DE202019005898U1 - Controllable drive device for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device that uses the principle of the double-acting hydraulic-pneumatic tandem cylinder - Google Patents

Abstract

Controllable drive device for a land vehicle, water vehicle and/or air vehicle based on a compressed gas-based energy conversion device which uses the principle of the double-acting hydraulic-pneumatic tandem cylinder, the drive device for the land vehicle, water vehicle and/or air vehicle having a motor driven by liquid flow and the liquid flow for driving the motor is provided by the said compressed-gas-based energy conversion device and the drive device also has a control device which is set up and designed in such a way that a driver and/or an automatic driver of the land vehicle, water vehicle and/or aircraft by means of the control device can control a driving force of the engine in that the control device can control a valve or a plurality of valves in the named compressed-gas-based energy conversion device in this way during ongoing operation of the engine, or k that an active supply of pressurized gas from the outside into a chamber (160, 165) to be pressurized with pressurized gas during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder can already be ended before a said chamber (160, 165) delimiting and through the pressurized gas moving piston (158, 162) reaches a stop that mechanically limits its movement path, with said piston (158, 162) then only moving under the influence of the pressure gas already filled into the chamber (160, 165) after the active compressed gas supply has been switched off from the outside Compressed gas in the direction of the movement of the piston (160, 165) moves mechanically limiting stop.

Description

In the broadest sense, the present invention relates to the technical field of compressed gas-based energy conversion devices and builds directly on the statements in the published German patent application DE 10 2013 105 186 A1 and on the statements in German patent application 10 2019 002 370.6 filed on April 2, 2019 and not yet published at the time of filing the present patent application, as well as on the statements in the patent application filed on September 24, 2019 and at the time of filing the present patent application not yet published German patent application 10 2019 006 695.2.

In a somewhat narrower sense, the present invention relates to the technical field of drive devices for land vehicles, water vehicles and/or aircraft based on a compressed gas-based energy conversion device.

Seen even more specifically, the present invention relates to a drive device for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device that uses the principle of the double-acting hydraulic-pneumatic tandem cylinder.

The basic principle of the double-acting hydraulic-pneumatic tandem cylinder is known to the person skilled in the art from the published German patent application DE 10 2013 105 186 A1 known. The statements in the German patent application 10 2019 002 370.6 filed on April 2, 2019 and not yet published at the time of filing the present patent application relate to some additions and improvements in this regard, but are at least fundamentally based on the principle of the double-acting hydraulic-pneumatic tandem cylinder. The statements in German patent application 10 2019 006 695.2, filed on September 24, 2019 and not yet published at the time of filing the present patent application, relate to some other related additions and improvements, but are at least fundamentally based on the principle of the double-acting hydraulic-pneumatic tandem cylinder.

The basic principle of the double-acting hydraulic-pneumatic tandem cylinder is that two cylinder-like vessels - hereinafter referred to simply as "cylinders" - are provided. In each of these two cylinder-like vessels or cylinders there is a piston that can be moved back and forth in the longitudinal direction of the respective cylinder, which divides each of the two cylinders just mentioned into two chambers, which are hydraulically and pneumatically sealed from each other by the respective piston . Both pistons are mechanically coupled to one another in such a way that a displacement of one piston immediately causes a corresponding displacement of the other piston and the volumes of the chambers in the two cylinders also change in accordance with the displacement of the two pistons. As in the published German patent application DE 10 2013 105 186 A1 described, the mechanical coupling of the two pistons can, for example, be accomplished simply by providing a single piston rod which extends from one cylinder into the other cylinder and carries one of the aforementioned pistons on each of its two end faces. Alternatively, a separate piston rod can also be provided for each individual piston, in which case both piston rods then have to be mechanically coupled to one another in a suitable manner.

As in the published German patent application DE 10 2013 105 186 A1 also described in detail, in an end position of the two pistons, the chamber with the respectively larger volume in this position is filled with gas in one cylinder and with liquid in the other cylinder. The chamber with the respectively smaller volume in this position is provided for liquid in said one cylinder and for gas in said other cylinder. Then, in the other cylinder mentioned, in which the maximum amount of liquid is initially located, gas is admitted from a pressurized gas tank at a pressure above atmospheric pressure into the initially smaller chamber there. With the appropriate valve position and integration of the cylinder in a hydraulic-pneumatic overall system, the liquid is pressed out of the other cylinder mentioned by a corresponding piston movement, as is the gas from the initially gas-filled chamber of the one cylinder mentioned. Said one cylinder sucks in liquid at the same time in its other chamber, which is provided for liquid filling. If the piston rod with its two pistons reaches the other end position after it has moved far enough, the valves are switched over accordingly and the process just described is repeated in the opposite direction. Ie, pressurized gas is now admitted into the chamber intended for gas of said one cylinder and in this way the piston rod with the two pistons is displaced in the direction opposite to its first direction of movement, which results in forcing the liquid out of the chamber intended for liquid in the said one cylinder, to simultaneously forcing gas out of the gas chamber of said other cylinder and sucking liquid into the liquid chamber of said other cylinder.

The compressed gas required to operate the double-acting hydraulic-pneumatic tandem cylinder is made available directly from a compressed gas reservoir specifically designed to store compressed gas, for example from a compressed gas cylinder, or as "residual gas" from another upstream compressed gas-based energy conversion device that has already completed some work step.

This describes at least the basic principle of the double-acting hydraulic-pneumatic tandem cylinder in its simplest form. In the manner set out above, the two pistons of the double-acting hydraulic-pneumatic tandem cylinder can be continuously moved back and forth synchronously by means of the action of compressed gas and suitable valve control, thereby keeping liquid in a liquid circuit in motion.

Fluid flown in this way can in turn be used to power a fluid powered machine, for example a hydraulically powered motor such as an oil motor. Such a motor drive realized using the basic principle of the double-acting hydraulic-pneumatic tandem cylinder has already been described in the published German patent application DE 10 2013 105 186 A1 as well as in the German patent application 10 2019 002 370.6 filed on April 2, 2019 and not yet published at the time of filing the present patent application as well as in the German patent application filed on September 24, 2019 and not yet published at the time of filing the present patent application 10 2019 006 695.2 always mentioned. However, the driving force of the hydraulically driven motors described in the three publications just mentioned cannot be controlled, or at least not sufficiently specifically, in the overall systems described there, which is more of a disadvantage for practical use.

The present invention essentially deals with applications and related detailed improvements of the motor drive just mentioned.

Before we go into this in more detail, the following should be expressly prefixed to the further explanations: If the term "gas" is used in the text of the present description of the invention and the patent claims, this term is currently primarily used for purely practical economic reasons to mean the gas " Air” is meant, however, from a purely physical and technical point of view, the present invention is in no way limited to the use of air as the gas used. Rather, from a purely physical and technical point of view, any gas, for example so-called “biogas”, can be used for the implementation of the invention described below. The use of the term "gas" in the text of the present description of the invention and the patent claims is by no means to be understood as being restricted solely to the gas air, although at least at present the use of the gas air is by far the predominant preference over the physical the use of other gases, such as any hydrocarbon gases, which is technically possible without further ado - and under certain conditions also makes very good economic sense.

Gas compressed above atmospheric pressure and in particular air compressed above atmospheric pressure, which is often simply referred to as "compressed air", has had great importance and a wide variety of practical applications in industrial technology for well over a hundred years. Compressed air has also been used as an energy store and as a means of propulsion for well over a hundred years, for example in compressed air-driven locomotives on mine railways. With the currently advancing so-called "energy transition" and the associated ever-widening spread of wind turbines and solar energy systems, the electrical energy production of which is naturally subject to very strong fluctuations over time, the need for such energy storage devices is increasing, with the help of which wind turbines and solar energy systems can temporarily be used in excess store energy that is provided and cannot be used immediately by electrical energy end consumers and can be called up later when required, for example if the wind turbines and solar energy systems are just not producing enough electrical energy to cover the electrical energy consumption via the electricity grid, or for other purposes that are completely independent of the electricity grid . There are various types of such energy storage devices in the prior art, including those in which the energy is stored in the form of compressed air, which is filled into compressed air cylinders or compressed air tanks by means of an air compressor. Simply put this compressed air, which can be stored and stored for any length of time, can then be released later at any time and used as a drive means for driving an electric energy generator or indirectly - as already described above - for driving a motor, in particular a hydraulically driven motor or oil motor . Various devices of this type, commonly referred to as “compressed air energy storage systems”, are already in use, for example DE 10 2013 105 186 A1 or in the U.S. 2012/0210705 A1 or in German patent application 10 2019 002 370.6 filed on April 2, 2019 and not yet published at the time of filing the present patent application or in German patent application 10 2019 filed on September 24, 2019 and not yet published at the time of filing the present patent application 006 695.2.

For compressing air or more generally for compressing gas, conventional electrically driven solid mechanical screw compressors and conventional electrically driven solid mechanical piston compressors have been known for many decades and are in use by the millions worldwide. Also found in the prior art are different and somewhat unconventional hydraulic air compression devices with double-acting cylinders in which a piston slides back and forth and one cylinder chamber is filled with air while the other cylinder chamber is filled with high pressure by means of an electrically powered pump oil is being pumped. As soon as the oil pressure in one cylinder chamber is higher than the pressure of the air in the chamber opposite the cylinder chamber just mentioned, this air is compressed and, for example, filled into compressed air storage bottles provided for it. Such a hydraulic air compression device just mentioned is for example in DE 10 2013 105 186 A1 described as part of the compressed air energy storage system presented in this publication. This latter, from the DE 10 2013 105 186 A1 Although the known hydraulic air compression device preferably runs only very slowly, the heat generated during air compression, which actually represents a loss of efficiency as such, can be collected very well and stored, for example, in the form of heated water. However, for the operation of in the DE 10 2013 105 186 A1 described hydraulic air compression device still a conventional electrically driven solid mechanical air compressor, such as an electrically driven solid mechanical screw compressor or an electrically driven solid mechanical piston compressor, useful as a pre-filler and for a really efficient operation in the DE 10 2013 105 186 A1 described hydraulic air compression device even absolutely necessary.

