DE2163303A1 - Device for moving a heavy body up and down - Google Patents

Description

Dipl.-Ing. Walter Jackisch 7 Stuttgart N. MenzefetnBe 40

POCLAIN

SocietS Anonymous:
ΕΒΕΧϊϊϊϊΚ

Le Plessis-Belleville

(Oise) France A 32 745 - sk

December 20, 1971

Device for moving a heavy body up and down

There are known piston pumps for operation deep in the ground in order to bring the sucked-in material from the depths to the surface conveying, e.g. pumps such as those used for oil wells.

Pumps of this type comprise a cylindrical body connected to a conduit formed by the hollow drill pipe is, while a piston via rods arranged coaxially to the hollow drill pipe with a drive device, e.g. a motor, which in turn is coupled to a connecting rod system. The rods and the piston form a relatively heavy unit, which are connected to the drive device via a tension member. To a To avoid too great a fluctuation of the potential energy during the up and down movement of the piston is often at least partly the weight of the piston and the rods by being arranged in opposite directions to the piston and the rods Counterweights balanced.

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_ ₂ _ 2183303

This results in some deficiencies, of which the need to emphasize in particular, is the vibration of a heavy one and bulky counterweight at one end of a lever or the like. accept what is a source of danger. aside from that the changing loads due to the acceleration of the counterweight must be absorbed by the drive device will. This limits the pumping capacity, as the maximum permissible speed is reached very quickly. the The overall performance of the known pump devices is consequently mediocre.

The invention is intended to eliminate these disadvantages and for this purpose creates a new drive device for up and Downward movement of heavy body or dg · in which the energy storage no longer takes place in the form of a shift in corresponding counterweights, but in contrast to this in an elastic manner Shape, choosing parts with little inertia. It is heavy for everyone to move up and down Body usable.

The object of the invention is therefore to create a drive device for moving a heavy body up and down, which is connected to a drive motor via a tension member, which can be transmitted to the body by the motor Forces alternately greater than the force of gravity acting on the body and the forces of friction are and in opposite directions Direction act, and are smaller than gravity and the frictional forces, and being one of the force of gravity counteracting device is constantly connected to the drive motor

To achieve this object, the device according to the invention comprises a spring motor.

In a particularly preferred embodiment, the spring motor comprises a liquid-operated reversible motor

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two permanently connected chambers, one with one first hydraulic fluid reservoir, the other with a second hydraulic fluid reservoir.

In addition, the tension member is preferably "flexible and easy to use" Winch wound up attached to the drive motor and the! Spring motor is coupled. .

The drive motor advantageously comprises a liquid-operated one Reversible motor with two chambers, one of which is permanently connected to a hydraulic fluid reservoir, the other optionally via a distributor with two settings either with a hydraulic fluid source or with the hydraulic fluid reservoir connected is.

The hydraulic fluid source advantageously comprises a volumetric hydraulic pump, on the pressure side of which a hydraulic fluid reservoir branches off. In another embodiment, this pressurized fluid source can comprise a gas compressor, A hydraulic fluid reservoir also branches off on the pressure side

The manifold with two settings further comprises a movable element with a control member for alternating Setting one of the two positions is connected; this control element is advantageously connected to the spring motor itself connected and can be regulated.

For reasons of simplifying the system, the second hydraulic fluid reservoir is advantageously used at the same time as the drive motor, the first hydraulic fluid reservoir is connected to the hydraulic fluid source.

In a particularly advantageous embodiment of the invention the drive motor is designed as a spring motor and a liquid-operated reversible motor with two chambers,

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one of which constantly has a first line with one Hydraulic fluid reservoir and the other via a second Line is connected to a liquid reservoir. The spring motor has a variable effective geometry and comprises a control element for controlling the pressure-acting elements Area, wherein the entire drive device comprises a pressure fluid source with a pressure line, which is connected to the first line and a tared throttle valve in a branch.

Advantageously, the simultaneously acting as a spring motor fe drive motor comprises a rotor with which the control member for Change in the drive torque is connected.

