EP0455258B1 - Method for operating a pneumatic motor and device for working the method - Google Patents

Description

The invention relates to a novel method for driving a pneumatic motor and a device for performing the method.

The new method replaces conventional gasoline or diesel engines or all types of internal combustion engines.

All previously known methods and devices for driving motors have the disadvantage that they have a relatively low efficiency.

The invention has for its object to provide a method and an apparatus for performing the method, which has a system with which a much larger power factor than that which was possible with previously known engines can be achieved and with which it is possible to drive energy to use in an economical and effective way.

According to the invention, the object is achieved by the characterizing features of method claim 1, further developments being achieved by method claims 2, 3 and 4; the object is also achieved by the characterizing features of claim 5, wherein further refinements are achieved by the features of claims 5 - 10.

According to the invention, there is the advantage that energy can be stored during the work process and used in the subsequent work process, so that energy storage of up to 80% can be achieved after the start-up phase has ended.

The drawing shows two exemplary embodiments of the subject matter of the invention.

A table (A) is attached, which gives the percentages of pressure recovery that can be achieved after the start-up procedure has ended during the normal working phase.

Fig. 1

einen der in Reihe geschalteten Zylinder entsprechend der Stellung des Zylinders II gemäß Fig. 3 in vergrößertem Maßstab;

Fig. 1a

den Gleitkolbenteller 11 mit den mit diesem einstückig verbundenen sich nach aufwärts erstreckenden Schubstützen und den sich nach abwärts erstreckenden Zweigen;

Fig. 2

sechs der in Reihe geschalteten Arbeitszylinder von insgesamt acht Arbeitszylindern, wobei die letzten beiden zur besseren Übersichtlichkeit fortgelassen worden sind im Längsschnitt;

Fig. 3

die ersten drei der in Reihe geschalteten Arbeitszylinder gemäß einem anderen Ausführungsbeispiel, wobei der Zylinder III in den drei Stellungen III a, III b, IIIc eine komplette Arbeitsphase des Zylinders III nach der Durchführung des Arbeitshubes darstellt;

ig. 4

vier der in Reihe geschalteten Arbeitszylinder gemäß einem anderen Ausführungsbeispiel der Durchführung des Verfahrens;

Fig. 5

eine Anordnung von acht zu einem Arbeitssystem zusammengefaßten Arbeitsdruckzylindern mit Verwendung zusätzlicher Kleinkompressoren zur Umströmkompression (wobei auch ein Umströmkompressor das gesamte System innerhalb des Umströmprozesses versorgen kann).

Fig. 6

zeigt die vertikal geringfügig bewegliche Befestigung des Zylindergehäuses der Steuerzylinder am Gleitkolbenteller 9A.

Fig. 7

ein zweites Ausführungsbeispiel eines zur Durchführung der Drucküberführung erforderlichen besonders gestalteten einseitigen Steuerzylinders;

In the drawing shows:

Fig. 1

one of the cylinders connected in series according to the position of the cylinder II of Figure 3 on an enlarged scale.

Fig. 1a

the sliding piston plate 11 with the upwardly extending thrust supports integrally connected thereto and the downwardly extending branches;

Fig. 2

six of the working cylinders connected in series of a total of eight working cylinders, the last two being omitted for the sake of clarity in longitudinal section;

Fig. 3

the first three of the working cylinders connected in series according to another exemplary embodiment, the cylinder III in the three positions III a, III b, IIIc representing a complete working phase of the cylinder III after the working stroke has been carried out;

ig. 4th

four of the working cylinders connected in series according to another embodiment of the implementation of the method;

Fig. 5

an arrangement of eight working pressure cylinders combined into a working system with the use of additional small compressors for flow compression (whereby a flow compressor can also supply the entire system within the flow process).

Fig. 6

shows the vertically slightly movable fastening of the cylinder housing of the control cylinder on the sliding piston plate 9A.

Fig. 7

a second embodiment of a specially designed one-sided control cylinder required for performing the pressure transfer;

The method for driving the pneumatic motor and using an energy-saving drive system is that the drive system includes a plurality of, for example, eight working cylinders I-VIII connected in series, as shown in FIG.

Each of these series-connected working cylinders I to VI contains, as shown in Fig. 1, a closed pressure expansion space 15, which contains a constant amount of compressed air throughout the working time, the chip pressure applied before the working thrust acts on the sliding piston plate 2, which acts with the Piston rod 5 is detachably connected via a locking lock 6 containing a locking device 3 to the piston rod 5 of the working cylinder which transmits the working power to the connecting rod device. This clamping pressure applied before the working push moves the sliding piston plate after the working push by 50% of its originally opened clamping pressure value 2 by the path length of the expansion with simultaneous work performance. In each of the working cylinders I-VIII, a pressure bypass chamber 16 is arranged in the area below the sliding piston plate 2, which is connected on the one hand to an injection pressure line 27 connected to a compressed air source 29, which is connected via controllable relay valves to the pressure bypassing chamber of all other working pressure cylinders and the on the other hand, is connected to a pressure bypass line 28 connecting the pressure bypass rooms of all working pressure cylinders I-VIII to one another via controllable relay valves, such that the working fluid expanding from the pressure bypass room 16 after the working stroke via the pressure bypass line 28 controllable by relay valves in the individual pressure bypass rooms 16 of the subsequent working pressure Cylinder can be stored (see Table A in this regard) and for re-opening the pneumatic clamping pressure in the pressure expansion chamber 15 partly from the pressure flue which is stored back into the pressure bypass chamber 16 of all subsequent working pressure cylinders dum can be retracted into the pressure bypass chamber 16 via the relay-controlled energy pressure bypass line 28 and the pressure fluid still required for the application of the required clamping pressure can be supplied via the injection pressure line 27 from the compressed air source 29, so that the slide piston plate 2 acting as the working piston moves upward again and the clamping pressure required for the next working stroke is raised in the pressure expansion space 15.

When using, for example, eight working cylinders I-VIII, 100% of the required clamping pressure is fed into the pressure bypass chambers 16 of the first three working cylinders from the compressed air source 29, the third working cylinder III carrying out the working thrust, with the pressure bypassing chamber 16 of the following working cylinder via the pressure bypass line is first connected in a relay-controlled manner to the pressure bypass chamber 16 of the next working pressure cylinder, 50% of the clamping pressure being stored therein after pressure equalization, whereupon the pressure bypass line is connected to the subsequent working pressure cylinder, where in turn at pressure equalization 50% of this clamping pressure are stored there and immediately until approximately 80% of the pressure fluid can be stored again during operation.

The residual pressure of the pressure bypass chamber 16 which is still required is passed into the subsequent container by means of a pressure fluid fed in from the compressed air source 29.

The large number of working cylinders connected in series can be used several times in parallel to ensure a continuous crankshaft drive.