In general and completely independently of the above-described possible uses of conventional electrically driven solid-state mechanical screw compressors and conventional electrically driven solid-state mechanical piston compressors, these two types of conventional compressors just mentioned have the following operational restrictions: A conventional electrically driven solid-state mechanical screw compressor must and should run as long as possible for optimal operation be switched off and on again as little as possible. On the other hand, a conventional electrically driven solid-state mechanical piston compressor should not be expected to operate for significantly more than fifteen minutes without a cooling break.

Such operational restrictions are subject to the DE 10 2013 105 186 A1 Described hydraulic air compression device not, ie they can tolerate both readily continuous operation as well as an operating mode in which they are repeatedly switched on and off again within very short time intervals, but works in the DE 10 2013 105 186 A1 The hydraulic air compression device described preferably only very slowly, which on the one hand is definitely an advantage for heat storage, as already indicated above, but on the other hand, with regard to some time-critical applications, for example with regard to the frequently also time-critical application in an air pressure energy storage system for the power grid - Buffer storage of energy from solar energy systems and wind turbines, can be disadvantageous.

The conversion of the energy stored in the form of compressed air into electrical energy provided by an electric generator or just into mechanical drive energy of a motor is with the in the DE 10 2013 105 186 A1 Compressed air energy storage system described in principle readily possible, but has in the DE 10 2013 105 186 A1 compressed air energy storage system described a serious disadvantage. It is in this compressed air energy storage system - seen in relation to the workability of the compressed air used therein - too much solid material required for the piston. The piston is therefore too heavy, the ratio of the piston mass to the working capacity of the compressed air is too bad and so that the operation of the entire system is too sluggish. However, this disadvantage can be remedied by the improvements described in German patent application 10 2019 002 370.6 filed on April 2, 2019 and not yet published at the time the present patent application was filed. Further detailed improvements are described in German patent application 10 2019 006 695.2, which was filed on September 24, 2019 and was not yet published at the time the present patent application was filed. Since both German patent application 10 2019 002 370.6 and German patent application 10 2019 006 695.2 had not yet been published at the time the present patent application was filed, the technical details from the two German patent applications 10 2019 002 370.6 and 10 2019 006 695.2 very largely repeated, while the content of the already published German patent application DE 10 2013 105 186 A1 is incorporated herein simply by reference.

The invention is based on the object of providing a novel drive device for a land vehicle, water vehicle and/or aircraft that is also controllable with regard to the drive force provided by it.

According to the invention, this object is achieved by a controllable drive device according to claim 1. According to the invention, the stated object is also achieved by a controllable drive device according to claim 2.

Advantageous and preferred embodiments of the controllable drive device according to claim 1 according to the invention are the subject of claims 4 to 56. Advantageous and preferred embodiments of the controllable drive device according to claim 2 according to the invention are the subject of claims 3 to 56.

• 1 schematisch und nicht maßstabsgerecht Details eines ersten Ausführungsbeispiels einer hydraulischen Kolbeneinrichtung zur Verwendung in einem Ausführungsbeispiel einer erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 2 schematisch und nicht maßstabsgerecht weitere Details des ersten Ausführungsbeispiels der hydraulischen Kolbeneinrichtung von 1,
• 3 schematisch und nicht maßstabsgerecht weitere Details des ersten Ausführungsbeispiels der hydraulischen Kolbeneinrichtung aus den 1 und 2,
• 4 schematisch und nicht maßstabsgerecht weitere Details des ersten Ausführungsbeispiels der hydraulischen Kolbeneinrichtung aus den 1 bis 3,
• 5 schematisch und nicht maßstabsgerecht ein erstes Ausführungsbeispiel einer Druckgasenergiewandlungseinrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung, wobei das erste Ausführungsbeispiel der Druckgasenergiewandlungseinrichtung das erste Ausführungsbeispiel der hydraulischen Kolbeneinrichtung aus den 1 bis 4 umfasst,
• 6 schematisch und nicht maßstabsgerecht Details eines zweiten Ausführungsbeispiels einer hydraulischen Kolbeneinrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 7 schematisch und nicht maßstabsgerecht Details eines zweiten Ausführungsbeispiels einer Druckgasenergiewandlungseinrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung, wobei das zweite Ausführungsbeispiel der Druckgasenergiewandlungseinrichtung das zweite Ausführungsbeispiel der hydraulischen Kolbeneinrichtung aus 6 umfasst,
• 8 schematisch und nicht maßstabsgerecht einen Längsschnitt durch ein Ausführungsbeispiel einer Druckgasenergiewandlungs-Wärmetauscher-Einrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 9 schematisch und nicht maßstabsgerecht einen Längsschnitt durch einen zentralen Abschnitt der Druckgasenergiewandlungs-Wärmetauscher-Einrichtung von 8,
• 10 schematisch und nicht maßstabsgerecht eine Draufsicht auf den in 9 im Längsschnitt zu sehenden zentralen Abschnitt der Druckgasenergiewandlungs-Wärmetauscher-Einrichtung von 8,
• 11 schematisch und nicht maßstabsgerecht den Längsschnitt durch das Ausführungsbeispiel der Druckgasenergiewandlungs-Wärmetauscher-Einrichtung von 8, wobei zusätzlich noch Zuleitungen für Gas dargestellt sind,
• 12 schematisch und nicht maßstabsgerecht einen Längsschnitt durch ein erstes Ausführungsbeispiel einer Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 13 schematisch und nicht maßstabsgerecht einen Längsschnitt durch ein zweites Ausführungsbeispiel einer Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 14 schematisch und nicht maßstabsgerecht ein Ausführungsbeispiel einer Druckgasenergiewandlungsvorrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung, wobei dieses Ausführungsbeispiel der Druckgasenergiewandlungsvorrichtung eine Kombination des Ausführungsbeispiels der Druckgasenergiewandlungs-Wärmetauscher-Einrichtung von 11 mit dem Ausführungsbeispiel der Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung von 12 als Vorstufe ist,
• 15 schematisch und nicht maßstabsgerecht ein Ausführungsbeispiel einer Druckgasenergiewandlungsvorrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung, wobei dieses Ausführungsbeispiel der Druckgasenergiewandlungsvorrichtung zwei Zweiergruppen gemäß dem Ausführungsbeispiel von 14 aufweist,
• 16 schematisch und nicht maßstabsgerecht ein weiteres Ausführungsbeispiel einer Druckgasenergiewandlungs-Wärmetauscher-Einrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 17 schematisch und nicht maßstabsgerecht ein drittes Ausführungsbeispiel einer Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung zur Verwendung in einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung,
• 18 schematisch und nicht maßstabsgerecht einige Details eines Ausführungsbeispiels der erfindungsgemäßen steuerbaren Antriebsvorrichtung in Seitenansicht,
• 19 schematisch und nicht maßstabsgerecht die Details des Ausführungsbeispiels der erfindungsgemäßen steuerbaren Antriebsvorrichtung von 18 in Draufsicht,
• 20 schematisch und nicht maßstabsgerecht einen Bug eines Wasserfahrzeugs mit einem Ausführungsbeispiel der erfindungsgemäßen steuerbaren Antriebsvorrichtung in Ansicht von vorne und
• 21 schematisch und nicht maßstabsgerecht den Bug des Wasserfahrzeugs von 20 in Ansicht steuerbords.

Advantageous and preferred exemplary embodiments of the invention are explained below with reference to figures. It shows:

• 1 schematic and not to scale details of a first embodiment of a hydraulic piston device for use in an embodiment of a controllable drive device according to the invention,
• 2 schematic and not to scale further details of the first embodiment of the hydraulic piston device of FIG 1 ,
• 3 schematic and not to scale further details of the first embodiment of the hydraulic piston device from the 1 and 2 ,
• 4 schematic and not to scale further details of the first embodiment of the hydraulic piston device from the 1 until 3 ,
• 5 schematically and not to scale, a first exemplary embodiment of a compressed gas energy conversion device for use in an exemplary embodiment of the controllable drive device according to the invention, the first exemplary embodiment of the compressed gas energy conversion device being the first exemplary embodiment of the hydraulic piston device from the 1 until 4 includes,
• 6 schematically and not to scale details of a second embodiment of a hydraulic piston device for use in an embodiment of the controllable drive device according to the invention,
• 7 schematic and not to scale details of a second embodiment of a compressed gas energy conversion device for use in an embodiment of the controllable drive device according to the invention, the second embodiment of the compressed gas energy conversion device the second embodiment of the hydraulic piston device 6 includes,
• 8th schematically and not to scale, a longitudinal section through an embodiment of a compressed gas energy conversion heat exchanger device for use in an embodiment of the controllable drive device according to the invention,
• 9 schematically and not to scale, a longitudinal section through a central portion of the compressed gas energy conversion heat exchanger device of FIG 8th ,
• 10 a schematic plan view, not to scale, of the in 9 to be seen in longitudinal section central section of the compressed gas energy conversion heat exchanger device of 8th ,
• 11 schematically and not to scale, the longitudinal section through the exemplary embodiment of the compressed gas energy conversion heat exchanger device from FIG 8th , whereby supply lines for gas are also shown,
• 12 schematically and not to scale, a longitudinal section through a first exemplary embodiment of a compressed gas energy conversion heat exchanger device for use in a preliminary stage device Embodiment of the controllable drive device according to the invention,
• 13 schematically and not to scale, a longitudinal section through a second exemplary embodiment of a compressed gas energy conversion heat exchanger device for use in an exemplary embodiment of the controllable drive device according to the invention,
• 14 schematically and not to scale, an embodiment of a compressed gas energy conversion device for use in an embodiment of the controllable drive device according to the invention, this embodiment of the compressed gas energy conversion device being a combination of the embodiment of the compressed gas energy conversion heat exchanger device from 11 with the embodiment of the compressed gas energy conversion heat exchanger device precursor device of FIG 12 as a precursor
• 15 schematically and not to scale an embodiment of a compressed gas energy conversion device for use in an embodiment of the controllable drive device according to the invention, this embodiment of the compressed gas energy conversion device two groups according to the embodiment of 14 having,
• 16 schematically and not to scale, a further embodiment of a compressed gas energy conversion heat exchanger device for use in an embodiment of the controllable drive device according to the invention,
• 17 schematically and not to scale, a third exemplary embodiment of a compressed gas energy conversion heat exchanger device for use in an exemplary embodiment of the controllable drive device according to the invention,
• 18 schematically and not to scale some details of an embodiment of the controllable drive device according to the invention in a side view,
• 19 schematically and not to scale, the details of the embodiment of the controllable drive device according to the invention from 18 in top view,
• 20 schematically and not to scale, a bow of a watercraft with an embodiment of the controllable propulsion device according to the invention in a view from the front and
• 21 schematically and not to scale, the bow of the watercraft 20 in starboard view.

