equilibrium position is reached, in which the projections 78 and 79 close the passages 86 and 87 - as already explained above.

The forward movement of the piston 39 also moves the crosshead 33 forward, the stop 28 towards the mouth is pivoted because the hat is in the form of an angle 36 formed, (Fig. 1-A) and designed so that the Screw blade is rotated in a direction opposite to arrow 37 x 1. The slope is made this way greater.

It is clear that in the equilibrium position of the coil the opposing forces exerted by the spring 69 and by the pressure forces of the flow medium acting on the coil, are balanced, due to the pressure drop in bore 72. Currents in hydraulic pressure cause spool 62 to pass through the unbalanced Force of the spring 69 is moved forward. The projection 78 abuts the pin 83 and prevents further forward movement of the spool with respect to the shaft 38. As a result, the bore 82 becomes aligned with the passage 87 brought so that the flow medium from the edge 52 in the Bore 7t can get. The projection 78 defines the

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leave 86 free so that flow medium can enter the space 51 from the bore 43.1 when the piston 39 passes through the Spring 60 is pushed forward. During this movement of the piston, the spool 62 is also pushed forward, since the spring 69 also moves the projection 78 against the pin 83. The coil 62 thus follows the piston 39 and the propeller reaches its maximum forward incline. The flow pressure in the passages in the hub is through Leakage losses through the seals in the rotary seal are relaxed, so that the formation of hydraulic blockages is excluded.

If the spring 60 were not fitted, the screw blades would Maintain the pitch angle that the propeller immediately before the hydraulic pressure failure or a pitch which is possibly undesirable and would result in the propeller blades acting forces was applied. For a ship's propeller with a diameter of about 1.22 m, the Actuating pressure about 70 kg / cm, the control pressure is

range from about 1.75-14.00 kg / cm · and the throughput volume is a maximum of about 16 liters per minute.

In summary, it is stated: The regulating coil 62 (! Ig. 2) is a device within bore 61 that slides back and forth therein and with respect to the hub. This coil 62 moves according to a difference between two opposing forces. According to Fig. 2, the force to move the bobbin backwards, while the force to move the bobbin forward is provided by the bobbin spring 69, so a compression spring is exerted. When the forces are not balanced, the coil moves in relation to each other on the bore and in relation to the hub. When, on the other hand, the forces are balanced, i.e. when they are equal, it takes place no movement in relation to the hole.

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When the coil 62 has covered a certain distance, means are provided to create a balance of forces. These means respond to the movement and cause the shaft 38, as well as the piston 39 and attached thereto the attached cross head 22 can be moved axially with respect to the hub by the corresponding distance. Included the shaft follows the spool, so that the spool assumes a new equilibrium position, which is stationary with respect to the hub is. Then the spool has the same position in relation to the bore of the shaft as at the beginning.

In the following, FIGS. 4 and 5 are referred to the other figures dealt with in more detail. In the embodiment according to FIG. 1, there is a continuous flow of the flow medium guided to one end of the coil 62 and thereby exerted a force on this coil caused by the spring is matched. A hub according to a modified embodiment is only used during the adjustment of the pitch fed with flow medium, so that any loss of liquid is reduced, as will be explained below.

Instead of the coil 62 according to FIG. 1, a modified coil is used. The spring 69 and the continuous flow of flow are replaced by two coil springs, one at each end of the coil being used is.

Another embodiment of an adjustable propeller is indicated generally at 130 in FIG. 4. This hub consists of a rear section 131 $ a Middle section 132 and a propeller flange 133 (Fig. 5) »which is fastened by screws. Sine rotatable Sealing arrangement 134 allows flow medium over the flange 133 to the hub fHessen, with the means used for this purpose

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correspond to those described with reference to FIG. 3 are. The flange 133 is on a conical portion 135 a stern shaft 136 is set, the axis of rotation with 137 is designated. Aft bearings in a shaft outlet or stern tube of the ship (not shown) correspond to those shown in FIG.

In an opening 141 in the central section 132 of the hub is a Screw blade root 140 inserted. The blade bearings correspond to those already described earlier. they consist of a blade connecting plate 142 which is fastened to the blade root 140 by screws or bolts; and a kingnut 143, into which an annular shoulder 144 engages within the central portion 132. The screw blade can rotate about an axis 146 and the rotation is controlled by a stop (not shown), the is slidably fitted in a groove (not shown) of a crosshead 148. The stop starts from an inner surface 142.1 of the blade connecting plate and corresponds to the stop according to FIG. 1. As already explained, the Backward movement of the crosshead 148 has a smaller pitch angle and its forward movement has a larger one Incline angle result. Other details directly related to the pitch angle adjustment mechanism, correspond to the measures already described.

The cross head 148 is attached to a shaft 150 which has a piston 151 approximately in its center. The front end section 152 of the shaft 150 is with a bore 153 and the rear end section 154 is provided with a bore 155.

A stop 159 is provided on a surface 158 of the central section 132 and protrudes aft. At this

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Attached to stop 159 is a shaft 160 which is slidably fitted into bore 153. The back section 131 of the hub has a forward facing centering shoulder 162, which is slidably seated in the bore 155. In this way, the shaft I50 is slidably supported at both ends, so that a longitudinal movement of the piston disk is possible within the hub. In a fixed partition 165 a bore 166 is arranged through which the shaft 150 is inserted and in which it slides.

A central bore 168 in the shaft 150 is separated from the bore 153 by an annular shoulder 169, while a further bore 170 connects the two bores 168 and 153 with one another. One slides in the bore 168 Eegelspule 172. Between the shoulder 169 and the spool, a front spring 173 is provided, which is attached to the front end the bobbin. A backward every 174 adjoins the back end of the spool 172. A detent 175 is provided at the back end of the bore 168 of the shaft 150. To this The spool 172 is enclosed between two springs and slides within the bore 168 between them Feathers. The spool 172 has a recessed central portion 176 so that projections 176.1 and 176.2 are formed at opposite ends of the coil.

The screw hub is divided into four separate trees. A rear cylinder space 177 is partially through the rear surface of the piston I51 and the front surface of the Section I3I limited. A front cylinder space I78 is limited in part by the front surface of the piston 151 and the rear of the partition 165.

A rear crosshead space 179 is defined in part by the rear face of crosshead 148 and the front

1 09834/02

the partition 165 limited. An anterior cruciform space 180 is made in part by the rear face 158 of the central section 132 and the front surface of the cross head 148 limited. Through a passage 181 in the cross head 148 can Flow medium flow between spaces 179 and 180.