For a better representation, the table assumes that the storable opening values within the pressure bypass chambers 16 and the missing residual values required for the following working stroke as injection energy after completion of the thrust via a compressor 30 from the free air of the compressed air source 29 and from this via the injection Pressure line can be supplied to the pressure bypass chamber 16. The pressure is diverted from the pressure bypass chamber 16 before the relief takes place at a pressure of 10 bar in the pressure bypass chamber 16 of the subsequent container, which is prepared for work with the full power of 10 bar, with one circulating compressor or several circulating compressors in the form of small compressors 32 for the system can be used.

This transfer corresponds to the power after the energy-free pressure circulation or equalization of a maximum of 20% of the energy to be delivered. Only about 1% wear energy is continuously supplied from the open air.

The pressure transfer takes place according to Table A from the pressure bypass chamber 16 of the working cylinder 1 in which the working thrust has just been completed, into the pressure bypass chamber 16, for example of the next cylinder III via the energy pressure bypass line 28, in which only the controllable control valves from Pressure bypass chamber 16 of this first working cylinder, in which the working thrust has just been completed, are open to the bypass chamber 16, for example of the next but one cylinder III.

wobei

D =

der ausgleichende Druck in Volumen % ist.

a =

der Anfangsdruck im Arbeitszylinder ist, in welchem der Arbeitsschub gerade vollendet ist und

b =

der Druck im Arbeitszylinder III ist, der vor dem Anfahrstadium = Null ist.

Pressure equalization follows according to the formula: $$\text{D =}\frac{\text{a + b}}{\text{3rd}}\text{=}\frac{\text{100 + 0}}{\text{3rd}}\text{= 33 vol\%}$$

in which

D =

the equalizing pressure is in volume%.

a =

is the initial pressure in the working cylinder in which the working thrust has just been completed and

b =

is the pressure in the working cylinder III, which is = zero before the start-up stage.

For the pressure fluid to be transferred, the compression effort is equal to the work effort of the flow compressor: $$\text{D =}\frac{\text{a + b}}{\text{2nd}}\text{= 50 vol.\%}$$

im Druckfahrraum dieses Zylinders gespeichert werden können, und sofort nach der Tabelle A.The pressure bypass chamber 16 of the working cylinder that has just completed the subsequent work boost is then connected in a subsequent process step via the pressure bypass line 28 with the corresponding setting of the controllable control valves to the pressure bypass chamber 16 of the next cylinder IV, after corresponding pressure equalization $$\text{D =}\frac{\text{50 + 0}}{\text{2nd}}\text{= 25 vol.\%}$$

can be stored in the pressure range of this cylinder, and immediately according to table A.

As can be seen from FIG. 1, the working cylinder has a sliding piston plate 2, which is in contact with the pressure expansion chamber 15, as the working piston, which can be locked by means of a locking means 3 of a locking lock 6 with the piston rod 5 running through a guide 4, with a certain distance below the sliding piston plate 2 a sliding piston plate 9 and one with an upward and in sliding seals and sliding openings 10 through the sliding piston plate 9 extending thrust supports 7 is provided sliding piston plate 11 which is provided with controllable valves c, the pressure evacuation space 16 being closed at the bottom by a lockable piston plate base plate 12, these thrust supports 7 being rigid with the sliding piston plate 11 are connected.

The with the sliding piston plate 2 integrally connected guide 4 can be locked by means of a lock 3 '. The sliding piston plate 9 can be replaced by two sliding piston plates 9A and 9B, the upper sliding piston plate 9A being rigidly connected to the cylinder housing 50 of a control cylinder 8 according to FIG. 6, the lower sliding piston plate 9B being connected to the piston rod 52 of a reversible piston 51 of this control cylinder 8 is rigidly connected.

When reversing the control cylinder 8, the same pressure from the flow compressor 30 'retracted pressure is constantly reversed into the back pressure chamber.

The thrust supports extend through all sliding piston plates 9A and 9B, but not through the sliding piston plate 2, but their downward branches 7 'also extend through the sliding piston plate base plate 12, which ensures that the rigid attachment of the sliding supports 7 on the sliding piston plate 11 Displacement of the sliding piston plate 11 no thrust or pressure build-up occurs. All valve, switching and locking systems are controlled electrically.

In order to prevent vacuum formation when moving the sliding piston plates 9A and 9B apart, an opening in the sliding piston plate 9a is free, which creates a connection to the atmosphere.

7 shows a further exemplary embodiment of a control cylinder 41 which can be controlled on one side and is required to carry out the pressure transfer.

During the pressure relief, but still before the transfer of residual pressure in the pressure bypass chamber 16, the sliding piston plate 2 rests continuously on a release ram 38 and presses a pair of scissors 39 which act as an expansion clamp, because the release ram 38 is equipped with a spring 40 with a low spring tension.

When the pressure transfer begins, the plungers 37 are retracted by the displacement of the sliding piston plates 9A and 9B and locked at the top dead center of the opened or contracted sliding piston plates 9A and 9B, the surface pressure of the sliding piston plate 2 on the release stamp 38 decreasing as soon as the sliding piston plate 11 together with its thrust supports 7 is moved vertically upwards after locking.

The spreading clamp-type scissors 39 then close and the piston of the pressure ram 37 is locked.

The pressure stamp 37 only extends when the pressure in the pressure bypass chamber 16 has dropped to a certain level. When the pressure in the pressure bypass chamber 16 rises again, the pressure rams 37 are retracted by sliding plate displacement and locked at the top dead center of the retracted sliding piston plates 9A and 9B. The sliding piston plate 11 displaces the sliding piston plate 9B and, after it meets the sliding piston plate 9A, also vertically upwards; then the release die 38 is relieved of pressure, the scissors 39 and locks the stamp 37.

The pressure chamber 42 of the unilaterally controllable control cylinder 41 is connected by means of a pressure line to a pressure vessel 43, the volume of which is many times greater than the volume of the pressure chamber 42 in order to prevent a pressure drop in the pressure bypass chamber 16 during the pressure transfer.

Arranged in the housing wall of the cylinder is a pressure feed pipe 13 opening into the pressure expansion chamber 15, which is connected to the injection pressure line 27 coming from the compressed air source 29. The energy pressure bypass line 28 is connected to the pressure bypass chamber 16 by means of a connecting line 19, a connection connecting piece 17 connecting the space lying between the sliding piston plate 2 and the upper sliding piston plate 9A and the atmosphere being arranged in the lower region of this space in the side wall of each cylinder 1 .

The mode of operation of the pneumatic motor according to FIG. 2 is then explained.