For the description of advantageous and preferred exemplary embodiments of the invention, controllable drive devices for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device that uses the principle of the double-acting hydraulic-pneumatic tandem cylinder, we first turn to the 18 and 19 which show some details of a very simple exemplary embodiment of a controllable drive device according to the invention, by no means all of them, schematically and not to scale. 18 Fig. 13 is a side view of some of the details of said embodiment of the controllable drive device according to the invention, and 19 is a plan view of the in 18 referenced details of the mentioned embodiment of the controllable drive device according to the invention for a land, water and / or aircraft based on a compressed gas-based energy conversion device, which uses the principle of the double-acting hydraulic-pneumatic tandem cylinder.

The 18 and 19 show a double-acting hydraulic-pneumatic tandem cylinder, which in principle is already known as such from the prior art. The double-acting hydraulic-pneumatic tandem cylinder has a hollow cylinder formally referred to here as the eleventh hollow cylinder 152 and a further hollow cylinder formally referred to here as the twelfth hollow cylinder 153 . The eleventh hollow cylinder 152 has at one end an end wall formally referred to here as the fifteenth end wall 154 and at its other end an end wall formally referred to here as the sixteenth end wall 155 . The twelfth hollow cylinder 153 has at one end an end wall formally referred to here as the seventeenth end wall 156 and at its other end an end wall 157 formally referred to here as the eighteenth end wall.

The interior of the eleventh hollow cylinder 152 is provided with a piston, formally referred to here as the ninth piston 158, which rests on one end of a piston rod, formally referred to here as the left partial piston rod 159, and can be moved back and forth within the eleventh hollow cylinder 152 in the longitudinal direction of the eleventh hollow cylinder 152 and divides the eleventh hollow cylinder 152 into two chambers of variable volume 160, 161, which are always sealed off from one another by the ninth piston 158. One of the two chambers 160, 161 just mentioned is formally referred to here as the nineteenth chamber 160 and the other as twenty tenth chamber 161, the nineteenth chamber 160 adjoining the fifteenth end wall 154 and the twentieth chamber 161 adjoining the sixteenth end wall 155.

Correspondingly, the interior of the twelfth hollow cylinder 153 is provided with a piston, formally referred to here as the tenth piston 162, which sits on one end of a piston rod, formally referred to here as the right partial piston rod 163, inside the twelfth hollow cylinder 153 in the longitudinal direction of the twelfth hollow cylinder 153 and back is movable forth and divides the twelfth hollow cylinder 153 into two chambers of variable volume 164, 165, which are always sealed off from one another by the tenth piston 162. One of the two chambers 164, 165 just mentioned is formally referred to here as the twenty-first chamber 164 and the other as the twenty-second chamber 165, with the twenty-first chamber 164 adjoining the seventeenth end wall 156 and the twenty-second chamber 165 adjoining the eighteenth end wall 157.

The current volume of the nineteenth chamber 160 or the twentieth chamber 161 depends on the current position of the ninth piston 158 . The respective current volume of the twenty-first chamber 164 and the twenty-second chamber 165 depends on the respective current position of the tenth piston 162 .

The left half piston rod 159 extends through the twentieth chamber 161 and through an opening in the sixteenth end wall 155 . The right half piston rod 163 extends through the twenty-first chamber 164 and through an opening in the seventeenth end wall 156 . The left partial piston rod 159 and the right partial piston rod 163 are fixed to one another by means of a screw 166 at their ends located outside of the eleventh or twelfth hollow cylinder 152, 153, respectively.

The nineteenth chamber 160 and the twenty-second chamber 165 are intended for holding gas, while the twentieth chamber 161 and the twenty-first chamber 164 are intended for holding liquid. Accordingly, the nineteenth chamber 160 is provided with a seventeenth gas connection device 167, via which gas can be introduced into the nineteenth chamber 160 and also led out of the nineteenth chamber 160 again. For this purpose, the seventeenth gas connection device 167 is provided with a correspondingly suitable valve, not shown in the figures. The twenty-second chamber 165 is provided with an eighteenth gas connection device 168, via which gas can be introduced into the twenty-second chamber 165 and also led out of the twenty-second chamber 165 again. For this purpose, the eighteenth gas connection device 168 is provided with a correspondingly suitable valve, not shown in the figures. The twentieth chamber 161 is provided with a ninth liquid connection device 169, via which liquid can be introduced into the twentieth chamber 161 and also led out of the twentieth chamber 161 again. For this purpose, the ninth liquid connection device 169 is provided with a correspondingly suitable valve, which is not shown in the figures. The twenty-first chamber 164 is provided with a tenth fluid connection device 170, via which fluid can be introduced into the twenty-first chamber 164 and can also be conducted out of the twenty-first chamber 164 again. For this purpose, the tenth liquid connection device 170 is provided with a correspondingly suitable valve, which is not shown in the figures.

The ones with reference to the 18 and 19 The details described form the basis of the operating principle of the double-acting hydraulic-pneumatic tandem cylinder, which is already known from the prior art. In this context, reference is made in particular to the statements in DE 10 2013 105 186 A1 which are incorporated herein by reference.

The ninth piston 158 and the tenth piston 162 are mechanically coupled to one another by the left partial piston rod 159, the screw 166 and the right partial piston rod 163 in such a way that a displacement of one of the two pistons 158, 162 just mentioned immediately causes a corresponding displacement of the other of the two pistons 158, 162 just mentioned and the volumes of the nineteenth chamber 160, the twentieth chamber 161, the twenty-first chamber 164 and the twenty-second chamber 165 also change in accordance with the displacement of the two just-mentioned pistons 158, 162.

When the ninth piston 158 and the tenth piston 162 in the in the 18 and 19 views shown have taken their furthest possible end position towards the left, the twentieth chamber 161 and the twenty-second chamber 165 each have their largest possible volume and the nineteenth chamber 160 and the twenty-first chamber 164 accordingly their respective smallest possible volume. Suitably provided mechanical stops, which are not shown in the figures, ensure that the volumes of the nineteenth chamber 160 and the twenty-first chamber 164, however are also not equal to zero and letting gas into the nineteenth chamber 160 via the seventeenth gas connection device 167 and flowing liquid into the twenty-first chamber 164 via the tenth liquid connection device 170 remain fundamentally possible in any case. The twentieth chamber 161 is filled with liquid and the twenty-second chamber 165 is filled with gas. Compressed gas, for example compressed air at a pressure far above atmospheric pressure, is now admitted into the nineteenth chamber 160 via the seventeenth gas connection device 167 . This results in movement of both the ninth piston 158 and the tenth piston 162 as viewed in FIG 18 and 19 To the right. With the appropriate valve position and integration of the eleventh hollow cylinder 152 and the twelfth hollow cylinder 153 into an overall hydraulic-pneumatic system, the fluid is pressed out of the twentieth chamber 161 by this movement of the ninth piston 158 from the twentieth chamber 161 via the ninth fluid connection device 169, and fluid is tenth liquid connection device 170 because of the movement of the tenth piston 162 in the view of 18 and 19 sucked to the right into the twenty-first chamber 164. The gas from the initially filled with gas twenty-second chamber 165 is via the eighteenth gas connection device 168 because of the movement of the tenth piston in the view of FIG 18 and 19 pushed out of the twenty-second chamber 165 to the right.

It is ensured by stops, which are not shown in the figures but are nevertheless provided and actually present, that the ninth piston 158 and the tenth piston 162 in the view of FIG 18 and 19 can only move so far to the right that at the end of this aforementioned piston movement to the right, the volumes of the twentieth chamber 161 and the twenty-second chamber 165 are minimal, but in any case not equal to zero and gas is admitted into the twenty-second chamber 165 via the eighteenth Gas connection device 168 and an inflow of liquid into the twentieth chamber 161 via the ninth liquid connection device 169 remain possible in principle.

If the ninth piston 158 and the tenth piston 162 move far enough into their position in the view of FIG 18 and 19 position as far to the right as possible, the valves are switched over accordingly and the process described in the previous paragraph is simply repeated in the opposite direction. That means that compressed gas is now admitted into the twenty-second chamber 165 via the eighteenth gas connection device 168, with the result that the tenth piston 162 and the ninth piston 158 in the view of FIG 18 and 19 move to the left. This leads to the liquid being pressed out of the twenty-first chamber 164 via the tenth liquid connection device 170, to the suction of liquid via the ninth liquid connection device 169 into the twentieth chamber 161 and to the gas being pushed out of the nineteenth chamber 160 via the seventeenth gas connection device 167.