Passages 182 and 183 connect tree 177 and tree, respectively 178 with the central bore 168. The longitudinal separation of the passages 182 and 183 is chosen so that when the Coil 172 is in a central or equilibrium position within the bore 168, the projections 176.1 and 176.2 the passages 182 and 183 close. The space 180 is with the bore 168 through a longitudinal passage 185 and a Radial passage 186 connected.

A passage 188 in the shaft 160 communicates with a radial passage 189 which in turn communicates with a further longitudinal passage 190 communicates. As can be seen from FIG. 5, the passages 190 communicate via an annular groove 192 in the rotary seal with a pressure port 191 in the rotatable sealing arrangement 134

The centering shoulder 162 (FIG. 4) is provided with a passage 194 which communicates with the multiple passage 195 stands. As can be seen from FIG. 5, the passage 195 communicates via several passages and an annular groove 195 · 1 in the rotatable seal assembly 134 with a pressure port 196. The pressure ports 191 and 196 are hydraulic Lines connected to a control device (not shown), the selectively flow medium under operating pressure from a hydraulic pump to the orifice 196 or to Muzzle 191 is aimed. To which mouth the flow medium depends on whether the slope should be set larger or smaller. The rotary seal has a

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another pressure port 198, which, if necessary, is used to lubricate the rear bearing. The Estuary 198 communicates with the rotary seal via an insertion groove 203 a longitudinal passage 199 (dashed in Jig. 5), which in turn with the aft bearing (not shown) and a Tree 200 at the back end of the conical section 135 of the Stern shaft is in connection. A passage 201 shown in dashed lines connects the trees 200 and 180 with one another and allows fluid to be flushed from the hub and used via passage 199 to lubricate the thrust bearing can be. Venn the passage 198 not for lubrication is used, it can be locked. The flow medium flushed from the hub via the passage 195 runs via the seals in the rotary seal into the groove 203 "in a manner similar to that explained in connection with FIG. 3 was, and lubricates the stern bearings · Then leaves the flow medium the bearing, according to the embodiment according to FIG. 1.

The control device can be provided with a valve to allow the flow medium flushed by the hub via the Control device and not to be traced back to the tank via the aft bearing. In this case, a pressure port is used in each case, either 196 or 191 »to a rinsing orifice, which directs the flow medium to the control device, which it then returns to the tank through valves.

A low-pressure seal 205 is arranged between the rotary seal 134 and the propeller flange 133, around the inlet of water in the rotary seal and leakage from the seal to the water.

A return spring (not shown) can be provided in space 177. This spring pushes the disk 151 forward

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and works in an emergency when the supply is on hydraulic Pressure to the hub may be disturbed. This spring works similarly to the return spring according to FIG. 1 and 2 and causes maximum forward pitch of the propeller. A hand pump is provided for emergencies in order to overcome any hydraulic locking that may result could occur that the coil closes the spaces 177 and 178. Through this hand pump, the flow medium is in the bore 155 is pumped to move the spool forward, fluid entering the space 177 and out of the space 178 to escape when the piston 151 is pushed forward by the return spring. Without such a feather the slope would remain essentially unchanged after failure of the hydraulic pressure.

O-ring seals are arranged around piston 151, bores 155 and 153, and spool 172. Decrease these seals leakage between components sliding against one another and other unspecified seals are used Used to reduce the leakage of the flow medium.

The rotary seal 134 has three pressure openings (FIG. 5) and four wear-resistant seals 204, one of which each is located between each orifice to control leakage of fluid from the orifices 191 and 196. The seals are, for example, piston rings as described together with FIG. 1.

The operation of the embodiment according to FIG. 4 is like follows: With a constant slope condition, the coil 172 is in general equilibrium due to the action of the springs 173 and 174 or held centered. In this position the passages 182 and I83 are through the projections 176.1 and 176.2 closed on the coil 172 and there is no flow

1Q9834 / 02U

flow to or from the hub. To adjust the incline, the flow medium is fed to one end of the coil under actuating pressure by switching on the control device. Which end of the coil that is depends on whether the pitch is desired to be smaller or larger.

In order to reduce the pitch of the propeller blades, the flow medium becomes the muzzle under actuation pressure 191 (FIG. 5), from which it leaves the sealing arrangement 134 via the groove 192 and the passage 190 and into passes through passage 188 in shaft 160 and enters bore 153. The flow medium flows from here through the bore 170 presses on the front end of the spool 172 and displaces it backwards, whereby the passage I83 is exposed for the flow medium under actuation pressure. This then passes through the passage I83 into the space 178 and here also moves the piston 151 to the rear in accordance with the movement of the coil 172 and enters space 177 through passage 182.

The equilibrium position of the coil is reached when the flow through the bore 153 stops and the coil is centered again and so the passages 182 and 183 are closed. The figure eight movement of the piston 151 moves the crosshead 148 also to the rear, with the screw blades about the axis 146 in the position of a smaller pitch angle to be turned around. The flow medium expelled from the space 177 enters the bore 168 and flows around the Ausgenomaenen Hittelabschnitt 176 and emerges from the passages 186 and 185 and into the space 180 from which it is flushed through the passage 201 from the hub into the space 200.

The passage 199 connected to the space 200 carries flow medium to the aft bearing for lubrication. That in the bo

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The flow priority medium located in 155 is passed through the passages 194 · and 195 to But 195.1 flushed, from where it is over the Seals to groove 203 seeps. From the Nat 203, the flow medium washed away leaves the splash 133 via the Passage 199 »that goes to the aft bearing for lubrication leads. The passage corresponds to the passage 101 according to FIG. 1.

In order to increase the pitch of the blade, a flow medium is used led under operating pressure to the pressure port 196, from where it is via the groove 196.1 into the passages 195 and 194- and enters the bore 155. The flow medium exerts a force on the back end of the coil 172 and moves it forward, the passage 182 being released for the flow medium under actuation pressure. It gets through the passage 182 into the tree 177 »where it presses on the back side of the piston 151 and this together with forcing the crosshead 148 forward. This process increases the pitch of the propeller. The flow medium in tree 178 is through the passage 183 ejected into the bore 168 and passes from here through the passages 186 and 185 into the tree 180, from where it exits as described above. The piston 151 moves forward until the flow of the flow medium falls below it Actuating pressure ceases, so that the projections 176.1 and 176.2 close the passages 182 and I83 when the bobbin is centered again.

The flow medium is expelled from the bore 153 through the passages 188 and 189 into the passage 190 (FIG. 5), from where it is flushed away from the hub by passing it over the seals into the groove 203 and then through the passage to the aft bearing seeps.