As can be seen from FIG. 2, eight working cylinders I-VIII connected in series are provided, with only the first six of the eight cylinders connected in series being shown in FIG. 2 for the sake of clarity, and the last two being omitted. According to a first exemplary embodiment, the mode of operation and operating mode of the pneumatic motor are as follows:
The pressure circulation volume from pressure bypass chamber 16 to pressure bypass chamber 16 is represented with a partly pneumatic internal pressure circulation and partly the pneumatic pressure circulation of the same pressure volume takes place by means of small compressors 32 with a slight pressure increase.

In this type of representation, the value of the pressure of the pressure expansion volume and the volume itself in the pressure expansion space 15 and its expansion value depend on the power of the engine.

This type of pneumatic motor is operated, for example, with an initial load on the area of expansion on the area of the sliding piston plate 2 from 10 bar to 100 cm 2 area.
The pressure volume in the pressure expansion chamber 15 is a dm³ at 10 bar.

After the work and the expansion of the pressure volume in the pressure expansion space 15, the original clamping force, i.e. To maintain the original pressure value of the pressure volume for a new work, a pressure volume of 1 dm³ with a pressure of 12.5 bar, which loads the plate of the sliding piston plate 9 on an area of 80 cm², is stored in the cylinder in the pressure bypass chamber 16, which has to be renewed Work performance that is prepared in the system connected in series.

At this moment, the original tension value of the pressure expansion space 15 becomes from the bypass space 16 by means of counter pressure Work done again. A pneumatic or hydropneumatic pressure in the control cylinder 8 can be used to control the circumferential torques of the pressure volume and for transferring residual volume pressure within the pressure bypass chambers of the individual cylinders. This pressure can be applied via a hydraulic pump, since it is a residual pressure, or if higher pressures are used to achieve a high work rate, the control system of the control cylinder 8 is operated via a compressor.

The pressure present in the control line system according to FIG. 6, which is responsible for the control cylinder 8, is generally always approximately constant, because when the slide piston plate in the control cylinder 8 is shifted, the pressure volume, the volume of which is constant, is bypassed with a small circumferential deviation.

The pistons of the control cylinder 8 have an area of 15 cm².

Two control cylinders 8 are incorporated in each working cylinder.
When transferring the residual pressure in the pressure bypass chamber 16, the pressure rams of the control cylinder 8 whose total area is 30 cm 2, the sliding piston plates 9B extend with their large pressure surface over a path length of 10 cm in order to bypass the residual pressure from this pressure bypass chamber 16.

The load on the sliding piston surface 9B is 375 kg per 80 cm² area.

In order to be able to bypass this pressure, a control pressure of 12.5 bar is applied to the piston of the control cylinder 8 with its 30 cm² total area, which within the bypassing process of transferring residual pressure in the pressure bypass rooms by means of the intermediate small compressor 32 up to a maximum of 15 bar is increased.

The thrust supports 7 have a cross-sectional area of 10 cm² and in their vertical course in the pressure bypass chamber 16 which has a height of 10 cm, they consequently occupy 200 cm³ of the volume of the pressure chamber.

Thus the pressure volume of the pressure bypass chamber is 16 1000 cm³ at a pressure of 12.5 bar.

The preparation phase for operating the pneumatic motor according to FIG. 2 is then described.

For example :

In the cylinders I-VIII, a certain pressure filling quantity is injected in the pressure expansion spaces 15 from the compressor 30 via the pressure injection line 27. It is the same in all pressure bypass rooms 15.
The expansion size of the expansion spaces 15 has a different volume within each cylinder before the engine is started up.
Therefore, the pressure is lowered at different heights according to the size of the room.
In the pressure expansion chamber 15 of cylinder I, 1 dm³ at 10 bar, in the pressure expansion chamber of cylinder II, 1 dm³ is also filled to 10 bar.
In the pressure expansion chamber 15 of cylinder III, filling is carried out to 5 bar in accordance with the control stand filling with a room volume of 2 dm³.
The pressure expansion chamber 15 of the cylinder IV has a room size of 3 dm³ which is filled with 3.75 bar of pneumatic volume.
The pressure expansion space of cylinder V is brought to 6.25 bar with 2 dm³ at 5 bar and the pressure expansion space 15 of cylinder VI with 1.75 dm³.
In this position, the pressure expansion chamber 15 of cylinder VII holds 1.20 dm³ at 8 bar and the pressure expansion chamber of cylinder VIII at 1 dm³ again has a pressure volume of 10 bar.
The pressure bypass chambers 16 of cylinders I and II are each filled with 1.6 dm³ and 12.5 bar.
The same is in the pressure bypass chamber 16 of the cylinder III; the pressure bypass area of cylinder IV is in the retracted position and has no pressure or pressure volume.
The pressure bypass area of cylinder V is filled with 0.8 dm³ and 6.25 bar.
The pressure bypass chamber 16 of cylinder VI has a pressure of 7.8 bar with a room volume of 1.1 dm³. In cylinder VII the pressure bypass chamber 16 has a volume of 1.44 dm³ at 10 bar and cylinder VIII in the pressure bypass chamber 16 has a pressure chamber size of 1.6 dm³ at 12.5 bar.

In the control line there is an opened control pressure for controlling the control cylinder 8 of 12.5 bar. The control line, which was not drawn in for reasons of space, is operated in the control system approximately as the pressure bypass line shown in the system.

According to the above, the position of the working cylinders I-VIII is shown in FIG. 2 of the drawing:
FIG. 2 shows this cylinder I with the pneumatic clamping pressure in the pressure expansion chamber 15 before the working thrust.

The sliding piston plate 2 is locked by means of the lock 3 'on the wall of the pressure cylinder.

Fig. 2 of the drawing shows the cylinder II with opened pneumatic clamping pressure with the sliding piston plate 11 retracted downwards together with the thrust supports 7 rigidly connected to them, so that these thrust supports 7 within the subsequent relief process in the pressure expansion chamber 15 the pneumatic pressure relief process by being placed on the Can not affect sliding piston plate 2 (before the working push). The space between the sliding piston plate 2 and the sliding piston plate 9A is connected to the atmosphere via the connector 17.
The relay-controlled valves c embedded in the sliding piston plate 11 are open.
The sliding piston plate 11 is moved within the pressure bypass chamber 16 without energy by the value of the spatial tension of the pressure expansion chamber 15 in relation to the relaxation path length.

Fig. 2 of the drawing shows the cylinder III in the position of the sliding piston plate 2 at the end of the working thrust, the locking 3 'released and the working sliding piston plate 2 down into the space cleared by the thrust supports 7 first by the path length down is moved until it rests on the thrust supports 7.
It now inserts the pressure transfer from the pressure bypass chamber 16 into the subsequent containers or into the following cylinders.
This is done via the constant energy pressure bypass line 28 (see the table).