In a first exemplary embodiment, the position of the control element is via a kinematic chain Control device changeable as a function of the position of the driven organ.

In a second exemplary embodiment, the position of the control member is the rotational speed of the by means of a The rotor of the drive motor scanning and the control chain transmitting control chain comprehensive control device in Ab-

. dependence on the current speed of the driven

'Organs ν changeable.

Advantageously, the device for scanning and transmission comprises a volumetric, reversible hydraulic pump, its drive shaft is connected to the rotor of the drive motor. A double-acting volumetric receiving organ is also included connected to the control member for changing the drive torque, and comprise the volumetric pump and the receiving member two chambers each, of which one chamber of the pump has a line with one chamber of the receiving member and the other chamber of the pump via a different line

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the other chamber of the receiving member is connected, in a "the two lines connecting further short-circuit line a throttle element is arranged and finally the control element for changing the drive torque is connected to an elastic eückholelement, which keeps the control organ in a given position or leads back to it.

Further features and advantages of the invention emerge from the description of exemplary embodiments with reference to the drawing.

Pig. 1 shows in section the entire pump device with a Drive device according to a first according to the invention Embodiment; . ■

Fig. 2 shows a schematic representation of an inventive hydraulic drive device; Fig * 3 shows a section of an inventive Drive device;

Fig. 4- shows a schematic representation of a hydraulic Drive device according to a second embodiment; FIGS. 5 and 6 show a first schematic representation or second embodiment of the control of the Eegelorganans for the power of the drive motor of Fig. 4, where _die_ Control as a function of the position of the driven body or as a function of the drive speed this body takes place.

1 shows a hollow rod 1 which has been driven into the bottom 2 and penetrated into an enclosure filled with a material in the form of a more or less viscous liquid, but which can be conveyed upwards by pumping. A body 4 of a piston pump with flap valves 5 is attached to the linkage 1, the piston 6 of which is attached to the rods 7 connecting it to the earth's surface 8. At the upper end of the rods 7 is * ei · ¹¹ tension member 9 is arranged, further to the drum or drums of a winch 10

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is rolled up. The winch 10 is made by, one on the earth's surface 8 is held stationary frame 11 and is also coupled to a hydraulic drive motor 12, which they in Rotational movement offset.

The moving pump parts, in the present case the piston 6 and the rods 7t are very heavy. At a In another exemplary embodiment, the movable pump parts could have included the cylinder 4, while the piston 6 is fixed.

) Fig. 2 shows an embodiment of a drive device for rotating the winch 10 in both directions. From the drawing it can be seen that the motor 12, but also another hydraulic motor 13 mechanically connected to winch 10 are. The motors 12 and 13 are reversible motors and can operate as either motors or pumps.

The motor 13 comprises two chambers, one of which is constantly leveling over a line 14- with a first hydraulic fluid reservoir and the other continuously via a line 16 with a second Hydraulic fluid reservoir 17 is connected. The memory 15, 17 are designed in their dimensions so that during t the rotation of the winch 10 to one side or the other of its starting position, the fluid pressure in the two reservoirs remains essentially constant, the pressure in storage 15 ′ being greater than in storage 17.

The engine 12 also comprises two chambers, one of which is constantly and the other ständig.über.eine line 19 is connected to a manifold 20 via a line 18 to the second memory 17, the two settings has. Two further lines end at the distributor 20: a reveal 21 branching off from the line 14 and a line 22 connecting the distributor 20 to the second pressure accumulator 17. In the first position of a movable control element, the distributor 20 provides a

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Connection between lines 19 and 21, while the Line 22 is blocked at its connection point to the distributor. In the second position of the movable element of the distributor 20 lines 19 and 22 are connected to one another, while on the other hand the line 21 is blocked at the junction .zum the distributor.

The movable element of the distributor 20 is via a control member 23 connected to the winch 10. In the present case, the distributor 20 is designed as a slide, the slide via the control member 23 designed as a crank linkage with the Winch 10 is in operative connection; this determines the angular position of the shaft 10a automatically adjusts the position of the slide of the distributor 20.