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The coil 172 forms a hydraulic one in its equilibrium position Lock for the piston 151 »in the process of movement of the crosshead 148 and prevents pitch creep of the screw blades.

The hydraulic high-pressure pump runs continuously and feeds the control device (not shown) with a fluid under a pressure of about 70 kg / cm. The control device has a triple valve, which - if one Change in slope is desired - flow medium either to the mouth 191 or to the mouth 196 directs. For lubrication A hydraulic low pressure pump (not shown) can be provided for the aft bearing through the mouth 198. The valve of the control device has three positions, namely closing, opening the mouth 191 and opening the mouth 196. It is spring loaded to return to the locking position when a change in slope is not desired. In this way, the spool 172 remains centered. If no change in slope is required for a longer period of time while the stern shaft is rotating, this is achieved under The flow medium at operating pressure does not reach the pressure orifices and the aft bearing is lubricated through the orifice 198.

The control coil 172 is provided for forward and backward movement in the bore, like the coil 62 according to Pig. 2. The coil 300 is moved by a hydraulic force and the movement is inhibited by a force generated by either the one spring 174 or the other spring 173 is applied. Which spring comes into action depends on the direction of movement away. The springs return to the equilibrium position when the hydraulic force ceases to act.

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You pig. 6 and 7 are to be understood together with Fig. 3- .. The rotary seal used in the two described embodiments can have disadvantages because of practical manufacturing restrictions in a fixed rotary seal, great variation of the scope and thus the barrel seat between the inner sleeve (Fig. 3) of the rotary seal and the stern shaft are given. Between the seals that Ifundungen the actuation pressure surrounded, a control of the leakage is required to regulate the throughput and the contamination of the flow medium under actuation pressure with flow medium in the reduce neighboring pressure mouths. Furthermore, there is also the possibility that the low-pressure seal fails, whereby contamination of the rotary seal by water or loss of flow medium can occur. Flow medium under actuation pressure is only perceived by the rotary seal during the change in slope and the controlled leakage or seepage is used for lubrication, as explained above. To a better one To effect control of the leakage or seepage of the flow medium, a new rotatable float seal assembly becomes used in conjunction with a water-lubricated bearing (Figs. 6 and 7). The floating effect of the rotary seal decreases essentially eccentricities and unevenly worn parts of the stern shaft and compensates for them. Ss can relatively tight running sit ze on the seals zwir see adjacent pressure outlets are maintained in order to improve the control of the leakage or seepage of the flow medium expediently. An embodiment a float seal is explained in more detail. This type of seal can be applied to any of the described configurations Marine propeller hub can be used.

10983W02U

Fig. 7 shows a stern shaft 220 with its axis of rotation 221 and a tapered rearward end portion 222 which terminates in a tapered portion within the propeller flange 223 fits. A marine propeller hub according to the invention (not shown) is fitted to the screw flange 223 aft. A shaft entry or tail pipe 225 is Drawn in dashed lines and is a fastener on the stern of a ship. At the rear of the stern shaft are Bearings 226 arranged, which are exposed to the surrounding water. They are known as water-lubricated bearings.

A passage 228 within the flange 223 communicates with a corresponding passage in the hub (not shown) and two further passages (not shown) in the Flanges communicate with passages in the marine propeller hub. The passage 228 in the propeller flange is connected to a hydraulic line 230 which runs in parallel to and adjacent to the shaft 220 is arranged. The other two passages are similarly with two other lines (not shown) are connected and are spaced and parallel around the circumference of shaft 220 arranged for this purpose. All three lines are expediently attached to the shaft using a fiberglass and resin composition and form a protective sleeve 230.1 which encloses the lines. It just becomes a flow path from the hub starting out, namely the hydraulic lines and the passages that are assigned to the passage 228. The other flow paths run parallel and are similar to this «

The front end of the pipe 231 communicates with a drilled one Passage 232 within the inner sleeve 233 of the rotary seal, which is attached to the stern shaft (Fig. 6). An annular mounting arm 235x1 of a known stuffing

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Bushing 235 surrounds the sleeve 233 and is connected to the tail or Vellenaustrittsrohr 225. From the sleeve section the stuffing box 235 has a shoulder 236.1 inwardly and forms a stop for sealing material 23W-. In the sleeve part 236, a collar 237 is fitted and slidable has at least three identical adjusting screws 233 (only two are shown), with which the collar on a splash 240 of the stuffing box 235 is attached. Each adjusting screw 238 consists of a screw spindle 239 which is attached to the flange 240 is fixed and protrudes axially forwards from this flange and is inserted into a hole in the collar 237. By a matte 241 becomes the collar 237 against the splash 240 tightened. The sealing material 234 installed between the collar 237 and the shoulder 236.1 is known per se Way squeezed. Rotation of the! Feed each set screw 238 compresses the sealing material and increases the sealing effect between the shaft and compensates to some extent for the wear of the material 234. This is a conventional stuffing box.

The screw spindle 239 protrudes through a radially arranged Slot (not shown) in a rotary seal flange 242 of a rotary seal assembly 243. One hatter and one Washers 242.1 are provided in order to fix the flat 242 along the screw spindle 239 and its Prevent rotation. The rotary seal assembly 243 surrounds the Shaft 220 and is supported in three places by the screw spindles 239 from the collar. The slots 243 permit small Badial movements of the sealing arrangement 243 with respect to FIG the stuffing box so that these slight eccentric movements can follow the shaft 220 «

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In the rotary seal 243 three individual pressure mouths 254 and four seals 246 are provided, one of the latter being arranged between each dog. The seals control the leakage or seepage of the Strömun ^ smediums between the mouths in a similar manner as has been described in connection with FIGS. 3 ^ n ^. 5 A low-pressure seal 247 is provided on each brew of the rotary sealing arrangement. The gland 235 keeps the section of the stern shaft in front of it essentially dry.

The rotation of the shaft 220 rotates the hydraulic lines within the fiberglass sleeve 230.1 and takes the inner sleeve 233 of the rotary seal with it. Eccentricities of the shaft or of the inner sleeve 233 cause slight radial ones Deviations of a periodic nature caused by a fixed point in relation to the ship, for example at the stern or Shaft outlet pipe, are observed. Such slight radial deviations in the rotation of the shaft can be caused by Radial movement of the sealing arrangement 243 can be absorbed by sliding the screw spindles 239 within the Radial slots running in the same direction as the shaft.