Fig. 2 of the drawing shows the cylinder IV, in the position of the sliding piston at the end of the relief process. The valves C are open during the lowering process of the sliding piston plate 11.
In this case, the pressure from the pressure bypass chamber 16 is passed into the following containers or into the following cylinders. The remaining pneumatic pressure in the pressure bypass chamber 16 between the sliding piston plate 9 and the sliding piston plate 11 either remains in this space during the entire working process of the entire system connected in series during the bypassing process and is transferred into this space or, due to its small pressure size, it is by means of run over by a compressor 30 'drivable control cylinder 8 in the subsequent container or cylinder.

Cylinder V shows the position of the sliding piston plate in which the pressure fluid is completely transferred to the successive container or cylinder and a renewed loading of the pressure bypass chamber with pressure fluid can begin.

Cylinder V of FIG. 2 of the drawing shows the thrust piston rod 5, which is idle again via the crankshaft and connecting rods, the pressure-relieved pressure bypass chamber 16, the adjoining sliding piston plates 9 and 11 in the pressure bypass chamber 16, and the expanded pressure expansion chamber 15. The thrust supports 7 of the sliding piston plate 11 lie on the underside of the sliding piston plate 2 and it can after the pressure expansion of the subsequent container, ie after its work and its beginning relief in this container or cylinder via the constant pressure bypass line 28 in the pressure bypass chamber 16 again injected pneumatic pressure (see table of the constant pressure circulation). The sliding piston plate 9A, 9B and the sliding piston plate 11 remain together in the opening process, the relay-controlled valves C of the sliding piston plate 11 are closed, the pneumatic pressure now entering via the constant energy pressure bypass line 28 is compressed by moving the sliding piston plate 2 in the upward direction, the pneumatic pressure in the pressure expansion space 15 to its original value.

Fig. 2 of the drawing shows the cylinder VI shortly before the renewed work thrust. The sliding piston plate 2 acting as a working piston is pressed up to the upper locking device 3 'by means of running over pressure fluid to the locking device 3' and the sliding piston plate 2 is locked at the top dead center. The locking also takes place on the piston rod 5 by means of the locking 3 on the sliding piston plate 2.

The cylinders VII and VIII are not shown in Fig. 2 of the drawing in order not to unnecessarily complicate the drawing. All subsequent containers have the same volume and are exposed to the same pressure. This ensures uniform pneumatic pressure transfer and pressure build-up in each working pressure vessel or cylinder with regard to pressure force and pressure volume.

Although it is possible to compress this space again directly after the pressure expansion in the pressure expansion space 15 by moving the sliding piston plate 11 to the sliding piston plate 9 with the relay valves closed, this requires a very high amount of energy because the compression energy in the pressure bypass chamber 16 is of the same size everywhere is present and a transfer of pressure fluid between the sliding piston plates 9 and 11 to the space between the sliding piston plates 11 and the locked piston plate base plate 12 is absolutely necessary.

In the operating mode shown, the pneumatic pressure relief process with pressure transfer by means of the constant energy pressure bypass line 28 into the following cylinders takes place by the relaxation of the pneumatic pressure in the pressure expansion space 15 and the associated steady relaxation of the pneumatic pressure in the pressure bypass space 16, with simultaneous pneumatic pressure transfer and the energy saving of 80%.
The residual pneumatic volume, which is transferred by means of compression, is very small in relation to its volume and pressure. The transfer uses very little energy. In terms of design, care should be taken that the pneumatic pressure in the pressure expansion chamber 15 before the average 50% relaxation for the purpose of relieving work is equal to the pneumatic pressure in the pressure bypass chamber 16.

The cylinder system can be connected in parallel several times in order to achieve better rotational movements of the crankshaft.

Fig. 3 of the drawing shows a complete working phase of the cylinder III, with pressure transfer after the working stroke.

The last three representations of the cylinder concern the cylinder III a in its first position, then the cylinder III b in its subsequent position and the cylinder III c in its final position, in which the residual pressure from the pressure bypass chamber 16 by means of the lowerable sliding piston plate 9B from the Pressure bypass chamber 16 of the same has been transferred via the energy pressure bypass line 28 into the other storing pressure bypass rooms. The pressure bypass volume, which after the working stroke of this cylinder III = 100%, is transferred in succession in the three phases shown. After the working stroke of the cylinder III, the sliding piston plate 9 can remain locked until the pressure volume from the pressure bypass chamber 16 of the cylinder III, which is first transferred into the cylinder VII, then into the cylinders VI-V and into the cylinder IV, has a pressure, which is less than the expanding pressure in the expansion space 15.

Then the locking of the sliding piston plate 9 is released, so that the thrust of the expansion pressure still present in the pressure expansion chamber 15 can transfer the pressure in the pressure bypass chamber 16 within the transfer to equalize a residual volume of 400 dm³. the remaining transfer takes place by extending the pistons 51 of the control cylinder 8 according to FIG. 3 of the drawing in the cylinder position according to cylinder III c.
The control pressure in the control cylinder 8 is 12.5 bar by means of a small compressor or hydraulic pump, depending on the type of application of the corresponding pressure medium, up to a pressure of max. 15 bar brought, the pressure bypass chamber 16 is emptied.

Engine run or operating time

According to a further embodiment, the cylinder II, due to its pressure volume in connection with the mechanical position of its parts, can do work by the expansion pressure in the pressure expansion space 15 expanding from 10 bar to 5 bar over a path length of 10 cm. At this moment, work on the piston rod is released in the form of an average force that is 750 kp over a path length of 10 cm.
Within this time sequence, the cylinder III according to FIG. 2 relieves the drawing, which its pressure bypass chamber 16 in which the cylinders VII-VI-V and IV within the pressure bypass chambers 16 are raised in the pressure volume, corresponding to the pressure volume in the pressure bypass chamber 16 of the cylinder III percentage decreases. The constantly constant driving values, which are approximately constant, can be seen from FIG. 2 of the drawing.

The control sequences in the moment of relief of the pressure bypass chamber 16 of the cylinder 1 can be seen in FIG. 3 of the drawing and have already been described in the preparation phase.
If we add up the pressure volume level of cylinder III and cylinder VII in the preparation phase, we have 100% in cylinder III and 80% in cylinder VII corresponds to 180% divided by two volume spaces = 90% in the pressure bypass chamber 16 of cylinder VII, i.e. 160 cm³ of the remaining pressure in cylinder III by means of the pressure bypass line and the small compressors 32 after bypassing the pressure in the pressure bypass chamber 16 of cylinder VIII, at one pressure of 12.5 bar can be recycled.
Thus, practically the cylinder VII, when it now mechanically retracts its thrust supports 7 with the valves C of the sliding piston plate 11 open, is prepared for work. The cylinder I has meanwhile completed the process just described, and can now do work by means of pressure expansion in the pressure expansion chamber 15, the cylinder II initiating the relief process of the pressure bypass chamber 16, starting with the transfer of pressure into the cylinder VI and this to 90% of the required pressure volume brings in the pressure bypass chamber 16, so that in turn a residual pressure of 10% of the 10% pressure volume of cylinder II and cylinder VI must be returned in the reversing process.