By appropriately controlled switching of the valves, this process can now again - as already described above - be repeated in the other direction, and the ninth piston 158 and the tenth piston 162 can be continuously moved back and forth and thus the liquid in one in the 18 and 19 keep the fluid circuit in motion, not shown in its entirety. The fluid which is set in motion, in turn, can be used to power a fluid powered machine, for example a hydraulically powered motor such as an oil motor. This engine is in the 18 and 19 not shown, but can be easily supplemented mentally.

That to operate the just with reference to the 18 and 19 The compressed gas required for the double-acting hydraulic-pneumatic tandem cylinder described, i.e. the eleventh hollow cylinder 152 and the twelfth hollow cylinder 153 with the other components just described, is taken directly from a compressed gas reservoir specifically provided for compressed gas storage, for example from a compressed gas bottle, or as “residual gas” from an upstream one other compressed gas-based energy conversion device that has already completed some work step. Although this is in the 18 and 19 not shown, but will be described in more detail below with reference to other figures.

That with reference to the 18 and 19 The basic principle of the double-acting hydraulic-pneumatic tandem cylinder explained in its simplest form of action is already known as such from the prior art (cf DE 10 2013 105 186 A1 ) In the manner described above, the two pistons 158, 162 of the double-acting hydraulic-pneumatic tandem cylinder can be continuously moved back and forth synchronously by means of the action of compressed gas and suitable valve control, thereby creating a liquid circuit and, by means of this, a machine driven by flowing liquid, for example a hydraulically driven machine Drive an engine such as an oil engine.

It should be expressly mentioned at this point that in embodiments of double-acting hydraulic-pneumatic tandem cylinders, in which the gas connection devices and the liquid connection devices - unlike in the very special and here only as a possible example described and shown embodiment of the 18 and 19 provided - in each case sit perpendicularly on the respective end walls 154, 155, 156, 157 of the hollow cylinders 152, 153, these end walls 154, 155, 156, 157 of the hollow cylinders 152, 153 can each themselves serve as movement-limiting stops for the respective pistons 158, 162 and then of course - unlike the very special embodiment of the 18 and 19 - There is the possibility of reducing the respectively corresponding chambers 160, 161, 164, 165 down to a volume of zero and correspondingly of completely removing gas or liquid from the respective chamber 160, 161, 164, 165.

In one of its embodiment variants, the present invention is now specifically a controllable drive device for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device that uses the principle of the double-acting hydraulic-pneumatic tandem cylinder. The drive device for the land vehicle, water vehicle and/or aircraft has a motor driven by a liquid flow. The fluid flow for driving the engine is provided by the aforesaid compressed gas based energy conversion device. Furthermore, the drive device has a control device which is set up and designed in such a way that a driver and/or an automatic driver of the land vehicle, watercraft and/or aircraft can use the control device to control a driving force of the motor by using the control device during an ongoing When the engine is operating, one or more valves in the aforementioned compressed-gas-based energy conversion device can be controlled in such a way that an active supply of compressed gas from the outside into a chamber 160, 165 to which compressed gas is to be applied during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder is already ended before a piston 158, 162, which delimits said chamber 160, 165 and is moved by the compressed gas, reaches a stop that mechanically limits its movement path, with said piston 158, 162 then only moving under one Influence of the compressed gas already filled into the chamber 160, 165 moves in the direction of the stop mechanically limiting the movement distance of the piston 158, 162.

The fifteenth end wall 154 or the sixteenth end wall 155 or the seventeenth end wall 156 or the eighteenth end wall 157 can serve as the stop mechanically limiting the movement distance of the piston 158, 162 in a correspondingly suitable assignment. However, any other suitable stop, not shown in the figures, which is independent of any of the end walls 154, 155, 156, 157 just mentioned, can also serve as the stop mechanically limiting the movement distance of the piston 158, 162.

With reference to the presentation of 18 and 19 In concrete terms, this means that in the working stroke of the movement of the ninth piston 158 and the tenth piston 162 to the right, the active compressed gas supply can already be switched off via the seventeenth gas connection device 167 by means of the control device when the ninth piston 158 and the tenth piston 162 have not yet reached their furthest possible extent have reached the position shifted to the right. Although the ninth piston 158 and the tenth piston 162 still move to the right up to their position, which is as far as possible to the right, after the active compressed gas supply has been switched off due to the influence of the gas under increased pressure that has already been filled into the nineteenth chamber 160, the pressure exerted on the liquid in the twentieth chamber 161 is not so strong, which in turn leads to a reduced driving force of the motor driven by the liquid. The same applies to the work cycle of the movement of the ninth piston 158 and the tenth piston 162 in the representation of FIG 18 and 19 to the left. The active supply of pressurized gas via the eighteenth gas connection device 168 can already be switched off by means of the control device when the tenth piston 162 and the ninth piston 158 have not yet reached their position which has been pushed to the left as far as possible. Although the tenth piston 162 and the ninth piston 158 still move to the left after the active supply of compressed gas has been switched off due to the influence of the gas under increased pressure that has already been filled into the twenty-second chamber 165, they are still in their position, which is as far as possible to the left the pressure exerted on the liquid in the twenty-first chamber 164 is not as great, which in turn leads to a reduced motive power of the motor driven by the liquid.

The driver and/or an automatic driver of the land vehicle, water vehicle and/or aircraft can control the propulsion force of the engine driving the land vehicle, water vehicle and/or aircraft by using the control device to activate the respective active compressed gas supply to the nineteenth Came mer 160 or the twenty-second chamber 165 in a work cycle of the double-acting hydraulic-pneumatic tandem cylinder turns off sooner or later. The sooner the active supply of compressed gas is switched off during the respective work cycle, the lower the current driving force of the engine is ultimately. The later the active supply of compressed gas is switched off during the respective work cycle, the greater the current driving force of the engine. As a result, the driving or flight speed of such a land, water and / or air vehicle can be controlled, which is provided with a compressed gas accumulator or with several compressed gas accumulators and a drive device based on a compressed gas-based energy conversion device, which uses the principle of double-acting hydraulic -Pneumatic tandem cylinder uses, and having a motor driven by the fluid flow provided by said compressed gas-based energy conversion device.

In another embodiment variant, the present invention is also a controllable drive device for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device that uses the principle of the double-acting hydraulic-pneumatic tandem cylinder. In this embodiment variant, too, the drive device for the land vehicle, water vehicle and/or aircraft has a motor driven by a liquid flow, and the liquid flow for driving the motor is provided by the named compressed-gas-based energy conversion device. In the embodiment variant now to be described, the drive device also has a control device which is set up and designed in such a way that a driver and/or an automatic driver of the land vehicle, watercraft and/or aircraft can control a driving force of the motor by means of the control device by the control device during ongoing operation of the engine, one or more valves in the named compressed gas-based energy conversion device can be controlled in such a way that the strength of an active supply of compressed gas from the outside in a working cycle of the double-acting hydraulic-pneumatic tandem cylinder with compressed gas acting chamber in a certain pressure range can be adjusted continuously and / or in stages changeable.

Consequently, this means with reference to the specific embodiment of 18 and 19 that the driver and/or an automatic driver of the land vehicle, watercraft and/or aircraft can use the control device during the respective work cycle of the double-acting hydraulic-pneumatic tandem cylinder to control the pressure at which the compressed gas is fed into the nineteenth chamber 160 or into the twenty-second chamber 165 is admitted. If the pressure is set high, the result is a strong flow of liquid to drive the motor and ultimately a large driving force of the motor. Decreasing the pressure results in less fluid flow to drive the motor, and ultimately less motive power from the motor. If the pressure is increased again, the strength of the liquid flow increases accordingly, which ultimately leads to an increased driving force of the engine. As a result, the driving or flight speed of such a land, water and/or aircraft can be controlled, which is provided with a compressed gas storage device or with several compressed gas storage devices and a drive device based on a compressed gas-based energy conversion device, which uses the principle of double-acting hydraulic-pneumatic tandem cylinder, and having a motor driven by the fluid flow provided by said compressed gas-based energy conversion device.

The embodiment variant of the controllable drive device according to the invention presented last can be expanded in one embodiment to include the idea of the embodiment variant of the controllable drive device according to the invention presented first, in that the control device is also set up and designed in such a way that it activates one or more valves during ongoing operation of the engine can be controlled in the named compressed gas-based energy conversion device in such a way that an active supply of compressed gas from the outside into a chamber 160, 165 to be pressurized with compressed gas during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder can already be ended before a and piston 158, 162 moved by the compressed gas reaches a stop that mechanically limits its movement path, said piston 158, 162 moving from au ßen then moves only under the influence of the already filled in the chamber 160, 165 compressed gas in the direction of the movement of the piston 158, 162 mechanically delimiting stop.

In general, in embodiments of both variants of the drive devices according to the invention, for example, further provided that the control device is set up and designed so that the control of the shutdown of the compressed gas supply or the control of the strength of the compressed gas supply or both Control of the strength of the compressed gas supply as well as the control of switching off the compressed gas supply takes place by means of an electronic pressure control.

If exemplary embodiments of the drive device according to the invention provide a control for switching off the active supply of compressed gas, it is preferable to provide the control device with a travel detection device 171, 172, which is set up and designed in such a way that this travel detection device 171, 172 can be used continuously during ongoing operation of the engine or that piston travel can be set in stages, after which the active supply of compressed gas is switched off. The displacement detection device 171, 172 is in 19 schematically indicated with a fixed component 171 and with a movable component 172. The displacement detection device 171, 172 can, for example, be a displacement detection device 171, 172 based on magnetic and/or mechanical and/or optical and/or electronic and/or optoelectronic functionality.