A line 24 connects the lines 14 and 22. Two one-way valves 25 and 26 are arranged in the line 24 in such a way that the liquid only flows from the line 22 into the line 14 to be led. A line 27 branching off from line 24 between the two valves 25 and 26 leads to line 19. Furthermore, a line 33 connects a pump 28 on its pressure side with the line 14. In a known manner, a line 29 connects the suction side of the pump 28 to a liquid container 30. Via a line 31 »in the tared throttle valves 32 are arranged, the lines 22 and 33 with the liquid container 30 connected.

In one of the embodiments of the invention, the Winch 10 carried by a frame 11, as shown in FIG. 3. The winch 10 includes a main gear 10b, which with the Motor 12 is connected, while the motor 13 is connected to a further gear 10c. A chain 9a runs over the both wheels.

In Fig. 4, a hanging at the outermost end of the tension member 9 weight 38 is shown; the tension member 9 is on the drum a winch 10 rolled up. This winch is connected to a drive motor 39 via a transmission, which in the illustrated

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Example of a pulley arranged on the shaft 41 of the winch 10 40, one with the drive shaft 43 of the rotor of the motor 39 connected pulley 42 and a drive belt 44 running in grooves of the pulleys 40 and 42 comprises.

The motor 39 is a hydraulic motor, reversible and with variable effective geometry. To change performance a lever 45 is provided which controls the drive torque forms and which in the present case can be pivoted about an axis 39a between two end positions 45a and 45b is stored. The regulation takes place automatically as a function of the rotation of the winch 10 by means of the winch 10 with the control device connecting the control device 45. Two examples of the design of the control device 46 are given in connection with the description of Figures 5 and 6, in which they are shown in detail.

The hydraulic fluid circuit of the motor 39 comprises a fluid reservoir 30, a pump 47 and a hydraulic fluid reservoir 48. The motor 39 comprises two chambers 49 and 50, one of which as an inlet chamber and the other serves as a pressure chamber or vice versa. The chamber 49 is via a first line 51 with the memory 48 and the chamber 50 with the container 30 via a second conduit 52 connected. Via a line 53, the pump 47 is connected to the Container 30 and connected via a line 54, in which the one-way valve 55 is arranged, to the first line 51 · Finally, line 56 branches off line 54 from the pump 47 seen from behind the valve 55 and establishes a connection to line 52. In this line

56 is a tared throttle valve 57 · The one-way valve allows the flow of liquid from the pump 47 towards the first line 51 and the tared valve

57 the overflow of the liquid from line 54 into the line 52.

The design of the control device shown in FIG

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- y "

46 is used to control the drive torque of the motor 39 depending on the position of the weight and thus on the Angle of rotation of the Vinde 10. A pulley 58 is with the Shaft 41 of the winch 10 is connected and acts via a drive belt 60 with a rotatably mounted on the "frame 11" Pulley 59 together, the frame 11 also carrying the winch 10. A cam plate 61 is rotatably fixed on the Shaft 59a of the pulley 59 is arranged.

A housing body 62 of the double-acting elastic return device is positively connected to the motor 39 via holding claws 63. A rod 64 is in the housing body 62 arranged displaceably and has two stops 65 and 66, between which two washers 67, 68 are located, which are provided to be freely slidable on the rod. A spring 69 is provided between the washers 67 and 68, the washers 67, 68 at a distance from one another and in contact with two inner stop surfaces 70, 71 of the housing body 62 to keep looking. At one of the ends of the rod 64, a bolt 72 is provided, the one provided in the lever 45 Recess 73 extends through, wherein the other end of the rod has the shape of a fork 74, between the two prongs Cam plate 61 is arranged in such a way that its cam rests against one of these prongs during its rotational movement.

In the exemplary embodiment shown in FIG. 6, some of the elements already described in connection with the description of FIGS. 4 and 5 are found again, which are also provided with the same reference numerals. Only the holding claw 63 is; has been replaced by the retaining claw 63a, which positively connects the housing body 62 to a further housing body 75 of a device described below; the housing body 75 is in turn positively connected to the motor 39 by means of retaining claws 76. Furthermore, the rod 64 has been replaced by a rod 64a, which is designed similarly to the rod 64, d ^{e (} loca without the fork 74 at its one outer end.