As a result of the continuous work performed by the pneumatic motor, the continuous functional process in the change phase is shifted one cylinder to the left. There is a rotation of the described individual processes.

The pressure volume required for a working stroke is 1000 cm³ at a pressure of 12.5 bar in the pressure bypass chamber 16, taking into account the one-off, initial filling torque of the pneumatic motor, 80-90% of which are generated by self-circulation and approx. 20-10% by small compressor 32 must be returned.
At 20% volume pressure return within the pressure bypass chambers 16, this corresponds to a rise in pressure of 3.75 bar and approximately 980 cm³ volume to 12.5 bar at 320 cm³ volume, based on the expansion phase of the work performed within a working stroke approx. 40% energy expenditure for this process.

For transferring the residual pressure by raising the control pressure into the plunger 8, an energy expenditure of 5-7% of the work achieved is required, so that, without taking into account the frictional losses, the pneumatic motor can in this way still give approximately 50% work within the operating time without energy consumption.

The operation of the pneumatic motor according to a further embodiment shown in FIG. 4 of the drawing.

The active and operating variant of the pneumatic motor is shown without pneumatic internal pressure circulation within the pressure bypass chambers 16.

In this illustration, the size of the pressure expansion space 15 and the amount of the pressure volume of the pressure expansion space 15 as well as the expansion value of the pressure volume are dependent on the expected power of the engine.
The sliding piston plate 9 can be divided horizontally into a sliding piston plate 9A and a sliding piston plate 9B.
A ratchet lock 18 (FIG. 6) is arranged on the sliding piston plate 9A, in which the cylinder housing 5o of the controllable control cylinder 8 is fastened in a vertically movable manner, the piston 51 of which is fixedly attached to the sliding piston plate 9B with its piston rod 52.
The thrust supports 7 are slidable and run through all sliding piston plates and through the piston plate base plate 12. This guarantees in the retraction moment of the thrust supports 7 with the controllable sliding piston plate 11, on which the thrust supports 7 are firmly locked, that within the pressure circulation space 16 at the time of retraction of the mentioned sliding piston plate 11 no thrust or pressure build-up occurs. All valve, switching and locking systems are controlled electronically.
The pneumatic motor is operated by its expansion surface loading on the surface of the sliding piston plate 2 from initially 100 bar to 100 cm². This corresponds to an initial expansion space volume of 1o dm³ and 1oo bar.

The stroke length of the commute is 4o cm. Due to this stroke length, the expansion space volume in the expansion pressure space 15 has a pressure volume of 14 dm³ at 8o bar.

On the way of 40 cm of work done 9 t are needed. From the pressure bypass chamber 16, the plate of the sliding piston plate 9 is loaded with 122 bar on an area of 80 cm 2. This corresponds to the initial loading of the sliding piston plate 2 on the part of the expansion pressure space 15. However, this also guarantees that the sliding piston plate 2 is returned to the original tension value in order to obtain a new work performance.

To control the circumferential torques of the circulating pressure in the pressure chambers of the individual cylinders, a pneumatic or hydropneumatic pressure of 225-235 bar is used to prevent pressure relief within the pressure circulating spaces 16 during the pressure circulating process.

The control cylinders 8 have a cross-sectional size of 20 cm² per stamp on their printing plate surfaces.

Two of these control cylinders 8 are stored in each working cylinder, so that a control pressure of approx. 9 t is applied to the pressure volume within the pressure bypassing spaces 16 during the pressure bypassing process at a 4o cm 2 high-pressure surface load. The high-pressure control line is also switched via a flow compressor and pressure vessel.
With the piston 51 of the control cylinder 8, it guarantees the presence of a constant high pressure during a change of control of the control cylinder, this pressure being increased by a few bar in order to be able to bypass the pressure volume in the working cylinder within the pressure bypass chamber 16.

The control line, which is connected to the control cylinder 8, is not shown for reasons of clarity.

The preparation phase for operating the pneumatic motor according to FIG. 4 of the drawing.

4 of the drawing in the pressure expansion chamber 15 of the cylinders I and IV a pressure volume of 10 dm³ injected at 100 bar.
14 dm³ at 80 bar are injected into the pressure bypass chamber 15 of cylinders II and III.
In the latter pressure expansion spaces 15, the cylinders with their mechanics are in an expanded state.
The pressure volume in all expansion rooms is the same. The vertical sliding piston plate load of the sliding piston plate 2 is in the tensioned state from the pressure expansion space 15, in cylinder I and IV 100 bar = 10 t.
In the relaxed state of the pressure expansion spaces 15, corresponding to cylinders II and III, 80 bar = 8 t are applied to an area of 100 cm².
The expansion pressure path is 40 cm, the relaxation value of the expansion pressure volume in the expansion pressure space 15 is 20%.
The work involved over a 40 cm path length is 9 t. 4 of the drawing, 2 dm³ pressure volume at a pressure of 122 bar is injected into cylinders I and II and IV, III.
The tappets of the thrust supports 7, the cross section of which is 10 cm², with a barrel length of 40 cm within the pressure bypass chambers 16, make it necessary to increase the pressure volume present in the pressure bypass chamber 16 to 122 bar in order to achieve an equivalent pressure force compensation between the pressure bypass chamber 16 and the pressure expansion chamber 15 so that the 100% pressure compensation in the pressure expansion chamber 15 when driving around the pressure volume from the pressure bypass chamber 16 of one cylinder to the pressure bypass chamber 16 of another cylinder is guaranteed upon receipt of the 100% tension value in the pressure expansion chamber 15 to obtain renewed work.

The stamps of the control cylinder 8 are due to the control position in the cylinder I and II in the retracted position, in the cylinder III and IV in the extended position.

It should be noted that the sliding piston plate 9 is slidably movable up to its uppermost locking position when the pressure and its volume are bypassed from the pressure bypass chamber 16 to the pressure bypass chamber 16.
The result of this is that the stamps of the control cylinders 8 move freely in the vertical direction when the pressure position is extended in the opening moment of the pressure opening spaces 16, as can be seen in the cylinder IV.
After reaching the clamping position of the piston plate surface 2 at the moment of its locking, the control high pressure is switched to the control cylinder 8, the sliding piston plate 9A remains freely movable, the sliding piston plate 9B is locked and the sliding piston plate 9A moves vertically downwards to the sliding piston plate 9B, with the sliding piston plate 11 simultaneously the thrust supports 7 moves vertically downwards. The vertical downward movement of these parts is 40 cm path length to ensure a working stroke.