With regard to the control device, such exemplary embodiments of the drive device according to the invention are very particularly preferred in which the control device has an operating device by means of which the driver of the land vehicle, watercraft and/or aircraft can operate the said control device. Examples of such an operating device are a pedal or a rotary controller or a joystick or a touchscreen or a voice-controlled operating device or a gesture-controlled operating device.

Air is often simply used as the compressed gas or gas for the controllable drive device according to the invention, but it should be emphasized at this point that instead of or together with air, any other gas, for example biogas and/or methane and/or any hydrocarbon gas and/or or a mixture of hydrocarbon gases and/or a mixture of air and one or more hydrocarbon gases can be used in the controllable propulsion device according to the invention.

With regard to the liquid used in the controllable drive device according to the invention for driving the motor, oil is often used for purely economic reasons. Accordingly, an oil motor has already been expressly mentioned above. However, the operation of the controllable drive device according to the invention is in principle also readily possible with any other liquid for driving the motor, for example with water.

If the vehicle to be driven by the controllable drive device according to the invention is a watercraft, a ship's propeller or a paddle wheel, for example, or also an air propeller driving the watercraft can be driven by the engine.

Some specific exemplary embodiments of the controllable drive device according to the invention, in which the vehicle to be driven is a watercraft 173, are particularly worth mentioning. In this context, compare the 20 and 21 , which are to be considered together and to which reference is made below. 20 shows schematically and not to scale a bow of a watercraft 173 with an embodiment of the controllable propulsion device according to the invention in a view from the front. Upon executing the “Full Speed Ahead!” command, Vessel 173 departs 20 so on the viewer of 20 to. 21 17 shows schematically and not to scale the bow of the watercraft 173 of FIG 20 in starboard view. Upon executing the “Full Speed Ahead!” command, Vessel 173 departs 21 so in the view of 21 to the right out of the picture.

In one exemplary embodiment of the controllable propulsion device according to the invention, the watercraft 173 to be driven is set up in such a way that gas which it has already performed in the compressed-gas-based energy conversion device is used to under the hull or under part of the hull of the watercraft 173 a To produce carpet of gas bubbles and / or gas bubbles 176. This reduces friction between the hull of the watercraft 173 and the water in which the watercraft 173 is sailing. Thus, with the above-mentioned carpet of gas bubbles and/or gas bubbles 176, a higher driving speed of the watercraft 173 can be achieved with the same driving force of the engine than without this carpet of gas bubbles and/or gas bubbles 176.

Also particularly worth mentioning are those exemplary embodiments of the controllable drive device according to the invention, in which the vehicle to be driven is a watercraft 173 which has a tube 174 in which an impeller 175 is arranged, with the purpose of driving the watercraft 173 by means of the impeller 175 on a end of the tube 174 water is drawn in from the body of water in which the watercraft 173 floats and is ejected again at the opposite end of the tube 174, and there is also a device 177 which is arranged to discharge gas which is produced by it in the compressed-gas-based energy conversion device has already performed the work to be performed, based on the direction of water flow in said pipe 174 behind the impeller 175, preferably immediately behind the impeller 175, in said pipe 174 to initiate. The impeller drive is used in addition to the drive of the watercraft 173 mediated by the motor of the controllable drive device. The gas introduced into the aforesaid pipe 174 expands explosively, thus helping to expel the water drawn in by the impeller 175 at high speed and thus improving the propulsion of the watercraft 173 even further.

Very particularly preferred are those exemplary embodiments - not shown in the figures - which are set up in such a way that the impeller is set up in a controllable manner in such a way that it can be used to move water in the named pipe both in one direction and in the opposite direction flow, and that the impeller can be switched between the two water flow directions mentioned and that, moreover, the said device, which is set up to gas, which has already been performed by it in the compressed-gas-based energy conversion device, based on the water flow direction in the said pipe downstream of the impeller, preferably immediately downstream of the impeller, into said pipe, is set up in a suitable manner in order to adapt the specific point at which the gas is introduced into said pipe to the respective current water flow direction. All of this serves to enable the gas-assisted impeller drive to be used both when the watercraft is being driven forwards and when the watercraft is being driven backwards.

Finally, in connection with the impeller drive, there are also exemplary embodiments of the controllable drive device according to the invention in which the watercraft 173 is set up in such a way that gas introduced into the named pipe 174 after it has exited the named pipe 174 under a part of the hull of the watercraft 173 Carpet of gas bubbles and / or gas bubbles 176 generated. Just such an embodiment of the invention is in the 20 and 21 to see. As already mentioned above in a somewhat different context, the carpet of gas bubbles and/or gas bubbles 176 reduces the friction between the hull of the watercraft 173 and the water in which the watercraft 173 is sailing. Thus, with the above-mentioned carpet of gas bubbles and/or gas bubbles 176, a higher driving speed of the watercraft 173 can be achieved with the same driving force of the engine than without this carpet of gas bubbles and/or gas bubbles 176.

At the in the 20 and 21 Watercraft 173 shown is in addition to the impeller 175 provided as a drive means, a ship's propeller, which is located at the stern of the watercraft 173 and in the 20 and 21 accordingly cannot be seen. This ship's propeller just mentioned is driven by a motor, which in turn is driven by a liquid flow provided by the compressed-gas-based energy conversion device already mentioned above.

In other exemplary embodiments, it can even be provided that there is no ship's propeller and also no paddle wheel and also no air propeller or the like in addition to the impeller, but that the impeller is the sole drive of the watercraft and is accordingly driven by a motor, which in turn is driven by a provided by the above-mentioned compressed gas-based energy conversion device liquid flow is driven.

If, in addition to the impeller, a ship's propeller, a paddle wheel, an air propeller or similar is provided as a drive device for the watercraft, in other exemplary embodiments of the invention, both the motor for driving the ship's propeller or the paddle wheel or the air propeller and the motor for the Driving the impeller are each driven by a liquid flow provided by the above-mentioned gas-based energy conversion device.

At the in the 20 and 21 watercraft 173 shown, the impeller 175 is arranged at the bow of the watercraft 173 . It is expressly pointed out that this is only one of many possible exemplary embodiments of the arrangement of the impeller. In other embodiments, the impeller and the tube in which the impeller is located are located at other locations under the hull or submerged sidewalls of a craft, such as near the center or near the stern of such a craft.

There are also exemplary embodiments of the controllable drive device according to the invention for a land vehicle, watercraft and/or aircraft based on a compressed gas-based energy conversion device, in which the compressed gas-based energy conversion device has a hydraulic piston device 1 which can be used at least for the purpose of gas compression. The 1 until 4 , which are to be viewed together, each show a purely schematic view and individual details, not true to scale, of a first exemplary embodiment of such a hydraulic piston device 1, which can be used at least for the purpose of gas compression. Identical reference numbers in the 1 until 4 denote about the overall view of 1 until 4 identical components are considered in each case.

That in the 1 until 4 The illustrated first exemplary embodiment of the hydraulic piston device 1 uses air exclusively as the gas and therefore functions as a first air compression device 1, at least insofar as it is operated for the purpose of air compression.

The first exemplary embodiment of the hydraulic piston device 1 has the following: a first hollow cylinder 2, which has a first end wall 3 at one end and a second end wall 4 at its other end, a second hollow cylinder 5, which has a third end wall 6 at one end and has a fourth end wall 7 at its other end, a third hollow cylinder 8, which has a fifth end wall 9 at one end and a sixth end wall 10 at its other end, a fourth hollow cylinder 11, which has a seventh end wall 12 at one end and at its other end an eighth end wall 13, and a piston rod 14 on which a first piston 15, a second piston 16, a third piston 17 and a fourth piston 18 are fixed.

The first hollow cylinder 2, the second hollow cylinder 5, the third hollow cylinder 8 and the fourth hollow cylinder 11 are arranged in a row in such a way that the second end wall 4 and the third end wall 6 face one another, and the fourth end wall 7 and the fifth end wall 9 face one another face each other, the sixth end wall 10 and the seventh end wall 12 face each other and accordingly the first end wall 3 is one end of said row of hollow cylinders 2, 5, 8, 11 and the eighth end wall 13 is another end of said row of hollow cylinders 2, 5, 8, 11 form.

The piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it is arranged in such a way that one end is located in the first hollow cylinder 2 and the other end is located in the fourth hollow cylinder 11 and the piston rod 14 accordingly passes through an opening in the second end wall 4, through an opening in the third end wall 6, through the second hollow cylinder 5, through an opening in the fourth end wall 7, through an opening in the fifth end wall 9, through the third hollow cylinder 8, through an opening in the sixth end wall 10 and extends through an opening in the seventh end wall 12, the first piston 15 is located in the first hollow cylinder 2 and divides it into a first chamber 19 and a second chamber 20, the first chamber 19 and the second chamber 20 passing through the first piston 15 are sealed against each other, the second piston 16 is located in the second hollow cylinder 5 and divides it into a third chamber 21 and a fourth chamber 22 , the third chamber 21 and the fourth chamber 22 being sealed off from one another by the second piston 16, the third piston 17 being located in the third hollow cylinder 8 and dividing it into a fifth chamber 23 and a sixth chamber 24, the fifth chamber 23 and the sixth chamber 24 is sealed from one another by the third piston 17, the fourth piston 18 is located in the fourth hollow cylinder 11 and divides it into a seventh chamber 25 and an eighth chamber 26, with the seventh chamber 25 and the eighth chamber 26 being separated by the fourth Piston 18 are sealed against each other.

The piston rod 14 can be moved back and forth in the longitudinal direction with the four pistons 15, 16, 17, 18 fixed to it, so that the size of the respective volume of each of the eight chambers 19, 20, 21, 22, 23, 24, 25 , 26 is variable according to the respective piston stroke.