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The drive shaft 80 of a volumetric reversing pump 77 with two chambers 78 and 79 is connected to the shaft 43 of the rotor of the motor 39. The housing body 75 is designed as a double-acting cylinder ¹ which comprises a chamber 81 or 82 on each side of the associated piston. A bolt 84 is fixedly arranged at one end of the rod 83 of the piston and extends through a recess 85 in the lever 45. A line

86 connects chambers 78 and 82 while another conduit

87 connects chambers 79 and 81. Finally, a line 88 provides the connection between lines 86 and here. A valve 89 with a calibrated opening 90 is located in this line 88.

The operation of the device according to the invention is described below.

Those produced by motors 12 and 13 of FIGS. 1-3 Moments are proportional to the respective products between the pressure difference between the liquid inlet and outlet each of the motors and pressurizing area of the respective engine.

The motor 13 has the task of counteracting the force of gravity of the piston 6 and the rods 7. That produced by him The moment is essentially constant because the pressure and thus the pressure difference in the liquid in the reservoirs 15 and 17 itself is substantially constant, and it is lower than that due to the characteristics of the selected motor 13 static section modulus of the pump (4-5-6).

The motor 12 forms the actual drive motor of the winch 10. The distributor 20 is in the first position the chambers of the motor 12 via the lines 19 and 14 on the one hand and via the line 18 on the other hand with the memory 15 and 17 connected. The torque generated by the motor 12 is then at a maximum, essentially constant and the same Direction like that of the motor 13 directed. The sum of the through the two motors 12 and 13 generated torques is thus higher than the static and during the pumping process of the

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Pump (4-5-6) usable sum of the moments of resistance and them opposite. On the other hand, when the distributor 20 is in its second position, the two chambers of the motor 12 are connected solely to memory 17, one via line 18, the other via lines 19 and 22. The through the Motor 12 then generated torque is essentially zero.

It is easily understood that by the alternate selection of the first or the second position of the distributor 20, the Zuleitun§ ^and the motors is regulated 12 and 13, thereby achieving alternately an engine torque even higher than the pump modulus then un lower again than is the static section modulus. This arrangement results in a reciprocating movement of the piston 6, on the one hand upwards for pumping under the prevailing effect of the two motors 12 and 13, on the other hand downwards under the prevailing effect of the weight of the piston 6 and the rods 7 against the Action of the motor 13 · Under the action of the motor 13, the rope-shaped tension member 9 is kept slightly tensioned.

Qe to and fro movement of the control slide of the distributor is via the connecting piece 23 as a function of the relation the winch 10 easily causes. It should be noted that the crank linkage given as an example should be prove to be unsuitable, can be replaced by such a device known per se, which is attached to the respective Reversal points of the oscillating rotary movement of the winch 10 is actuated..So is in Fig. 3 ice. Embodiment shown, which comprises a lever 34- which is pivotable about an axis 35 which is attached to the frame 11 and which has two feeler elements 35a and 35b, which can work together with a finger 36 attached to the gearwheel 10b, and via a switching rod 37 is connected to the movable part of the distributor 20. The adjustable feeler elements on the lever 35 in the inner position 35a and 35b are the organs for controlling the stroke length of the piston 6.

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When establishing the connection between the chambers of the Motors 12 and the two stores 15 and 17 »i.e. at When this motor reaches its maximum torque, the liquid escapes from motor 12 through line 18 and then by the branching off from the line 22 line 31 and the tared valve 32 back into the container 30. The absence the liquid in the circuit due to this return to the container is controlled by the power of the volumetric pump 28 balanced.