Before the onset of a working stroke within a cylinder, which is caused by the downward movement of the sliding piston plate 2, the upwardly extending thrust supports 7, together with the sliding piston plate 11 rigidly connected to them, with the valves c open, have to be moved downward in the pressure bypass chamber 16 with little mechanical energy expenditure Path length of the working stroke can be reduced. This can be done in that a rack section of a mechanical rack and pinion control system 33 is attached to the lower end of one of the downwardly extending branches 7 'of the thrust supports at a height below the sliding piston base plate 12, and this meshing with the gear on the outer Cylinder wall is attached and can be driven via the connecting rod or crankshaft.
In the rack-and-pinion control system 33, the engagement between the gear and the rack can be released by any control system, so that the sliding piston plate 11 with its upward thrust supports 7 and also with downwardly extending branches 7 'is freely displaceable.

Engine run and operating time. The start-up phase was described in accordance with FIG. 4 of the drawing. According to this figure 4, the operating time now begins.
In cylinder I releases the lock 3 'of the sliding piston plate 2 with a pressure of 9 t on a 40 cm path length. The sliding piston plate 2 moves vertically downward when the piston rod 5 is driven to actuate the crankshaft until it rests on the control cylinder 8.
In this time phase, the control cylinders 8 in cylinder II now extend their piston rods 52 by a small compressor 30 'by means of a reversible line 20, which now acts on the top of the piston of the control cylinder 8, space "a" and the pressure during the work process by a few bar increased to increase pressure.
Within the vertical sliding surface on the sliding piston plate 9A with raster locking 18, in which the control cylinders 8 find guidance and are vertically movable by a few millimeters, the high-pressure stamp 8 moves by this difference, so that the expanding pressure means once on the cylinder housing 50 of the control cylinder 8 the surface of the sliding piston plate 2 generates a pressure effect from the pressure expansion space 15 and, on the other hand, the extending piston rods 52 of the control cylinder 8 are exposed to an equivalent counter-pressure effect by means of the surface of the sliding piston plate 9B if the pressure volume from the pressure bypass chamber 16 of the cylinder II is now in the by means of the small compressor 32 Pressure evacuation space 16 of the cylinder III is transferred. The pressure expansion chamber 15 of the cylinder III compresses its expansion pressure volume from 14 dm ³ and 80 bar to 10 dm³ and 100 bar in this time sequence when the tension value is restored to achieve renewed work, the mechanical locks locking the sliding point when these sizes are reached.
During the described process, the line 20 from the compressor 30 'to the room b of the control cylinder 8 was switched over in the cylinder IV and the control cylinder 8 retracted, the sliding piston plate 9A, as already explained, moving vertically downwards and laying on the locked sliding piston plate 9B .

The cylinder housing 50 of the control cylinder 8 are thus also moved vertically downwards.
The thrust supports 7 are also retracted mechanically when the valve "c" of the sliding piston plate 11 is open.
The expansion stroke of the cylinder IV begins, that is to say that work is carried out in the cylinder IV in that the sliding piston plate 2 is released from its locking. The workflow just described completely within all cylinders is now shifted to the left by one cylinder in the following work phase according to FIG. 4 of the drawing.

The current pressure expansion phase within one cylinder is faster within the phase than the pressure circulation within the other cylinders.
This is due to the corresponding cross-sectional sizes of the pressure bypass line 28 and the correspondingly lower printing speeds in relation to the expansion force.
The cross-section of all line systems should therefore be kept as large as possible and the row of cylinders of an engine block according to FIG. 4 of the drawing should be connected in parallel several times, it being possible to offset the individual pressure expansion stages in order to ensure a continuous crankshaft drive.

The pressure volume required for a working stroke is dm³ or 4000 cm³, taking into account the one-off filling torque within the pneumatic motor, at a pressure of 122 bar and with an energy expenditure of approx. 10 bar max. be bypassed once. The energy expenditure for this working stroke within the control cylinder 8 is approximately equivalent to that just described.

According to the conventional way of generating an equivalent pressure volume, the same pressure volume is probably required for an equivalent performance for each working stroke, at a pressure which must be brought from 0 to 100 bar.

The efficiency factor of the pneumatic motor increases by at least 700 to 800% in contrast to the conventional type of compression energy systems for operating pneumatic motors.
In other words, a pneumatic motor of this type needs around 20% of the work it produces to compare the operation of the system without taking wear and friction losses into account, in order to maintain the operator process and can continuously state 80% of the work as power for operating system systems.

The pneumatic pressure energy of 33 to approximately 60 or 70% stored in the pressure bypass chamber 16 of the pressure cylinder 1 before the working stroke of the sliding piston plate 2 is to be introduced into the pressure circulation line 28 without any expenditure of energy with gradual pneumatic pressure compensation.
The remaining percentages of pneumatic energy remaining in the pressure flow process must also be transferred by volume flow compressors in the same way.

The process just described can also take place via two separate pressure circulation lines 28, a pressure circulation line transferring potential energy in volume flow from cylinder to cylinder in the flow process and the transfer being carried out in series parallel to this process by means of a flow compressor. Another possibility of pneumatic pressure transfer for the entire potential energy to be transferred by means of a pressure circulation line 28 is possible with a flow compressor 32 within the pneumatic system in that the individual compression chambers of the overflow compressor, regardless of whether they are piston compressors or wheel compressors, have connecting pieces in which non-return valves are installed.
These connecting pieces within the individual compression stages are closed with the pressure circulation line 28, so that the respectively required nominal pressure at the pressure connection which changes continuously in the bypassing process of the potential energy due to the pressure build-up of the pressure bypass chambers 16 can enter the pressure circulation line 28 in an energy-saving manner and from the respective pressure bypass rooms 16 is removed.

Furthermore, in the overflow or bypass process, the constantly changing suction pressure from the pressure bypass chamber 16, from which the compressible medium is extended, is to act on the reverse side on the surfaces of the parts in the bypass compressor which contribute to the compression.
This saves enormous compressor performance and the potential energy of the free circulation transfer via the compressor or through the compressor does not impair the necessary transfer performance of the flow compressor or the flow compressors.

The flow compressor is intended to transfer some of the stored potential energy, for example from cylinder I to cylinders III-VIII, for further use.

Active power of a compressor with buffer volume within a pneumatic motor.
The compressed air has to suck out from the pressure bypass chamber 16 of the cylinder 1 in a very short time, for example similar to the expansion time of the air.
The potential energy has to be conveyed into the cylinders III-VIII via the pressure circulation line 28 in which a bypass is arranged in relation to the stroke volume of the compressor and a buffer volume container which is at least 10 times the stroke volume. The pumping out of the air volume from cylinder I and the inflow of compressed air of, for example, up to 11 bar while observing the constructively promoted parameters for flow compressors into cylinders III-VIII are timed by control elements.
With a 10-fold cylinder stroke volume of the buffer, the pressure only fluctuates by approx. 1 bar during the work cycles. Pressure can flow from the buffer into the cylinder volume of the leading piston in cylinder 3 even before it is fed from cylinder 1.

