DE2655732A1 - HYDRAULIC DRIVE WITH A STATOR CARRYING A SCREW - Google Patents

Description

Patent attorneys Dipl.-Ing. Hans Langosch Dr.-lng. Heinz Hosenthien 7000 Stuttgart 1 Hordwgg 62 Telephone (0711) 206523

Applicant:

company

Societe dite: CENTER D ¹ ETUDES

ET DE REALIZATIONS INDUSTRIAL

DE L'ATLANTIQUE

(C.E.R.I.A.)

1 and 3, rue Marcel Sembat

F-44049 Nantes (Loire-Atlantique)

Hydraulic drive with a stator carrying a screw

The invention relates to a hydraulic drive with a stator carrying a screw, a nozzle, a circumferential groove within a guide in which one Screw is guided, the screw having a round rim, from the inside reaching to the center The wings go out and the outside as part of a hydraulic engine

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is trained.

Drives of this type are known from US Pat. Nos. 3,487,805, 3,531,214 and 3,610,713, the rim is provided with a toothing in which the motor-driven gears engage.

Furthermore, from DT-PS 558 428 and US-PS 2 085 a drive is known in which an outer ring is a Screw fixed turbine blades carries, the type that the drive and its drive turbine have a common stator and rotor. In all of these drives, the screw is on one of the traverses mounted vertical shaft arranged. In addition, the drive turbine of the last-mentioned patent specifications is suitable not for driving with hydraulic fluids of high pressure and the arrangements according to the named patents require a large construction volume.

The object of the invention is to provide a drive of the initially to create the type mentioned, which manages without a vertical shaft and which is very high with a hydraulic medium Pressure can be applied, which has a particularly small volume and in structure and in production is easy.

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To solve this problem, the invention provides that the circumferential groove of the stator is cam-shaped is and that the outer circumference of the screw carries radially displaceable slide and as part a vane motor is used.

To form the profile of the circumferential groove of the slide and the recesses for receiving the same the same techniques are used that are known for vane motors and pumps. The difference is that according to the present invention, the vane motor instead of the compact, massive The rotor is designed to be hollow on the rim of a screw, for example for a ship propulsion system, so that no concentric shaft for mounting the screw is necessary, but a free passage of the medium conveyed through the wings is achieved.

The circumferential groove can particularly advantageously have a plurality of identical cams which are symmetrical on the circumference arranged at equal angular intervals and assigned an equal number of inlet slots and outlet slots are. This also distributes the stress on the rim of the screw more evenly around the circumference and through this balance of forces, the camps are in radial direction practically only through the intrinsic

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weight of the screw loaded.

Particularly advantageously, the circumferential groove has an even number of cams, by which an even number of "cylinders" is formed, the cylinder groups thus formed can be acted upon in groups with the pressure medium, so that with the same flow rate of a hydraulic pump different speeds and torques can be reached on the screw. For this purpose, it is then necessary that each cylinder group that can be pressurized at the same time is evenly distributed over the circumference of the drive , preferably as a group of two or as a group of three.

The construction is particularly simple with a low weight if the supply lines to the inlet slots and the outlets of the outlet slots are arranged circumferentially in the body of the stator. Appropriate the lines are staggered in the axial direction and approximately concentric at a distance from the circumferential groove arranged at the same radial distance, whereby the smallest volume of the drive can be achieved.

Further advantages and features of the invention emerge from the following description with reference to the enclosed Drawings of an embodiment. It shows:

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Fig. 1 is a partial longitudinal section of a

approximately rotationally symmetrical drive,

Fig. 2 is a side view of the in Fig.

stator shown in section according to arrow II in Fig. 1 and

Fig. 3 shows a cross section through the in

Fig. 1 shown drive on a smaller scale at the level of arrow II with a schematic Representation of the lines and the pressure oil supply.

The embodiment of a drive shown in Figs. 1 to 3 has a nozzle housing 1, which by ribs not shown is stiffened. The nozzle housing 1 is designed so that various Organs of the drive are housed in it and that the resulting forces in a known manner via the drive bracket on the ship to be driven, for example, or the like. can be transferred. The nozzle housing 1 itself is designed in a known nozzle shape to promote flow. The screw 10 consists from an inner rotor part 11, are arranged on the blades 12, the outer ends of which by a round one Wreath 13 are connected to each other. The wheel-shaped wreath

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13 is rotatably mounted in a stator via a roller bearing 19, this roller bearing 19 at the same time as The axial bearing is used, as can be seen in FIG. 1. The stator 20 shown alone in FIG. 2 is concentric fixed in the nozzle housing 1. The centering is achieved by a second bearing 18, for example a needle bearing the screw 10 improved. The bearing 19 is supported by a sealing ring 26 and accordingly the bearing 18 is sealed.