Both the fourth chamber 22 and the fifth chamber 23 are each intended to be completely filled with liquid. Both the first chamber 19 and the second chamber 20 and the third chamber 21 and the sixth chamber 24 and the seventh chamber 25 and the eighth chamber 26 are completely filled with gas.

The fourth chamber 22 is provided with a first liquid connection device 27 and with a second liquid connection device 28 . The fifth chamber 23 is provided with a third liquid connection device 29 and with a fourth liquid connection device 30 . The first chamber 19 is provided with a first gas connection device 31 and with a second gas connection device 32 . The seventh chamber 25 is provided with a third gas connection device 33 and with a fourth gas connection device 34 . The sixth chamber 24 is provided with a fifth gas connection device 35 .

A first gas line 36 leads from the second gas connection device 32 to the fifth gas connection device 35. A second gas line 37 leads from the fourth gas connection device 34 to the fifth gas connection device 35.

The second chamber 20 is provided with a sixth gas connection device 38 and with a seventh gas connection device 39 . The eighth chamber 26 is connected to an eighth gas port direction 40 and provided with a ninth gas connection device 41 . The third chamber 21 is provided with a tenth gas connection device 42 .

A third gas line 43 leads from the seventh gas connection device 39 to the tenth gas connection device 42. A fourth gas line 44 leads from the ninth gas connection device 41 to the tenth gas connection device 42.

The third chamber 21 is provided with an eleventh gas connection device 45 . The sixth chamber 24 is provided with a twelfth gas connection device 46 .

The first gas connection device 31 is set up by means of a valve device belonging to it in such a way that the first gas connection device 31 serves to suck gas into the first chamber 19 when the valve is set appropriately.

The third gas connection device 33 is set up by means of a valve device belonging to it in such a way that the third gas connection device 33 is used for sucking gas into the seventh chamber 25 with a correspondingly suitable valve setting.

The sixth gas connection device 38 is set up by means of a valve device belonging to it in such a way that the sixth gas connection device 38 is used for sucking gas into the second chamber 20 with a correspondingly suitable valve setting.

The eighth gas connection device 40 is set up by means of a valve device belonging to it in such a way that the eighth gas connection device 40 serves to suck gas into the eighth chamber 26 with a correspondingly suitable valve setting.

The second gas connection device 32 is set up by means of a valve device belonging to it in such a way that the second gas connection device 32 is used for discharging compressed gas from the first chamber 19 into the first gas line 36 with a correspondingly suitable valve setting.

The fourth gas connection device 34 is set up by means of a valve device belonging to it in such a way that the fourth gas connection device 34 is used for discharging compressed gas from the seventh chamber 25 into the second gas line 37 with a correspondingly suitable valve setting.

The fifth gas connection device 35 is set up by means of an associated valve device in such a way that the fifth gas connection device 35 serves to introduce compressed gas from the first gas line 36 or from the second gas line 37 into the sixth chamber 24 with a correspondingly suitable valve setting.

The seventh gas connection device 39 is set up by means of a valve device belonging to it in such a way that the seventh gas connection device 39 serves to discharge compressed gas from the second chamber 20 into the third gas line 43 with a correspondingly suitable valve setting.

The ninth gas connection device 41 is set up by means of a valve device belonging to it in such a way that the ninth gas connection device 41 serves to discharge compressed gas from the eighth chamber 26 into the fourth gas line 44 with a correspondingly suitable valve setting.

The tenth gas connection device 42 is set up by means of an associated valve device in such a way that the tenth gas connection device 42 serves to introduce compressed gas from the third gas line 43 or from the fourth gas line 44 into the third chamber 21 with a correspondingly suitable valve setting.

The eleventh gas connection device 45 is set up by means of a valve device belonging to it in such a way that the eleventh gas connection device 45 is used for discharging compressed gas from the third chamber 21 with a correspondingly suitable valve setting.

The twelfth gas connection device 46 is set up by means of a valve device belonging to it in such a way that the twelfth gas connection device 46 is used for discharging compressed gas from the sixth chamber 24 with a correspondingly suitable valve setting.

The first liquid connection device 27 is set up by means of a valve device belonging to it in such a way that the first liquid connection device 27 serves as a liquid inlet for pumping liquid into the fourth chamber 22 with a correspondingly suitable valve setting.

The third liquid connection device 29 is set up by means of a valve device belonging to it in such a way that the third liquid connection device 29 serves as a liquid inlet for pumping liquid into the fifth chamber 23 with a correspondingly suitable valve setting.

The second liquid connection device 28 is set up by means of a valve device belonging to it in such a way that the second liquid connection device 28 can be used as a liquid outlet for the appropriate valve setting Squeezing liquid out of the fourth chamber 22 is used.

The fourth liquid connection device 30 is set up by means of a valve device belonging to it in such a way that the fourth liquid connection device 30 serves as a liquid outlet for forcing liquid out of the fourth chamber 23 with a correspondingly suitable valve setting.

In the first exemplary embodiment of the hydraulic piston device 1, oil is used as the liquid.

The first exemplary embodiment of the hydraulic piston device 1 is set up such that compressed gas discharged from the eleventh gas connection device 45 is supplied to a consumer of compressed gas and/or to a compressed gas storage device, which in the present exemplary embodiment is a compressed air storage device.

The first exemplary embodiment of the hydraulic piston device 1 is also set up such that compressed gas discharged from the twelfth gas connection device 46 is supplied to a consumer of compressed gas and/or to the compressed gas storage device, which in the present exemplary embodiment is the compressed air storage device.

The first exemplary embodiment of the hydraulic piston device 1 is also set up in such a way that liquid pressed out of the second liquid connection device 28 is fed to a liquid storage device, which in the present exemplary embodiment is an oil tank.

Furthermore, the first exemplary embodiment of the hydraulic piston device 1 is set up in such a way that liquid pressed out of the fourth liquid connection device 30 is supplied to the liquid storage device, which in the present exemplary embodiment is the oil tank.

In addition, the first exemplary embodiment of the hydraulic piston device 1 is set up in such a way that the hydraulic piston device 1 can draw oil from the oil tank for pumping into the first liquid connection device 27 and/or into the third liquid connection device 29 .

• Als Beispiel einer Startposition wird die in den 1 bis 4 gezeigte Position der Kolbenstange 14 angenommen, bei welcher sich der erste Kolben 15 ungefähr in der Mitte des ersten Hohlzylinders 2, der zweite Kolben 16 ungefähr in der Mitte des zweiten Hohlzylinders 5, der dritte Kolben 17 ungefähr in der Mitte des dritten Hohlzylinders 8 und der vierte Kolben 18 ungefähr in der Mitte des vierten Hohlzylinders 11 befinden. Die vierte Kammer 22 und die fünfte Kammer 23 sind jeweils voller Öl. In der ersten Kammer 19, der zweiten Kammer 20, der dritten Kammer 21, der sechsten Kammer 24, der siebenten Kammer 25 und der achten Kammer 26 befindet sich Luft auf Atmosphärendruck.

The first exemplary embodiment of the hydraulic piston device 1 functions in its operating mode as the first air compression device 1, for example, as follows:

• As an example of a starting position in the 1 until 4 The position of the piston rod 14 shown is assumed, in which the first piston 15 is approximately in the center of the first hollow cylinder 2, the second piston 16 approximately in the center of the second hollow cylinder 5, the third piston 17 approximately in the center of the third hollow cylinder 8 and the fourth piston 18 are approximately in the middle of the fourth hollow cylinder 11. The fourth chamber 22 and the fifth chamber 23 are each full of oil. In the first chamber 19, the second chamber 20, the third chamber 21, the sixth chamber 24, the seventh chamber 25 and the eighth chamber 26 there is air at atmospheric pressure.

The valve device belonging to the first liquid connection device 27 is closed. The valve device belonging to the second liquid connection device 28 is open. The valve device belonging to the third fluid connection device 29 is open. The valve device belonging to the fourth liquid connection device 30 is closed. The valve device belonging to the first gas connection device 31 is open. The valve device belonging to the second gas connection device 32 is closed. The valve device belonging to the third gas connection device 33 is open. The valve device belonging to the fourth gas connection device 34 is closed. The valve device belonging to the fifth gas connection device 35 is closed. The valve device belonging to the sixth gas connection device 38 is closed. The valve device belonging to the seventh gas connection device 39 is open. The valve device belonging to the eighth gas connection device 40 is closed. The valve device belonging to the ninth gas connection device 41 is open. The valve device belonging to the tenth gas connection device 42 is open. The valve device belonging to the eleventh gas connection device 45 is closed. The valve device belonging to the twelfth gas connection device 46 is open.

Further oil is then pumped from the oil tank via the third liquid connection device 29 into the fifth chamber 23 by means of a pump. Due to the incompressibility of the oil, this means that, starting from the in the 1 until 4 assumed starting position shown, the piston rod 14 moves with the first piston 15, the second piston 16, the third piston 17 and the fourth piston 18 to the right. Accordingly, at the same time, the oil is conveyed out of the fourth chamber 22 via the second fluid connection device 28 into the oil tank. The air in the sixth chamber 24 is about the twelfth Gas connection device 46 pushed out of the sixth chamber 24 and supplied to the compressed air storage device. The air from the second chamber 20 and the air from the eighth chamber 26 is pressed via the third gas line 43 or via the fourth gas line 44 through the tenth gas connection device 42 into the third chamber 21 and forms an excess air pressure there. The latter happens even when the volume of the third chamber 21 increases because two chambers—namely the second chamber 20 and the eighth chamber 26—act in only one—namely the third chamber 21. The excess air pressure in the third chamber 21 accordingly helps to force the air out of the sixth chamber 24 through the twelfth gas connection device 46 and also to force the oil out of the fourth chamber 22 through the second liquid connection device 28 . The piston stroke of the piston rod 14 is coordinated such that the movement of the piston rod 14 in the image of 1 until 4 to the right lasts until both the second chamber 20 and the fourth chamber 22 as well as the sixth chamber 24 and the eighth chamber 26 each have a volume of almost zero. Meanwhile, the first chamber 19 has sucked in air via the first gas connection device 31 and the seventh chamber 25 has sucked in air via the third gas connection device 33 . Accordingly, at the end of the movement of the piston rod 14 have in the picture 1 until 4 to the right both the first chamber 19 and the third chamber 21 and the fifth chamber 23 and the seventh chamber 25 assumed their maximum possible volume. In this case, air is then at atmospheric pressure both in the first chamber 19 and in the seventh chamber 25 . The third chamber 21 contains air at a pressure above atmospheric pressure, ie compressed air, and the fifth chamber 23 contains oil.