This comes from the reserve of the penultimate working stroke of cylinder 1.

W = 1100 Nm (bei gewählten
   V₂ = 1 dm³
   p = 11 barThe work stored in cylinders III-VIII at the end of the pressure transfer process is $$\text{W = P x V = 1100 N / m² x 1 dm³}$$

W = 1100 Nm (with selected
V₂ = 1 dm³
p = 11 bar

höher, also beträgt $${\text{W}}_{\text{k}}\text{= W x}\genfrac{}{}{0ex}{}{\text{1}}{\text{hk}}$$

The required coupling work of the compressor still lies around the product with the reciprocal coupling efficiency $\genfrac{}{}{0ex}{}{\text{1}}{\text{hk}}$

higher, so is $${\text{W}}_{\text{k}}\text{= W x}\genfrac{}{}{0ex}{}{\text{1}}{\text{hk}}$$

The function required for the overflow from the pressure bypass chamber 16 of cylinder I to the pressure bypass chambers 16 of cylinders III-VIII by means of a compressor, including a buffer volume, results from the function $${\text{w}}_{\text{K}}{\text{= fp}}_{\text{m}}\text{x V₂}$$

der thermodynamischenFrom the expression $$\frac{\text{P₂}}{\text{P₁}}\text{x}\frac{\text{n. 1}}{\text{n}}\text{= 1}$$

the thermodynamic

Gas laws result for the pressure ratios between 1 and 11 bar $$\text{(II =}\frac{\text{P₂}}{\text{P₁}}\text{between 1 to 11)}$$

In the case of an isotropic change in state n = 1.4, an average pressure ratio for the calculation of the work required during the suction process from 11 to 1 bar from
II m = 4.4 (Dubbel I / 1955, p. 749)

w

= P_m x V₂
= 430 N/m² x 1 dm³

w

= 430 N/m

The required overflow work from cylinder I to cylinders III-VIII will be

w

= P _m x V₂
= 430 N / m² x 1 dm³

w

= 430 N / m

The work saved is

As with the normal filling of cylinder I from 1 to 11 bar, the coupling work required is the product with the reciprocal coupling efficiency.

However, the isothermal coupling efficiency, which is 0.534 kT from 1 bar to the respective nominal output, also improves by 60 when an overflow compressor works within a pneumatic motor due to the shortened operating time of the compressor, the pressure medium that is used, which loads the compressor with a medium pressure %.
It increases from 0.534 kT to 0.854 kT.
The overflow compressor therefore only needs a clutch output of P _K = 40%.

The pneumatic motor, in which work is carried out in the pressure evacuation chamber 15 of the individual cylinders by means of the sliding piston plate 2 in the relief process, should, in terms of effectiveness, perform the work which was carried out in the pressure circumvention rooms 16 of the individual cylinders.

In the expansion process, the amount of work that is given decreases continuously along the length of the expansion path.
It is therefore imperative that a flow compressor gradually feeds this work into the respective pressure bypass chamber 16 of the cylinders, each with a variable nominal output.

This guarantees that as a percentage, the work in the pressure bypass rooms with a small amount of energy can be taken off as a work rate in a much larger percentage ratio, provided that the design parameters of a flow compressor, that is, the connecting pieces of the chambers within the individual compressor stages are built with check valves opening with pressure direction to the pressure circulation capacity 28 and within the overflow or bypass process the respectively changing suction pressure from the pressure bypass chamber 16, from which the compressive medium is extended, is on the reverse side within the bypass compressor on the surface of the parts which contribute to the compression.

If the pressure fluid from a pressure bypass chamber 16 of a cylinder to be transferred is not run down to 1 bar during the transfer process to the subsequent cylinders, i.e. if there is a residual pressure fluid of several bar, the sliding piston plates 9a and 9b divide with the help of the extending control cylinders 8 and the residual pressure volume is transferred to the subsequent cylinder responsible for this at a constant pressure.

The parameters of increased pressure transfer do not have a disadvantageous effect in relation to the parameters of the always increasing mean pressure transfer in connection with the free pressure circulation, which are responsible for the performance of the flow compressor.

The performance of a pneumatic motor within the operating time.

In order to obtain expansion work in the expansion pressure chamber 15, compressed fluid is drawn in by means of a compressor in the pressure bypass chamber 16 in the start-up process and thus with a coupling active factor of 0.534, a pressure of 1 bar is brought to the respective nominal output.

Required workload 2050 Nm.
For an actual output of 1100 Nm.

In order to keep this 1100 Nm constant in the operator process of the system, the circulation compressor now works with a work saving of 60% due to the existing pressure medium, i.e. to get 1100 Nm work per stroke of the system the circulation compressor requires an energy expenditure of 430 Nm at one changed clutch factor of 0.854. Because the overflow compressor only has to transfer a maximum of 50% of the pressure fluid, which overflows the other pressure fluid in its own pressure circulation, until the respective pressure equalization within the transfer cylinder, this output is divided again by two; taking into account friction and wear losses, it is possible to obtain a workload of up to 200% within the operating process of the system for a 100% energy expenditure.
If an internal combustion engine, which serves as the drive unit of the engine, is connected upstream of the pneumatic one, the effective factor performance of this engine can improve up to 100%.
A generator which is driven by means of the pneumatic motor can be connected to an electric motor with a downstream pneumatic motor for obtaining work.
This guarantees that the electrical system operates within the operator process without energy expenditure and that up to 60% of the operator's own power required can be obtained either in the form of electrical energy from the generator or in the form of kinetic energy via the pneumatic motor.

Instead of the flow compressor, it is possible to set a hydraulic pump, provided that each pressure bypass chamber 16 of a cylinder within the pneumatic motor is followed by a hydraulic tank in which the expanding pressure fluid can expand from the pressure bypass chamber 16 and thus shift the respective nominal pressure to the hydraulic oil.
The hydraulic oil circulated by means of the hydraulic pump and entering the tank again compresses the respective pressure fluid around the corresponding pressure bypass chambers.
It should be noted that this variant never runs down to 1 bar in the pressure lowering and transfer process in the pressure lowering pressure bypass chamber 16.

A pressure fluid of medium pressure level must be run over by means of the control cylinders 8 and division of the sliding piston plates 9a and 9b from pressure bypass chamber 16 to pressure bypass chamber 16. The performance of the hydraulic pump also relates to the average load in the bypass process.

Favorable working conditions of the working cylinders can be achieved if the volume of the respective pressure expansion spaces 15 corresponds approximately to the volume of the respective pressure bypass spaces 16 in each individual case.

Should the temperature of the working cylinder exceed the permissible operating temperature during operation, a cooling system provided, which can be controlled by a temperature sensor, is switched on.