A float seal as described above can use seals 246 that have a smaller clearance in Relative to the main shaft, providing improved control of leakage and seepage between the seals can be achieved. The seepage of water is largely reduced by the sealing material 234, whereby what is achieved is that the shaft adjacent to the rotary seal is essentially dry, the stern shaft bearing is lubricated in the usual way by the water.

In fig. 8 and 9 »is one compared to the execution according to the pig. 4 and 5 show a somewhat modified construction.

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The passages are assigned to a differently designed regulating coil and the passage within the ship is very easy to use. bennabe has also been changed slightly.

The modified embodiment of the hub 260 has a rear section 261 which is screwed to a central section 262. A propeller flange 263 is also attached to the central section and is enclosed at its front end by a rotatable sealing arrangement 264. The propeller is on a stern shaft 265 arranged, the axis of rotation of which is denoted by 266. A ship's propeller root 267, which is only partially shown, is rotatable mounted within an opening 262.1 in the central section 262. A cross head 268 effects the pitch adjustment, as described in connection with the crosshead 148 (FIG. 4).

The cross head 268 is attached to a shaft 270 (Fig. 8), in the center of which a piston 271 is mounted. The shaft has a front bore 272 and a rear bore 273 provided. A centering boss 274 protruding aft is slidably fitted into the forward bore. A Centering shoulder 275 protruding to the front slides in the aft hole. A solid partition wall 276 has a bore 277, in which the shaft slides and in this way is freely axially movable within the hub.

The interior of the hub is, as described above, divided, namely, into a rear cylinder space 279, a front cylinder chamber 280, a rear cross-head space 281 and a front cross-head space 282. A passage through the crosshead connecting the space 281 with the space 282. Forward A central bore 286 extends from the rear bore 273 in the shaft 270, which

109834/0244

leave 288 and 289 connected to rooms 279 and 280. A shoulder 291 'in which an inner bore 292 is provided is, separates the central bore from the front bore 272. A passage 294 within the centering boss 274 communicates with bore 272 and with rotatable seal assembly 264 via multiple passage 295 * one passage 297 within the centering shoulder 275 communicates with the bore 273 and via the individual passages 298 with the rotatable seal assembly 264 (Fig. 9).

The construction described above is generally similar to that shown in Figs. The culverts 186 and 185 (FIG. 4) have been omitted in the embodiment according to FIG. 8 and the passage 199 (FIG. 5) is in Fig. 9 does not exist. Further differences, in particular with regard to the passages with a regulating coil 300, are made described below.

The control coil 300 (FIG. 8) has a rear face

301 and a front surface 301.1 and slides in the Bore 286. A compression spring 302 tensions against the rear surface 301, while against the front surface 301.1 a compression spring 303 pushes. The back end of the spring

302 rests on a catch 304, while the front end the spring 303 rests on the shoulder 291, which serves as a lock for this spring 303. This way both are Springs 302 and 303 are tensioned and the control coil is held in an equilibrium position between them. The coil points a recessed central portion 305, the projections 3O6, 307 at the outer ends of the coil. At constant If the pitch of the blade remains constant, the coil is kept in equilibrium and the projections 306 and 307 are closed the passages 288 and 289. On the projections the coil is provided with diametrical passages 308 and 310, which «it

109834/0244

Communicate longitudinal passages 311 and 312 in the coil. Dio Longitudinal separation of the passages 308 and 310 is such that then, when the spool is displaced forward, the passage 288 for the bore 286 is cleared and the passage 310 bit aligns with the passage 289. When the spool is moved aft, the passage 289 becomes for the bore 286 is exposed and the passage 308 is aligned with the passage 288. To allow the movement of the coil to be aligned behind it To prevent positions, sleeves 314 and 315 are provided, surrounding springs 302 and 303. The sleeves are so long that they can move beyond the desired positions not possible. The sleeves 314 and 315 can be omitted if the springs are sufficiently long that when they are fully tensioned, it is not possible to move the coil too far. Such feathers are for example in the embodiment according to fig. 4th used.

A one-way valve 316 is provided in the wall 276 in order to prevent the stagnation of flow fluid in the spaces 281 and 282 to reduce. The valve lets flow medium through in the direction of arrow 317.

The rotatable seal assembly 264 (Fig. 9) is with three pressure ports 320, 321 and 322, which are provided with associated annular grooves 323, 324 and 325 within an inner sleeve 326 the rotatable seal assembly 264 communicate. The passage 295 is with the annular groove 324 and the passage 298 with the annular groove 325 connected. A dashed line Passage 328 connects the courage 323 to an aft bearing (not shown). Between hats 323, 324 and 325 the rotary seal assembly 264 four seals 329 are provided, which correspond to the seals in the seal assembly 134 (Fig. 5) are similar. The seals between the pressure mouths

109834/0244

control the seepage of flow medium. If sufficient leakage fluid emerges to lubricate the rear bearing, the mouth 320 can be closed. You orifices 321 and 322 are on a control device (not shown) connected and supply the flow medium under actuation pressure only to adjust the pitch of the blade. In the event that the supply of hydraulic pressure to the hub is disturbed, there is a hand-operated hydraulic pump provided, which can be used in case of hot. If this occurs, the speed of rotation becomes the Wave decreased or stopped. The pump is used to pressurize the flow medium to close the coil move and release the hydraulic lock in the cylinder chambers, as already described above became.

The work of this embodiment will be summarized with reference to FIG 4 and 9 explained in more detail. Moving the cross head backwards results in a smaller slope of the propeller blade and the opposite displacement of this crosshead has a greater pitch As a result - the flow medium is led to the pressure outlets 321 and 322 (FIG. 9) - as already described was - and the flow medium is flushed from the hub by controlled seepage through the seals 329 and to the Used to lubricate the rear bearing.

A flow medium is used to reduce the inclination of the leaves passed under actuation pressure into the orifice 321, which leads to the passages 295 and 294 and to the bore 272 leads. Ss flows through the bore 292 and moves the spool 300 backwards and tensions the spring 302 until the sleeve prevents further backward movement. The passage 289 is the one located in the bore 286 under actuation

109834/0244

The flow medium is exposed to the supply pressure and then passes through the passage 289 into the space 280. In this Space it pushes the piston 271 and, consequently, the crosshead 268 rearward, reducing the pitch. As the piston moves backward, fluid is expelled from space 279 through passage 288, which is aligned with passage 308 within the spool. The flow medium from the space 279 passes through the passages 308 and 311 into bore 273 and exits through passages 297 and 298. This comes from the latter Flow medium into the annular groove 325 and seeps through the Seals 329 into groove 323 and then through the passage 328 to lubricate the stern bearing (not shown). When the desired pitch is reached, the The supply of flow medium under actuation pressure is interrupted so that the coil is again in its equilibrium position can take.