In the case of motor 13, only a certain amount of liquid is transferred over from memory 15 to memory 17 and vice versa determined, depending on whether the piston is on the way up or down is. The motor I3 cooperating with the two accumulators 15 and 17 thus forms a hydraulic Mermotor. However, a simple spring motor could be equivalent be considered. Definitely will be during the movement of the piston 6 downwards gained energy, which the drive device during the upward movement of the piston 6 is fed back.

It is noteworthy that the inertia of the motor 13 is lower than the inertia of the classic counterweights. Using the motor 13 is also dangerous Swinging such counterweights switched off. Finally, savings in the size of the system are also achieved which facilitates their manufacture, all the more so as the elements of a hydraulic circuit are very easily attached the circumstances can be adapted and built what to is already known.

The following is the workflow of the FIGS. 4-6 illustrated embodiments described.

For the embodiment shown in FIGS the individual phases of the work process are first examined on the basis of the upward movement of the weight 38. the Winch 10 is arranged at a certain angle, and their

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Rotation speed is zero. The angular position the winch 10 corresponds to the angular position of the cam disk 61, that is, a position of the rod 64 which is opposite to the Central position under tension of the compression spring 69 in cooperation with the washers 67 »68 and the stop surfaces 65 »66 is shifted. The bolt 72 has so aligned the lever 45 in a position in which the effective Working area is maximum and therefore the upward torque of the motor 39 at constant pressure of the liquid inlet as well is maximum. The pressure resistance will be discussed further below. The engine drives under these conditions 39 the winch 10 in the direction of the upward movement of the weight 38, the motor torque being greater than the drag torque the force of gravity and the force of friction.

The weight 38 rises and the cam 61 rotates in. taking rod 64 and lever 45 with it Direction of the reduction in the effective working area of the motor 39 », ie the reduction in the motor torque. On one At a certain point, the engine torque corresponds to the resistance torque, then it becomes lower than this. The weight 38 so continues to rise until its speed becomes zero.

The weight 38 then begins to sink, the moment due to gravity being greater than the motor moment, which is still acting in the same direction but is reduced. The cam 61 rotates counter to the direction during the upward movement and moves the lever 45 in the direction of increasing the effective working surface and strengthening of the torque of motor 39. The Motormomeifc is again greater than the moment of the gravitational force and the frictional force. The weight 38 continues to drop, but at a decreasing speed. When the speed is zero , it is moved up again and a new work cycle similar to the one just described begins.

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With a single drive motor a drive of the symbolic e.g. a pumping device corresponding to the pump 4-5-6 became possible Or the like. Representing weight 38 achieved in alternating directions without having to use counterweights or the like had to be used.

It has been mentioned above that during the increase in weight 38 the pressure in the chamber 49 of the motor 39 conducted liquid is essentially constant. This approximate constancy naturally depends on the characteristics of the the supply circuit of the motor 39 forming elements and, depending on the variable effective geometry of the Motor 39, the capacity of the memory 48, which must be sufficiently large, and the power of the pump which must also be large enough to compensate for the feed to the motor 39 fed from the memory 48.

Otherwise, the feed circuit functions as indicated above. When the weight 38 remains in its lower position, the rotor of the motor 39 is also stopped. The pump 47 sucks liquid from the container through line 53 and accumulates it in reservoir 48 and lines 54 and 51 · If If the dynamic pressure exceeds a certain value under certain circumstances, the tared valve 57 and that of the pump open 47 additionally pumped liquid will be returned to the container 30 through the lines 56 and 52.

The pressure of the liquid located in the reservoir 48 is dimensioned in such a way and the effective geometry of the motor 39 is controlled in such a way that the motor 39 drives the winch 10. The chamber 49 of the motor 39 is thus fed with hydraulic fluid from the memory 48 and the line 51; It is returned to the container 30 via the chamber 50 and the line 52 with little or no pressure. The memory 48 is designed in such a way that the supply pressure * r chamber 49 remains relatively constant during the increase in weight 38 , with a tendency to decrease in pressure.