After completion of the stroke of the piston rod 14 in the image of 1 until 4 The valve devices are switched to the right as follows: The valve device belonging to the first liquid connection device 27 is opened. The valve device belonging to the second liquid connection device 28 is closed. The valve device belonging to the third liquid connection device 29 is closed. The valve device belonging to the fourth liquid connection device 30 is opened. The valve device belonging to the first gas connection device 31 is closed. The valve device belonging to the second gas connection device 32 is opened. The valve device belonging to the third gas connection device 33 is closed. The valve device belonging to the fourth gas connection device 34 is opened. The valve device belonging to the fifth gas connection device 35 is opened. The valve device belonging to the sixth gas connection device 38 is opened. The valve device belonging to the seventh gas connection device 39 is closed. The valve device belonging to the eighth gas connection device 40 is opened. The valve device belonging to the ninth gas connection device 41 is closed. The valve device belonging to the tenth gas connection device 42 is closed. The valve device belonging to the eleventh gas connection device 45 is opened and the compressed air located in the third chamber 21 is fed to the compressed air storage device. The valve device belonging to the twelfth gas connection device 46 is closed.

Oil is now pumped from the oil tank via the first liquid connection device 27 into the fourth chamber 22 by means of the pump. Due to the incompressibility of the oil, this leads to the fact that the 1 until 4 the piston rod 14 with the first piston 15, the second piston 16, the third piston 17 and the fourth piston 18 is now moved to the left. Accordingly, at the same time, the oil is conveyed out of the fifth chamber 23 via the fourth liquid connection device 30 into the oil tank. The air located in the third chamber 21 is pressed out of the third chamber 21 via the eleventh gas connection device 45 and fed to the compressed air storage device. The air from the first chamber 19 and the air from the seventh chamber 25 is pressed via the first gas line 36 or via the second gas line 37 through the fifth gas connection device 35 into the sixth chamber 24 and forms an excess air pressure there. The latter happens even when the volume of the sixth chamber 24 increases because two chambers—namely the first chamber 19 and the seventh chamber 25—act in only one—namely the sixth chamber 24. The excess air pressure in the sixth chamber 24 accordingly helps to press the air out of the third chamber 21 through the eleventh gas connection device 45 and also to press out the oil from the fifth chamber 23 through the fourth liquid connection device 30 . The piston stroke of the piston rod 14 is coordinated such that the movement of the piston rod 14 in the image of 1 until 4 to the left lasts until both the first chamber 19 and the third chamber 21 as well as the fifth chamber 23 and the seventh chamber 25 each have a volume of almost zero. Meanwhile, the second chamber 20 has sucked in air via the sixth gas connection device 38, and the eighth chamber 26 has via the eighth gas connection device tion 40 air sucked. Accordingly, at the end of the movement of the piston rod 14 have in the picture 1 until 4 to the left both the second chamber 20 and the fourth chamber 22 and the sixth chamber 24 and the eighth chamber 26 assumed their maximum possible volume. In this case, air is then at atmospheric pressure both in the second chamber 20 and in the eighth chamber 26 . The sixth chamber 24 contains air at a pressure above atmospheric pressure, ie compressed air, and the fourth chamber 22 contains oil.

After completion of the stroke of the piston rod 14 in the image of 1 until 4 to the left, the valve devices are switched back to their first position described above, namely: The valve device belonging to the first liquid connection device 27 is opened. The valve device belonging to the second liquid connection device 28 is closed. The valve device belonging to the third liquid connection device 29 is closed. The valve device belonging to the fourth liquid connection device 30 is opened. The valve device belonging to the first gas connection device 31 is closed. The valve device belonging to the second gas connection device 32 is opened. The valve device belonging to the third gas connection device 33 is closed. The valve device belonging to the fourth gas connection device 34 is opened. The valve device belonging to the fifth gas connection device 35 is opened. The valve device belonging to the sixth gas connection device 38 is opened. The valve device belonging to the seventh gas connection device 39 is closed. The valve device belonging to the eighth gas connection device 40 is opened. The valve device belonging to the ninth gas connection device 41 is closed. The valve device belonging to the tenth gas connection device 42 is closed. The valve device belonging to the eleventh gas connection device 45 is opened. The valve device belonging to the twelfth gas connection device 46 is closed.

Oil is now pumped from the oil tank via the third liquid connection device 29 into the fifth chamber 23 by means of the pump. Due to the incompressibility of the oil, this leads to the fact that the 1 until 4 the piston rod 14 with the first piston 15, the second piston 16, the third piston 17 and the fourth piston 18 is now moved to the right again. Accordingly, at the same time, the oil is conveyed out of the fourth chamber 22 via the second fluid connection device 28 into the oil tank. The air in the sixth chamber 24 is pressed out of the sixth chamber 24 via the twelfth gas connection device 46 and fed to the compressed air storage device. The air from the second chamber 20 and the air from the eighth chamber 26 is pressed via the third gas line 43 or via the fourth gas line 44 through the tenth gas connection device 42 into the third chamber 21 and forms an excess air pressure there. The latter happens even when the volume of the third chamber 21 increases because two chambers—namely the second chamber 20 and the eighth chamber 26—act in only one—namely the third chamber 21. The excess air pressure in the third chamber 21 accordingly helps to force the air out of the sixth chamber 24 through the twelfth gas connection device 46 and also to force the oil out of the fourth chamber 22 through the second liquid connection device 28 . The piston stroke of the piston rod 14 is coordinated such that the movement of the piston rod 14 in the image of 1 until 4 to the right lasts until both the second chamber 20 and the fourth chamber 22 as well as the sixth chamber 24 and the eighth chamber 26 each have a volume of almost zero. Meanwhile, the first chamber 19 has sucked in air via the first gas connection device 31 and the seventh chamber 25 has sucked in air via the third gas connection device 33 . Accordingly, at the end of the movement of the piston rod 14 have in the picture 1 until 4 to the right both the first chamber 19 and the third chamber 21 and the fifth chamber 23 and the seventh chamber 25 assumed their maximum possible volume. In this case, air is then at atmospheric pressure both in the first chamber 19 and in the seventh chamber 25 . The third chamber 21 contains air at a pressure above atmospheric pressure, ie compressed air, and the fifth chamber 23 contains oil.

After completion of the stroke of the piston rod 14 just described in the picture 1 until 4 to the right, the valve devices are then switched over in preparation for the repeated stroke of the piston rod 14 to the left, as has already been explained above before the description of the stroke of the piston rod 14 to the left. The piston rod 14 then moves back and forth with the first piston 15, the second piston 16, the third piston 17 and the fourth piston 18, and compressed air is alternately provided at the eleventh gas connection device 45 or at the twelfth gas connection device 46 Which either - as described above - a compressed air storage device can be supplied, but which also instead any NEM compressed air consumer, such as a blower device or a pneumatic hammer device, can be supplied. In other exemplary embodiments of the hydraulic piston device 1 according to the invention, provision can also be made for the eleventh gas connection device 45 and the twelfth gas connection device 46 to be provided with such valve devices that a user can optionally decide operatively whether the gas connection device 45 straight out of the respective eleventh or twelfth gas connection device 46 exiting compressed air is either introduced into a compressed air storage device or supplied to a consumer of compressed air.

6 shows a second exemplary embodiment of the hydraulic piston device 1 schematically and not to scale. This second exemplary embodiment of the hydraulic piston device 1 functions in principle in exactly the same way as that described above with reference to FIG 1 until 4 described first embodiment of the hydraulic piston device 1, but differs from this by the arrangement and the proportions of the four hollow cylinders 2, 5, 8, 11, which results in improved operational properties.

In the case of the above with reference to the 1 until 4 All four hollow cylinders 2, 5, 8, 11 described in the first exemplary embodiment of the hydraulic piston device 1 have the same shape and size, and each one of the four hollow cylinders 2, 5, 8, 11 is arranged separately from the others, so that there are three spatial There are sections in which the piston rod 14 is located outside of any hollow cylinder 2, 5, 8, 11 (see in this respect 1 until 4 ). Such a design of the hydraulic piston device 1 is quite possible as an exemplary embodiment, it actually works and is well suited for explaining the basic functioning of the hydraulic piston device 1, but such a design is far from optimal for the purposes of gas compression or air compression.