In order to make the gradient greater, the flow medium is conducted under actuation pressure into the mouth 322 and from there via the annular groove 325 to the passages 298 and 297 and into the bore 273. The flow medium enters the bore 286 and displaces the coil forwards until the spring 303 is so strongly tensioned that further movement of the coil through the sleeve 315 is prevented. In this way, the passage 288 is exposed to the flow medium which is under actuation pressure within the bore 273 and which then enters the space 279 and here presses forward on the piston 271. When the piston moves forward, the cross head moves accordingly, increasing the pitch of the blade. Flow medium located in the seam 280 is pushed through the passage 289 into the passage 310 within the coil. From here it flows through the bore 292 into the bore 272, which it

10983A / 02U

2105356

-which exits passages 294 and 295 to go into the rotary seal to get. The passage 295 carries flow medium into the groove 324, from where it seeps past the seal 329 and enters the groove 323, which in turn opens into the passage 328, from where the flow medium to the Lubrication of the rear bearing is taken. The force acting on the piston 271 moves the shaft 270 and with it this moves the crosshead 268 forward, the pitch of the blade becoming greater. As already stated, after reaching the desired blade pitch, the supply of fluid under actuation pressure is stopped and the coil returns to its equilibrium position. The coil 300 is located within the bore and operates in general like coil 172.

A return spring can be provided in space 279 to bring the pitch back to the full advance position, if the hydraulic pressure fails. This is for emergencies.

An accessory device associated with the marine propeller hub is shown in FIG. The ship's propeller hub 10 according to the embodiment in Fig. 1 is attached to the stern shaft 16 and in the stern or shaft exit pipe 17 x 1 at the stern 339 stored on a ship. It is driven by a motor gearbox and clutch assembly 34-0. Hydraulic Lines 34-2 and 34-1 are at the mouths 94- resp. 102 connected in the rotary seal 14- and lead Strö ·. tion medium from a control device and pumping arrangement 34-3. The pump assembly 34-3 is through a hose 34-5 connected to a storage tank 344 for flow medium. A flushing hose 346 brings flow medium from passage 107 back to tank 344 after it has lubricated the tail or shaft exit pipe. A separate hose that

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Flow medium for lubricating the rear bearing to an optional arranged mouth 103 (not shown) is in this Pig. omitted.

If a float seal (Figs. 6 and 7 or Figs. 11, 12 and 13) is used, hydraulic lines provide the Connection with a rotary seal in front of the tail or shaft outlet pipe (not shown in Fig. 10).

In the embodiment according to FIGS. 1-3, the blade pitch is the propeller can be seen from the position of the spool 62 in relation to the hub. This position can be made from known characteristics of the spring 69 can be calculated. The determination of the fluid pressure in the bore 64 (measured by a pressure gauge or manometer / not shown /) indicates the forces on the spool 62, which is the position of the coil in relation to the hub and thus indicate the pitch of the blade.

Reference is made in particular to the embodiments in FIGS. 4, 5, 8 and 9: The outlet temperature is a sensitive indicator of the engine load and the slope is a parameter influencing the load. As a result By adjusting the pitch of the blade, an optimal load can be approximately achieved. The described embodiments are suitable for use with known automatic devices to achieve the desired effect achieve.

A modified rotatable seal assembly 350 (dry tail shaft) is shown in FIG. It has a stationary outer sleeve 351 with an inner surface 351 * 1 and an inner sleeve 352 attached to the stern shaft 353. The tail shaft has an axis of rotation 353.1. Each sleeve 351 and 352 can consist of two halves and they are shown in Fig. 11 ao

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shown. The outer sleeve 351 is provided with a rotary sealing flange 354 provided, which has a radial slot 354.1, into which the screw spindle 355 of an adjusting screw 356 is inserted. The adjustment screw is on a solid Part of the ship attached behind the rotary seal. The rotatable sealing arrangement has at least three adjustment screws which correspond to the adjusting screws according to FIGS. 6 and 7. The slots ensure that Eccentricities in the rotation of the stern shaft are absorbed by moving the screw spindle in relation to the radial slots can be moved.

The inner sleeve 352 has an outer surface 352.1 and two Passages 359 and 360 open into the flow medium under actuation pressure reaches and to the propeller flange (not shown). The passages 359 and 360 communicate with the inlet ring groove en 361 or 362 the rotating inner sleeve 352. Pressure ports 364 and 365 are connected to the annular grooves 361 and 362, respectively during the pitch adjustment, flow fluid under actuation pressure is sent to one of the passages 359 or 359 guided. On each side of each inlet ring groove, one outlet ring groove is provided longitudinally at a distance. the Annular grooves are separated from one another by a ring member, referred to below as a barrier dam. Between the inlet ring groove 361 and the outlet annular grooves 367 and 369 are the shut-off dams 368 and 370, and between the inlet annular groove 362 and the outlet annular grooves 371 and 373, the shut-off dams 372 and 374 are arranged. The exit mouths 367 and 377 communicate with the exit annular grooves 367 and 3691 while the outlet mouths 379 and 380 are connected to the outlet annular grooves 371 and 373.

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2105356

A seal 383 is between two annular baffles 384 and 385 are used, which in turn are between two Annular grooves 369 and 371 are arranged. The seal is preferably a piston ring seal as used in piston engines. She is closer based on the Pig. 12 and 13 described. Similar annular baffles 386 and 387 adjacent to the annular grooves 367 and 373 create space for further piston sealing rings 388 and 389 · These piston sealing rings project radially outwards and thus grip the inner surface 351 · 1 cm of the outer sleeve 351 of the rotary seal.

The barrier dams serve as a leakage or seepage control between the inlet ring grooves and the outlet ring grooves. The cylindrical outer surface 370.1 of the dam 370 ist.vom the cylindrical inner jacket 351.1 of the sleeve 351 through a gap 390 separated. The radial dimension of this gap 390 is limited by the maximum change in the clearance between the inner sleeve 352 and the outer sleeve 351, when one turns in relation to the other. This change is litsgt usually in a range of 0.001-0.003 inches. The gaps are best seen in FIG. A large amount of throughput in the inlet port creates a controlled, lowered outlet flow under reduced pressure to the Outlet mouth, the pressure and throughput volume being controlled through the gap 390. A valve that controls the flow of flow from the outlet mouth will be explained later. The guide walls are used for axial localization. sizing of the seals and also - similar to the above-mentioned barrier dams - to the pressure of the flow medium lower the seal. The baffles have a similarly controlled clearance as will also be described later.