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During the descent of the weight 38 this takes the winch 10 with and thus drives the motor 39 in the opposite direction Direction to buoyancy. The motor 39 works as a pump, sucks the liquid from the container 30 through the line 52 and the chamber 50 and presses the liquid into the Storage 48. The pressure of the liquid therein then increases under the action of the liquid supplied by the motor 39 and the continued to be supplied by the pump 47. The storage of the released by the downward movement of the weight 38 potential energy takes place there also in elastic form via the combined action of the motor 39 and the Memory 4-8, which form a hydraulic spring motor.

The total amount of the chamber 49 during the upward movement fluid supplied by body 38 is greater than that Total amount of by the motor 39 in the line 51 during liquid returned from the downward movement of the body 38. A test run as well as the evaluation of the working diagram of the motor 39 confirm this. This peculiarity explains the Necessity and role of the pump 47, which is to to provide the additional amount of fluid that is missing from each work cycle.

Finally, the workflow of the embodiment shown in FIGS. 4 and 6 is examined. If the Winch 10 in the direction of upward movement of weight 38 rotates, the volumetric pump 77 is driven via the shaft 43 of the motor 39. For example, consider the case that they the pressure fluid through its chamber 78 in the Line 86 pushes. The flow rate of the drainage liquid on the pump pressure side depends on the speed of rotation of waves 43 and 80 and is usually proportional to it. This amount must pass through the calibrated opening 90 of the throttle valve 89 to get into the other chamber of the pump 77. The throttle valve 89 causes that the pressure in the line 86 is increased in accordance with the throttling of the liquid as it flows through the opening 90.

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The liquid in the line 86 thus acts in the chamber 82 on the piston of the cylindrical housing body 75 and presses the rod 83 and the lever 45 in the direction of reducing the drive torque of the motor 39 and thus the speed of the shaft 43 · the speed or power of the motor 39 and thus also the delivery rate of the pump therefore decreases until it is equal to zero. The lever 45 is returned to its central position by the spring 69, and the winch 10 is then driven by the downward moving weight 38 in the opposite direction to the previous direction. The pump 77 is also driven in the opposite direction and presses the liquid into the line 87-As before in the line 86, the pressure in the line 87 rises and the lever 45 is guided in such a way that the torque of the motor 39 is increased. The workflow should appear very similar to that of the exemplary embodiment shown in FIG. However, the control is no longer primarily carried out by the position of the weight 38, but rather by the drive speed of the pump 77, ie ultimately the speed of the weight 38.

It should be noted that the arrangements of FIGS and 6 can be combined to achieve a work flow that is simultaneous with position and speed of weight 38 depends.

Finally, it is recalled that the drive device shown in FIGS. 1 to 3 comprises a drive motor, which is first fed with a pressure fluid at regular intervals in order to avoid active, power-consuming Phase of the driven organ to deliver a positive torque, then short-circuited by connecting the inlet to the outlet in order not to provide a moment during the passive work phase.

The transition from one circuit to another or from a given moment to a moment 0 can lead to shocks,

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which are detrimental to the service life, in particular of the driven organ on which they act. In the FIGS. 4 to 6, on the other hand, allows the workflow to change the torques continuously. This way, there are no jerky movements during the workflow.

Deviations and changes are possible without departing from the scope of the invention. The invention is. i.a. for example also applicable to the drive of an eammbär to drive stakes, as can be seen, for example, from the symbolic use a weight 38 as a driven organ of a general nature without further results.

Claims (17)