By means of the ring 13, the wings 12, which are connected in a form-fitting manner, are immediately set in rotary motion. In addition Radial recesses 14 are provided in the ring part 13 ', in which slides 15 are slidably guided. Opposite in the stator 20, a circumferential groove 21 is provided, the width of which corresponds to that of the slide 15. The depth of the groove 21 is different in the circumferential direction, so that a type of cam is formed on the circumference will. The slides 15 in the radial recesses 14 are always in all angular positions by springs the screw 10 pressed against the bottom of the groove 21 (Fig. 3).

It is particularly important that the depth of the groove 21 is shaped in the circumferential direction so that it is uniform distributed on the circumference several identical cams with the same

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Distances formed from one another and thus inlet chambers or outlet chambers acting as hydraulic motors are given, each of which is in communication with an outlet slot and an inlet slot 22, respectively. All inlet slots 22 are with a supply line 24 and all outlet slots 23 are with an outlet line 25 in connection. In order to obtain the smallest possible drive, it is advantageous that the lines 24 and 25 are provided in axial alignment in the area in front of the circumferential groove 21 in the stator 20 (FIG. 1).

In Fig. 3 a cross section through the drive is shown, from which the four "cylinders" distributed around the circumference are clearly visible. To achieve a force balance of the screw 10 in the radial direction, it is advantageous that there is always an even number of "cylinders" are provided, wherein the cylinders are evenly distributed on the circumference, always opposite each other in pairs or at one Arrangement of three or a multiple of three cylinders, these are always offset by 120 to each other.

By means of a manually operated control valve 31, the opposing cylinders can be operated in pairs or all of them acted upon together with a pressure medium (Fig. 3)

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Correspondingly, in other arrangements 6, 8 or 2 η or 6, 9 or 3 η cylinders can be connected, with each cylinder 2n or 3n can only be pressurized in pairs or only three, so that always only opposing cylinders or cylinders offset by 120 are pressurized or depressurized. Through this there is practically no radial load on bearings 18 ″ and 19.

Each control valve 31 is made in a known manner via a line 34 and a pump 32 with a pressure medium a container 33 is supplied. The pump 32 is continuously connected to a cylinder or a group of cylinders Line 34 and line 24 in connection, while the other symmetrical cylinder or the other symmetrical Cylinder groups via a line 34 'and the supply line 24' optionally via the hydraulic control valve 31 can be supplied with the print medium. If the line 34 is not pressurized, it is Connected via the switching valve 31 and a line 35 to the container 33 and thus depressurized (FIG. 3). This allows a different drive speed of the screw with a constant pump delivery Score 10.

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Claims (7)

Claims 1.J Hydraulic drive with a one screw load-bearing stator of a nozzle of a circumferential groove within a guide in which the screw is guided is, wherein the screw has a round rim, from the inside to the center reaching Go out wing and the outside is designed as part of a hydraulic motor, characterized in that that the circumferential groove (21) of the stator (20) is cam-shaped and that the outer circumference the screw (10) radially displaceable slide (15) carries and serves as part of a vane motor. 2. Drive according to claim 1, characterized in that the circumferential groove has several identical cams has, which are arranged symmetrically on the circumference at equal angular intervals and that he has a has the same number of inlet slots (22) and outlet slots (23). 3. Drive according to claim 2, characterized in that the circumferential groove (21) has an even number of cams by which an even number of "cylinders" are formed. CENTER D ¹ ETUDES 0810 001 7 0 9 8 2 5/0293 ° ^MINAL "- ¹ V 4. Drive according to claim 3, characterized in that the cylinders can be pressurized in groups are. 5. Drive according to claim 4, characterized in that each cylinder group which can be pressurized at the same time is evenly distributed on the circumference of the drive, preferably as a group of two or as a group of three . 6. Drive according to one of claims 1 to 5, characterized characterized in that the supply line (24,24 ') to the inlet slots (22) and the discharge lines (25,25') the outlet slots (23) are arranged circumferentially in the body of the stator (20). 7. Drive according to claim 6, characterized in that the circumferential in the body of the stator (20) provided supply lines (24,24 *) and the discharge lines (25,25 ') staggered in the axial direction and at a distance from the groove (21) and are arranged approximately concentrically at the same radial distance. CENTER D'ETUDES Ο « 10 0Ol 709825/0293