Ball bearings 391 and 392 support the outer sleeve on the Reduce sleeve and twin seals 394 and 395

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Leakage from the rotatable seal assembly and reduce possible contamination of the fluid in the seal from the outside. Maximum runout or maximum eccentricity of the bearing is a major factor in determining a lowest limit of the gap width. The inner surfaces of the twin seals contact bearing sleeves 397 and 398, the have beveled outer edges 399 and 4OO. These bevels make it easier to pull the sleeves over the Piston seals. O-ring seals 401 and 402 reduce leakage between the bearing sleeves and the inner sleeve 352 of the rotary seal. The bearing sleeves locate the ball bearings and are held in position by spring clips 403 and 404-.

The piston seal ring 383 is between the inner sleeve 352 and the outer sleeve 351 inserted (Figs. 12 and 13). He has a cylindrical outer surface 383.1 and a cylindrical one Inner surface 383.2 and parallel radial surfaces 383.3 and 383.4-. The seal is a ring with a Gap and has a rectangular cross-section. A cylindrical outer surface 384 ·. 1 of the guide wall 384 (dashed in 12) is separated from the cylindrical inner surface 351.1 of the outer sleeve 351 by a radial gap 406. This gap is similar to the gap in dams and is only a few thousandths of an inch. It depends on the Viscosity of the flow medium under actuation pressure and other working conditions. The minimum size is limited by the maximum runout of the ball bearings .

The outer surface 383.1 of the seal jumps against the outside the inner surface 351.1 in front of and in Met all-to-Me tall Contact to prevent the flow of the fluid.

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However, it is lubricated and relatively free to turn, i.e. to rotate around axis 353.1 if desired. Such cushioning is known in piston rings used in internal combustion engines.

The cylindrical inner surface 383.2 is arranged at a distance from the cylindrical outer surface 352.1 of the inner sleeve, so that a hadial gap 407 is formed between the two surfaces. The gap 407 is used in a manner known per se for fitting the piston ring seal. This seal 383 has a conventional lap joint as in FIG 12 is shown at 408. Two fingers 409 and 410, which run along the circumference and against one another, overlap one another, such that two gaps 411 of 0.002-0.003 inches are formed. There are column with close play to excessive Avoid licking over the overlap.

There are numerous passages through the piston seals 383 413, which are approximately 0.020 of an inch in diameter. They are arranged parallel to the axis 351.1. A Passage with this diameter can transport flow medium from the surface 383.3 to the surface 383.4 and back. Numerous radially arranged passages 415 are arranged through the piston sealing ring, their diameters as well is about 0.020 inches and the outer surface 383.1 connect with the inner surface 383.2 of the piston sealing ring 383. The passages 413 and 415 are alternating on the circumference spaced around the piston ring seals, the distances between the passages being the same.

The passages provide lubrication between the surfaces that touch the piston seals, so that they wear out and their service life is increased.

109834/0244

When working the modified embodiment of the rotary seal flow medium is fed under actuation pressure either into the mouth 364 or into the mouth 365, depending on whether the slope should be adjusted smaller or larger. A throughput in the property of, for example about 12 later per minute (3 gal.) about about 8 seconds causes the slope to change from small to large or from fine to coarse.

If the incline is to be set to a larger one, then Flow medium supplied under operating pressure into the inlet port 364, in a throughput rate that is larger than it is necessary to operate the hub, e.g. about 36 liters (9 gallons) per minute. the end The flow medium reaches the opening 364 in the hat 361 and the flow rate of about 12 liters (3 gallons) per minute exits the hat through passage 359 to enter the To enter the propeller hub. The excess flow rate of about 24 liters (6 gallons) per minute oozes via the barrier dams 368 and 370 in the hanging grooves 367 and 369 and leave the rotatable sealing arrangement through the outlet openings 376 and 377 in flushing hoses (not shown). The flushing hoses are forked and closed together connected to a main flush hose, the flow through the tubes through a flush flow valve (not shown) is controlled. The excess flow rate has reduced pressure, as will be explained in more detail below. That Flow medium enters the annular groove 361 under pressure of about 70 kg / cm. But after the flow medium at If the flow past the barrier dams is metered, the pressure in the annular grooves 367 and 369 is considerably lower. Because of of the pressure drop in these annular grooves 367 and 369 only a relatively small amount of the flow medium seeps via the baffles 386 and 384. This effect

109834/0244

2105356 - 47 -

a further metering of the flow medium, so that only relatively small forces on the seals 388 and 383 act, the wear of which is thereby reduced. wear of directions 388 and 383 by their movement With respect to the surfaces they touch, lubrication is provided from the passages 413 and 415 and due to the comparatively low forces between the surfaces, which are only comparatively low here exert surrounding pressures of the flow medium, reduced. This reduces axial forces on the seal and their lifespan increased.

If the feed pump fails, the stern shaft can be stopped, the purge flow valve closed, and the pitch adjustment be carried out by the supply flow from the hand emergency pump. The flow medium knows through this pump be conveyed into the ship's propeller hub in order to set the desired pitch, because of the closed No or essentially no leakage across the dams occurs. Venn the desired pitch angle is reached, the hand pump is switched off, the stern shaft is driven again and the ship moves.

A device for displaying the pitch of the blade is indicated generally at 420 in FIGS. This display device is attached to the hub 260 (Fig. 8) and has a controllable relief valve 421, which with a compression spring 422 which is slidably inserted within a passage 424 in crosshead 268. The additional provided for passage 283 in cross head 268 (FIG. 8) Passage 424 is drilled parallel to axis 266 of the stern shaft and is capped at its rearward end 425 locked ^ which also act as a lock for the i "^: --- ■ - ü diant.

109834/0244

The anterior crosshead space 28 ?. has a forward end wall 426 with a passage 427 that is aligned with passage 424 in the crosshead. The front end of the passage 427 is provided with a valve seat 429 against which the spring 422 presses a ball 451. A valve stem 433 is connected to the ball 431, which sits loosely within the coils of the spring 422 and serves to keep the spring straight when it is tensioned.