- IU * " Claims 1 · Drive device for upward and downward movement at constant. variable speed of a heavy body or the like. Driven organ that or with a drive motor is connected via a tension member, whereby the forces transmitted to the body by the motor are alternately greater than those on the body acting gravity and the frictional forces are and act in opposite directions, and smaller than that Gravity and the frictional forces, and where a device counteracting this gravity is constantly connected to the drive * motor is connected, characterized in that the counteracting Device comprises a spring motor (13i 39). 2. Drive device according to claim 1, characterized in that the spring motor (13) is a liquid-operated reversing motor with two chambers, one of which is continuously connected to a first hydraulic fluid reservoir (15) and the other is continuously connected to one second hydraulic fluid reservoir (17) is connected. 3. Drive device according to claims 1 or 2, characterized . characterized in that the tension member (9 »9a) is flexible and wound on a cable winch (10) which is connected to the drive motor and the spring motor is connected. 4 ·. Drive device according to one of claims 1 to 3 » characterized in that the drive motor (12) is a fluid-operated reversible motor with two chambers, One of which is permanently equipped with a liquid reservoir (17) and the other is optionally adjustable in two positions via one Distributor (20) is connected to a pressure fluid source (pump 28) or the memory (17). 5. Drive device according to one of claims 1 to 4-, characterized in that the pressurized fluid source is a comprises volumetric hydraulic pump (28), with the pressure side of which a pressure fluid reservoir (15) is connected. 209829/0585 6. Drive device according to one of claims 1 "to 5» characterized in that the pressure fluid source is a gas compressor, with its pressure side a pressure fluid reservoir connected is. 7. Drive device according to one of claims 1 to 6, characterized in that the adjustable in two positions Distributor (20) comprises a movable control part which is connected to a control device (23). 8. Drive device according to one of claims 1 to 7 »characterized in that the control device (4-5) of the movable part is connected to the spring motor (39). 9. Drive device according to one of claims 1 to 8, characterized in that the connection of the movable Partly with the spring motor (39) comprises a control device. 10. Drive device according to one of claims 1 to 9 » characterized in that the second store (17) is also connected to the drive motor (12). 11. Drive device according to one of claims 1 to 10, characterized in that the first memory (15) also with the volumetric hydraulic pump (28) is connected. 12; Drive device according to one of Claims 1 to 10, characterized in that the first store (15) also includes is connected to the gas compressor. 13. Drive device according to one of claims 1 to 12, characterized in that the drive motor (39) at the same time is designed as a spring motor and as a liquid-operated reversible motor with two chambers (4-9, 50), one of which (49) continuously via a first line (51) with a hydraulic fluid reservoir (48) and the other (50) via one second line (52) with a liquid storage container (30) 209829/0586 is connected, wherein the spring motor (39) has a variable effective geometry and a control member (4-5) for Includes control of the pressurized effective area, and the entire drive device comprises a pressure fluid source (pump 47) with a pressure line (54-), the is connected to the first line (51) and a tared throttle valve (57) in a branch. 14. Drive device according to one of claims 1 to 13, characterized in that the drive motor (39) has a Includes rotor, with which the control member (4-5) is connected to change the drive torque. 15 · Drive device according to a cifer claims 1 to 14-, characterized in that the position of the control organ (4-5) is via single Sfnematic chains (10, 41, 3-ΙΓ 6O / 59 ", 739a, '61, 774, _64V, 72j 73) -7comprehensive regulation (46) depending on from "the position of the driven organ can be changed. (Fig. 5) 16. Drive device according to one of claims 1 to 15 »characterized in that the position of the control element (45) by means of a control chain (43, 80, 77) which scans the rotational speed of the rotor of the drive motor (39) and transmits it to the control element (45) , 86, 87, 88, 89, 75, 83, 84, 85) comprehensive control device (46) can be changed as a function of the current speed of the driven member. (Fig. 6) 17. Drive device according to one of claims 1 to 16, characterized in that the device for sensing and transmitting is a volumetric, reversible hydraulic pump (77), the drive shaft (80) of which is connected to the rotor of the drive motor (39), a double-acting volumetric.es receiving element (75) with the control element (45) 209829/0585 is connected to the change of the drive momentum, the volumetric The pump (77) and the receiving member (75) each have two Chambers (78, 79 »81, 82), of which one chamber (79) of the pump (77) via a line (87) with the one chamber (81) of the receiving member (75) and the other Chamber (78) of the pump (77) connected to the other chamber (82) of the receiving member (75) via another line (86) is, wherein a further short-circuit line (88) connecting the two lines (86, 87) also has a throttle element (89) is arranged, finally the control member (45) to change the drive torque with an elastic Return element (62) is connected, which holds the control member (45) in a given position or leads back there. 2 0 9 8 2 9 / C) B 8 5