Claims (10)

1. Method for the drive of pneumatic motor with the use of a drive system which contains a plurality of working cylinders which are connected in series and each comprise a closed pressure expansion chamber (15), which during the entire working time contains a constant quantity of compressed air, the pressurising pressure of which - exerted before the working stroke and expanding after the working stroke in accordance with its originally attained pressurising value - moves the sliding piston plate (2) by the travel of necessary expansion during work performance, and a pressure bypass chamber (16) is arranged in each working cylinder, which chamber is connected on the one hand with an injection pressure duct (27), which is connected to a compressed air source (29) and by way of controllable relay valves with the pressure by-pass chamber (16) of all remaining working pressure cylinders, and on the other hand with a pressure by-pass duct (28) connecting the pressure by-pass chambers (16) of all working pressure cylinders one with the other by way of controllable relay valves in such a manner that the working fluid expanding out of the pressure by-pass chamber (16) is stored, by way of the pressure by-pass duct (28) controllable by relay valves, in the individual pressure by-pass chambers (16) of the following working pressure cylinders and - for the renewed attainment of the pneumatic pressurising pressure in the pressure expansion chamber (15) - partially the pressure fluid stored back in the pressure by-pass chambers (16) of all following working pressure cylinders is moved by way of the relay-controlled energy pressure by-pass duct (28) into the pressure by-pass chamber (16) partially in energy-free pressure by-pass and partially by by-pass flow compressor (32), wherein the pressure fluid still needed for the exertion of the required pressurising pressure is fed in the steady operating process from working cylinder to working cylinders by way of the injection pressure duct (27) from a compressed air source (29) pressure-loaded by means of a compressor (30) so that the sliding piston plate (2) acting as working piston is moved upwardly and the pressurising pressure, which is required for the next working stroke, is attained in the pressure expansion chamber (15).
2. Method according to claim 1, characterised in that in the case of the use of for example eight working cylinders (I to VIII), 100% of the required pressurising pressure is exerted in the pressure by-pass chambers (16) of the respective first three working cylinders (I to III) from the compressed air source (29), wherein the respective third working cylinder (III) performs the working thrust, wherein the pressure by-pass chamber (16) of the fourth working cylinder (IV) is connected by way of the pressure by-pass duct (28) initially relay-controlled with the pressure by-pass chamber (16) of the next working pressure cylinder (V), wherein 50% of the pressurising pressure is stored in this after pressure equalisation, whereupon the pressure by-pass duct (28) is connected with the following working cylinder, where 50% of this pressurising pressure is again stored there after pressure equalisation and so on until nearly 80% of the pressure fluid is stored and re-usable each time during the operation.
3. Method according to claim 1 or 2, characterised in that the pressure volume, which has remained behind in the pressure by-pass chamber (16) after pressure equalisation is moved over into the following containers by means of a by-pass flow compressor (30′) acting on a control cylinder (8).
4. Method according to claim 1 or 2, characterised in that the plurality of working cylinders connected in series is used seveial times running in parallel in order to assure a continuous crankshaft drive.
5. Device for the performance of the method according claims 1 - 4, for the drive of a pneumatic motor with the use of a drive system which contains a plurality of working cylinders which are connected in series and each comprise a closed pressure expansion chamber (15), which during the entire working time contains a constant quantity of compressed air, the pressurising pressure of whichexerted before the working stroke and expanding after the working stroke in accordance with its originally attained pressurising value - moves the sliding piston plate (2) by the travel of necessary expansion during work performance, and a pressure by-pass chamber (16) is arranged in each working cylinder, which chamber is connected on the one hand with an injection pressure duct (27), which is connected to a compressed air source (29) and by way of controllable relay valves with the pressure by-pass chamber (16) of all remaining working pressure cylinders, and on the other hand with a pressure by-pass duct (28) connecting the pressure by-pass chambers (16) of all working pressure cylinders one with the other by way of controllable relay valves, wherein
   by-pass flow compressors (32) are arranged in the pressure by-pass duct (28),
   a compressed air source (29) connected with the injection pressure duct (27) is connected with a compressor (30) to be loadable by pressure and
   small compressors (30′), which act on control cylinders (8) and serve for the complete emptying of the pressure by-pass chamber (16), are arranged in each cylinder
   and each working cylinder (1) displays a sliding piston plate (2), which lies against the pressure expansion chamber (15), as working piston which is lockable to a piston rod (5), which extends through a guide (4), by means of a catch (3) of a catch fastener (6) and a sliding piston plate (9) bounding the pressure by-pass chamber (16) is arranged at a certain spacing under the sliding piston plate (2) and thereunder a sliding piston plate (11), which is provided with controllable valves (c), wherein the pressure by-pass chamber (16) is closed off downwardly by an arrestable piston plate base plate (12).
6. Device according to claim 5, characterised in that the guide 4, which is rigidly connected with the sliding piston plate (2), of the piston rod (5) is lockable to and again detachable from the housing of the cylinder (1) by means of a catch (3′).
7. Device according to one of the claims 5 and 6, characterised in that in the cylinder wall of each cylinder (1), there is provided a pressure feed nipple (13) opening into the pressure expansion chamber (15) thereof as well as a pressure feed nipple (14) opening into the pressure by-pass chamber (16) thereof, both of which nipples are connected with an injection pressure duct (27) standing in communication with the compressed air duct (29), and a connecting nipple (17), which connects the space lying between the sliding piston plate (2) and the upper sliding piston plate (9A) with the atmosphere, is arranged in the lower region of this space in the side wall of each cylinder (1).
8. Device according to one of the claims 5 to 7, characterised in that a pressure by-pass duct (28) is provided, which connects the pressure by-pass chambers (16) of all working cylinders one with the other and is provided with controllable relay valves and by way of which the working fluid expanding out of the pressure by-pass chamber (16) is stored into the individual pressure by-pass chambers (16) of the following working cylinders and also - during the renewed attainment of the pneumatic pressurising pressure - the stored pressure fluid is moved into the pressure by-pass chamber (16) partially in energy-free pressure by-pass and partially by by-pass flow compressors (32).
9. Device according to one of the claims 5 to 8, characterised in that the sliding piston plate (2) is divided into two sliding piston plates (9A and 9B) and the sliding piston plate (9A) is connected with the cylinder housing (50) of the control cylinder (8), which is loadable by a pressure fluid from a pressure store, while the lower sliding piston plate (9B) is connected with the piston rod (52) of a piston (51), which is reversible bilaterally and displaceable upwardly and downwardly, of this control cylinder (8).
10. Device according to one of the preceding claims 5 to 9, characterised in that the sliding piston plate (11) is rigidly connected with upwardly and downwardly extending thrust supports (7), the parts of which extending in upward direction extend slidingly and sealingly through the sliding piston plates (9A and 9B) and the parts of which extending in downward direction extend slidingly and sealingly through the piston plate base plate (12).

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