A passage 436 emanates from an outlet opening 430 in the valve seat 429 and communicates in a passage (not shown) in the rotary seal. This passage is connected to a second pump (not shown) with constant volume works and belongs to the pitch scanner (Fig. 15). Flow medium from this second pump enters the passage 436 in the direction of arrow 437 and lifts the ball 431 from the valve seat 429 against the tension of the spring 422. The distance at which the ball emerges from the exit orifice 430 is shifted, determines the constriction of the flow through the valve. The back and forth movement of the Cross head 268, illustrated by the double arrow 434, increases or decreases the force acting on ball 431 and thereby changes the flow constriction of the valve outlet opening 430. The flow medium exiting here enters the front cross head space 282 and leaves it through a flush port 439 'to return to the basin.

This process becomes clear from FIG Incline indicator 4? .O. In the following description be ». ^5. The expression "lines ¹¹ both _t \ --- £ di; iii>e.;Ha.i". The hub bored diameter

1 0 9 8 3 kl 0 2 U ^C0PY

BAD ORIGfNAL

circle

as well as, uf die ^ "Z ^^ ° · '*' ¹ °> _W u is a drifted form of the circle g _{Dlart slope} which has no facilities for an attachment to _Hesse , B, have already been», the. ^^ _{the Ho} . the pitch described, the a ^^ ^

rr. ::::: r r

. . -wi »i for the blue elevation of the eriindongegemäaee * j.iel _e circle ι _w . _t - _en , _{nd au3} and switches the said Sohwi.rl ^ elt.n "°« ζ ^ , was through a direct reading of the »^ -tl ^

dCanx.ig

the piston attached to a """-^^" edruCanx.iger " _{flt w} dergeapan ^ th piston in a cylinder /„, „„ ,,!.

, u a rotatable »^ '- ^'" ^, _white .t

u ^

fpebaut Ut like the seal 450 β »*« »* ^Γ1 8 · "' Ι :! " a usat . The hi "τ" ended distribution lines 4 ₅ 6 and 457 are similar to the tolt "Ln 341 and 542 in FIG. 10 and stir Btromungamediu *" nt "ZD of the first pump. 442 through dl, rotary seal 4 2 into the passage 294 bw 298 of the hab. 260 (ν _β 1. »fig. B). A nor ".l" rweiee open four-way valve 458 can _b "ohlo sen""d","nn the high pressure pump" 2 should fail .. In di ... "Tall, the leaf tendency can be activated by actuating a Ifcnd pump (not shown) werd.n, wi. «Β

COPY 109834/0244 ^BA D original

has already been described. The flushing line '»55 epUlt flow medium through the sealing from the R« u » ²⁸ I ₁ ]? ¹¹ *ommuni59 Vtil »^ /« "Β flow medium over io iltg
adorned with a flushing line 459 from the valve ^ / mungsmedium through a ». common flush line 1-55 ^{ln don} fpnK 448 returns ;.
The work of the Blattsteigunes display corner is' ¹ S- ¹⁵ "The second Pvmpe 4J8 working with constant volume demands flow medium through the rotary valve 452 into the DuroUa .. 4 ₃ 6, through the valve 421 into the tree 282. The. Eagung des Durchfluasea in the valve 420 by wira "O- _rac teristiken the .Teder 422 and the position ^ s ^ eu.kopr in Bo, ug on the end face 426 is determined. Wenu Rich the Kc.." opr astern bewe _e t, ^ "ni _B he benötig to the _Eue el from valves lifting force 451,429 ... FoI eleee ₈ Iloh "Lrd _{e" rinB} erer pressure at Hanometer ^ ₅ a ^. ^ "^^ _{Bl <a} crosshead _T or ^ c. b ««., · Dk ^ η

_{Broö3 The more} the pressure is, the greater the V 8

ram. When the cross head moves from the one o ^

Z * a neutral, ur other ^^^ Zl \ I -

_Bloh the D ^ uck of a K ^ - »» ^, ^^ „ _BerrtC n

Then it shows «! tonometer 44? aB 3 ^ &

the sheet ate ation; at.

in? iK. 11 correspond. ^ _σ *.

" , L ^ d 57 in the inner sleeve 552, di. in the "" 11) through, di. in «utes embedded Ko.

, 588 and 589 separated from each other Bind. At the> »5ÖÖ una?« 7 _{j <ä} Tr _rt iH «nrinKe and die

109B3A / 0244

BATH ORIGINAL

The associated skins were thrown away. The remaining components represent both seals are identical.

The rotatable sealing arrangement according to FIG. 11 is for emergencies equipped. If the high pressure pump fails, the Stern shaft locked, the Viervrege-Yentil closed and the Blade pitch can be adjusted using the hand pump. In case of emergancy decrease piston seal lags 388, 383 and 389 (Fig. 11) Excess flow losses of a relatively low volume flow from the hand pump so that the slope can be changed. As at the swimmer's rotating line 260 geiaässig »16 which do not have piston seals If the high pressure pump fails, the pitch of the blade can be caused by excess flow losses due to the low pressure seals cannot be changed simply by a hand pump. In such an emergency the shaft is stopped and the hoses from the hand pump are connected directly to the bypassing the float seal Hub connected.

109834 / 02U

COPY
BATH ORIGINAL

Claims (14)

Q buildable propeller,
characterized in that a hollow hub (10; 260) is provided on which the propeller blades are arranged and which is positively connected to the stern shaft (16; 136) of a ship, (A) a shaft arranged coaxially in the hub (10; 260) and is reciprocable together with a piston and a cross head, the shaft has a central bore, (b) in which a control element is inserted so that it can slide axially, on the opposite ends of which forces act which are either equal or different, so that in the event of unequal forces the control element in the bore of the shaft with respect to the hub is out of an equilibrium position. or has been moved back, (c) Means are provided for balancing the forces moving the control element and for creating a new state of equilibrium of the control element that is fixed in relation to the hub after a certain distance covered, (d) at least one of the applied forces is a hydraulic force, IeI for transmitting the movement of the control element to the piston, the shaft and the cross head, force-fit connections are provided in such a way that these components cover the same axial distance in relation to the hub as the control element and this is the same in the new equilibrium position The position in relation to the bore of the shaft is the same as in the initial position, and (f) that the cross head is connected to the propeller to transmit its movement and to adjust the pitch of the propeller. 109834/0244 2. Ship propeller according to claim 1, characterized in that that at least one of the forces acting on the control element is a compression spring (69). 3. A ship's propeller according to claim 1, characterized in that the ship's propeller blade is used to adjust the pitch of the blade has a longitudinal axis (30) and a root (19) on which a connecting plate (26) with a stop (28) is arranged, the blade in an opening (18) in the central portion (12) of the hub (10) by a shoulder-groove connection (25 »27) is attached and rotatably arranged about its longitudinal axis (30), and that the cross head (33) has a surface (34) which is parallel to the inner surface (26.1) of the connecting plate (26) and perpendicular to the longitudinal axis (30) of the sheet, this surface (34) has a groove (35) arranged at an angle (36) with respect to the shaft axis (34) has, in which the stop (28) of the connecting plate (26) engages and therein during the movement of the cross head (33) slides along and rotates the sheet about its longitudinal axis (3 °). 4. Ship's propeller according to claims 1 to 3 »characterized in that that for the failure of pressure in the hy ,. additional hydraulic equipment for full blade adjustment are provided. 5. Ship's propeller according to claims 1 to 3, characterized in that that the control element is a coil (62) which has a central bore (71) and a metering bore (72) has, and through which the hydraulic fluid flows continuously under control pressure, the control pressure one end of the spool exerts a force equal to the flow pressure, with the compression spring (69) against the opposite The end of the coil (62) is tensioned to vary the flow rate of the flow under control pressure 109834/0244 _ 54 - nningsmediums communicating passages are provided, wherein a passage (86) leads from the bore (61) radially through the shaft (58) and with a rear cylinder space (51) communicates in the hub (10), a second passage (87) from the bore (61) radially into a front cylinder space (52) the hub leads, the passages alternating hydraulic flow medium from a pressure source lead and move the piston through pressure differences, furthermore Means are provided for flushing away flow medium displaced by the movement of the piston, and that the The outer jacket of the coil (62) is turned behind at various points (75 77) in such a way that projections around the coil jacket (78, 79) protrude whose heights and distance from one another are dimensioned so that they are in the equilibrium position close the two radially arranged passages (86 and 87) of the coil. 6. Ship propeller according to claim 4, characterized in that a compression spring for the failure of the hydraulic pressure (60) is provided which pushes the piston (39) into a forward position. 7. Ship propeller according to claims 1 to 3 »characterized in that that within the bore (168) of the shaft (150) a regulating coil (172) is provided against the opposite one Saiden One compression spring each (173 or 174) butts, the middle section (176) of the outer jacket of this Eegel coil is excluded in such a way that on its opposite End edge projections (176.1 and 176.2, respectively) are formed; the screw hub is divided into several cylinder spaces, wherein a passage (182) from the central bore (168) of the shaft (150) to the rear cylinder space (177) and a Passage (183) leads from the central bore of the shaft into the front cylinder space (178) of the hub, this passage 109834/0244 In the equilibrium position, let the regulating coil (172) be closed by its projections (176.1 and 176.2); for supplying pressurized hydraulic flow medium to the ends of the Hegel coil and for building up a pressure difference at these ends, various passages (188-190, 194-195) are provided and can be closed by the projections on the control coil, passages (186, 185 ) feed pressurized hydraulic flow medium to the recessed central section (176) of the outer jacket of the Hegel coil (172), in such a way that when one of the passages (182 or I83) emerges from the central bore (168) of the shaft (150) by the movement of the coil is enabled, the T Lben (151) and move therewith the shaft (15O) and the crosshead (148) and adjust the blade pitch, and that means are provided for flushing the displaced by the movement of the piston the flow medium. 8. Ship propeller according to claim 7 »characterized in that dsss a rotatable sealing arrangement (14; ...) with the stern shaft (16j ...) of the ship and with lines for the supply of pressurized hydraulic flow medium is provided. 9. Ship propeller according to claims 1 and 8, characterized in that that for the rotatable sealing arrangement the hub (10) has a flange (13) with a conical bore (104), which complements and takes care of a conical section of the aft end of the stern shaft (16), which rotatable sealing arrangement is provided with mouths (94, 102) which via annular grooves (93 »95) of the rotary sealing arrangement with passages (93 »95) communicate in the flange (I3), the passages being connected to the bore (61) of the shaft (38) are and for the supply of flow medium into this bore 109834/0244 2105356 10. Ship's propeller according to claims 1 and 8, characterized in that that the hub has a flange (13) with a conical bore (104) which has a conical section of the stern end of the stern shaft is supplemented and taken care of, the rotatable sealing arrangement (350) has a fixed has an outer sleeve (351) with an inner surface (351.1) and an inner sleeve (352) attached to the stern shaft, the outer sleeve is provided with a flange (354), in with at least three radial slots (such as 354 ·· 1) are, with which adjusting members (356) cooperate and accommodate eccentricities in the rotation of the stern shaft, the outer sleeve (351) with connecting lines for the supply of pressurized hydraulic flow medium is provided and further passages for the hydraulic flow medium are connected to the bore of the shaft in the hub. 11. A ship's propeller according to one or more of claims 1 to 10, characterized in that the devices for supplying flow medium into the bore consist of an inlet groove (361) provided in the inner sleeve (352), which between outlet annular grooves (367 » 369) are arranged and separated from them by dams (368, 370); the inlet groove communicates with the inlet opening (364) and the outlet grooves communicate with the outlet openings (367 »377), the openings being provided in the fixed outer sleeve (351), the dams having cylindrical outer surfaces (352.1) which are separated from a cylindrical inner surface ( 351.1) are separated by a gap (390); are arranged on the side facing away from the Absperrdämmen sides of the discharge grooves (367, 369) piston-ring-like seals (383, 388), and the discharge grooves of the ¹ sealing rings by annular baffles (38 ^ - »384 * are separated and these baffles of the ^. ylindrisciien inner surface (351.1) are separated by gaps (406). 1Q9834 / 02U 12. A ship's propeller according to claim 10, characterized in that that the device for supplying flow medium into the bore from an inlet groove (361) in the inner sleeve (352), which is arranged between annular outlet grooves (367, 369) and from these through dams (368, 370) are separated, the inlet groove with an inlet opening (364) and the outlet grooves with outlet openings (376, 377) communicate, the mouths are arranged in the outer sleeve (351) and that the dams have cylindrical outer surfaces (352.1) which are separated from the cylindrical inner surface (351.1) by a gap (390). 13 · Ship's propeller according to one or more of Claims 1 to 12, characterized in that with the crosshead and in response to its movements a pitch indicator (420) is connected. 14. Ship's propeller according to claim 13 »characterized in that that the blade pitch indicator (420) has a controllable relief valve (421) that works with the Cross head is connected and the outlet opening (430) can be changed by the position of the cross head and the The flow rate of the flow medium is determined by the expansion valve through an input line (454) with a constant-volume pump is connected, and that between the pump and the expansion valve Manometer (445) is arranged. 109834/0244 ■ St Blank page