At the in 6 shown second embodiment of the hydraulic piston device 1, all four hollow cylinders 2, 5, 8, 11 each have the same length. The second hollow cylinder 5 and the third hollow cylinder 8 each have the same diameter. The first hollow cylinder 2 and the fourth hollow cylinder 11 each have the same diameter, and the diameter of the first hollow cylinder 2 is larger than the diameter of the second hollow cylinder 5. It is particularly preferred to make the diameter of the first hollow cylinder 2 at least twice as large as the diameter of the second hollow cylinder 5. The size of the first piston 15 and the size of the fourth piston 18 must of course also be adjusted accordingly in order to ensure that they continue to fit closely to the inner wall of the first hollow cylinder 2 and the fourth hollow cylinder 11 snuggly and continue to ensure a pneumatically tight separation of the first chamber 19 from the second chamber 20 and the seventh chamber 25 from the eighth chamber 26. The advantage of such in 6 shown construction compared to in the 1 until 4 The construction shown for generating compressed air is that in the second exemplary embodiment of the piston device 1, when the piston rod 14 moves to the right, the second chamber 20 with a large volume and the eighth chamber 26 with a large volume flow into the third chamber 21, which has a much smaller volume , act in such a way that a significantly higher excess air pressure can be achieved in the third chamber 21 than in the first embodiment of the piston device 1. The same also applies to the movement of the piston rod 14 to the left: In the second embodiment of the piston device 1 act during movement of the piston rod 14 to the left, the first chamber 19 with a large volume and the seventh chamber 25 with a large volume into the sixth chamber 24, which has a much smaller volume, so that a significantly higher excess air pressure is achieved in the sixth chamber 24 can than in the first exemplary embodiment of the K according to the invention piston device 1.

Generally speaking, the size ratios of the four hollow cylinders 2, 5, 8, 11 to one another are always in relation to the gas pressure or air pressure that can be achieved at the end of the gas or air compression.

This in 6 The second exemplary embodiment of the hydraulic piston device 1 shown is also set up such that the first hollow cylinder 2 and the second hollow cylinder 5 are seated directly against one another, so that the second end wall 4 and the third end wall 6 coincide at least partially. In addition, the third hollow cylinder 8 and the fourth hollow cylinder 11 sit directly against one another, so that the sixth end wall 10 and the seventh end wall 12 coincide at least partially. Such a structure offers significant advantages in terms of sealing technology compared to the 1 until 4 shown structure of the first embodiment of the hydraulic piston device 1, in which all four hollow cylinders 2, 5, 8, 11 are arranged completely separately from each other and correspondingly a higher sealing technology effort must be operated.

In a further embodiment of the hydraulic piston device 1, not shown in the figures, it is provided that the diameter of the piston rod 14 over the length of the col The piston rod 14 varies such that the piston rod 14 immediately following the first piston 15 in the direction of the second piston 16 has a larger diameter than immediately following the second piston 16 in the direction of the first piston 15 and that, moreover, the piston rod 14 immediately following the fourth piston 18 in the direction of the third piston 17 has a larger diameter than immediately following the third piston 17 in the direction of the fourth piston 18 . Such a design measure provides even further improved support for the gas or air compression.

Although the individual specific exemplary embodiments of the hydraulic piston device 1 described in more detail here have been explained above, above all with reference to the use or compression of the gas air, it should be emphasized at this point that any other gas, for example Biogas and/or methane and/or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of air and one or more hydrocarbon gases can be used in the hydraulic piston device 1 and compressed by it.

The same applies to the naming of oil as the liquid to be used in the hydraulic piston device 1 . Although oil is often used as a liquid in the hydraulic piston device 1 for purely economic reasons, the operation of the hydraulic piston device 1 is in principle also readily possible with any other liquid, for example water.

The use of the hydraulic piston device 1 for the purpose of gas compression has been described above, and the hydraulic piston device 1 is always designed and suitable for this purpose.

However, the hydraulic piston device 1 can also function as an essential component of a compressed gas energy conversion device 50 and then not only—as described above—in gas compression mode, but also vice versa, namely in gas expansion mode. An exemplary embodiment of the controllable drive device according to the invention for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device is accordingly set up such that the compressed gas-based energy conversion device has such a compressed gas energy conversion device 50 .

5 shows a first embodiment of this compressed gas energy conversion device 50, and 7 shows a second embodiment of this compressed gas energy conversion device 50. The difference between these two just mentioned embodiments of the compressed gas energy conversion device 50 is that in 5 shown first embodiment of the compressed gas energy conversion device 50 is constructed on the basis of in the 1 until 4 illustrated first embodiment of the hydraulic piston device 1 and in 7 shown second embodiment of the compressed gas energy conversion device 50 is constructed on the basis of in 6 illustrated second embodiment of the hydraulic piston device 1.

Since both the first exemplary embodiment of the hydraulic piston device 1 and the second exemplary embodiment of the hydraulic piston device 1 have already been described in great detail above, the 5 and 7 are considered together, and in the following the focus is placed solely on the description of those components of compressed gas energy conversion device 50 which are identical in the first exemplary embodiment of compressed gas energy conversion device 50 and in the second exemplary embodiment of compressed gas energy conversion device 50, so that in the following there is no further distinction between the 5 and 7 or between the first exemplary embodiment of the compressed gas energy conversion device 50 and the second exemplary embodiment of the compressed gas energy conversion device 50 .

The compressed gas energy conversion device 50 has a hydraulic piston device 1 as an essential component, the latter being able to be constructed, for example, like the first exemplary embodiment of the hydraulic piston device 1 already described in detail above (cf 5 ) or, for example, like the second exemplary embodiment of the hydraulic piston device 1 already described in detail above (cf 7 ). The compressed gas energy conversion device 50 also has a compressed gas storage device--not shown in the figures--and a liquid storage device--also not shown in the figures.

The eleventh gas connection device 45 is connected to the compressed gas storage device and set up by means of the valve device belonging to the eleventh gas connection device 45 in such a way that the eleventh gas connection device 45 with a correspondingly suitable valve setting for insertion ren compressed gas from the compressed gas storage device in the third chamber 21 is used.

The twelfth gas connection device 46 is connected to the compressed gas storage device and is set up by means of the valve device belonging to the twelfth gas connection device 46 in such a way that the twelfth gas connection device 46 is used for introducing compressed gas from the compressed gas storage device into the sixth chamber 24 when the valve is set appropriately.

The second liquid connection device 28 is connected to the liquid storage device and is set up by means of the valve device belonging to the second liquid connection device 28 in such a way that the second liquid connection device 28 is used to suck liquid from the liquid storage device into the fourth chamber 22 when the valve position is appropriate.

The fourth liquid connection device 30 is connected to the liquid storage device and is set up by means of the valve device belonging to the fourth liquid connection device 30 in such a way that the fourth liquid connection device 30 is used for sucking liquid from the liquid storage device into the fifth chamber 23 with a correspondingly suitable valve setting.

The first liquid connection device 27 is set up by means of the associated valve device in such a way that the first liquid connection device 27, with a correspondingly suitable valve setting, serves to introduce liquid from the fourth chamber 22 into a first liquid line 47, which is designed in such a way that it can be introduced into it and liquid flowing through it to a machine 48 to be driven by the flowing liquid, this machine 48 being, for example, a drive device for an electrical energy generator or the motor already mentioned above for driving the land vehicle, water vehicle and/or aircraft, in which the exemplary embodiment of the controllable Drive device is installed with the compressed gas energy conversion device 50 described here, can be.

The third liquid connection device 29 is set up by means of the associated valve device in such a way that the third liquid connection device 29 is used, with a correspondingly suitable valve setting, for introducing liquid from the fifth chamber 23 into a second liquid line 49, which is set up in such a way that it is introduced into it and liquid flowing through it to a machine 48 to be driven by the flowing liquid, which is, for example, a drive device for an electrical energy generator or the motor already mentioned above for driving the land vehicle, water vehicle and/or aircraft, in which the exemplary embodiment of the controllable drive device according to the invention with the Compressed gas energy conversion device 50 described here is installed, can be.

The tenth gas connection device 42 is set up by means of the associated valve device in such a way that the tenth gas connection device 42 serves to introduce gas from the third chamber 21 into a fifth gas line 51 with a correspondingly suitable valve setting.

There is also a first pressure control valve device 52, which regulates gas pressure and liquid pressure against one another, is connected to the fifth gas line 51 on the gas side by means of a sixth gas line 53 and is connected to the second liquid line 49 on the liquid side by means of a third liquid line 54.

The fifth gas connection device 35 is set up by means of the associated valve device in such a way that the fifth gas connection device 35 serves to introduce gas from the sixth chamber 24 into a seventh gas line 55 with a correspondingly suitable valve setting.

There is also a second pressure control valve device 56, which regulates gas pressure and liquid pressure against one another, is connected to the seventh gas line 55 on the gas side by means of an eighth gas line 57 and is connected to the first liquid line 47 on the liquid side by means of a fourth liquid line 58.

The fifth gas line 51 also leads to a consumer device 59 that uses gas originating from the fifth gas line 51 thermally and/or mechanically and/or chemically.

The seventh gas line 55 also leads to a consumer device 59 that uses gas originating from the seventh gas line 55 thermally and/or mechanically and/or chemically.

As in the case of the hydraulic piston device 1 described in detail further above, the compressed gas energy conversion device 50 can of course also use air as the gas, for example. However, it is also just as possible with the compressed gas energy conversion device 50 that instead of or together with air, any other gas, for example biogas and/or methane and/or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of Air and one or more hydrocarbon gases may be used in the compressed gas energy conversion device 50.

The same applies to the liquid to be used in the compressed gas energy conversion device 50 . Although oil is often used as the liquid in the compressed gas energy conversion device 50 for purely practical economic reasons, the compressed gas energy conversion device 50 can in principle also be operated with any other liquid, for example water.

Both exemplary embodiments of the compressed gas energy conversion device 50 described above from a purely structural point of view function as follows:

Imagine that, based on the views of the 5 and the 7 , initially the piston rod 14 may be in its most left-shifted position. Accordingly, the first chamber 19, the third chamber 21, the fifth chamber 23 and the seventh chamber 25 initially each have their smallest possible volume, while the second chamber 20, the fourth chamber 22, the sixth chamber 24 and the eighth chamber 26 initially their respective have the largest possible volume. The second chamber 20, sixth chamber 24 and eighth chamber 26 are each initially filled with gas, while the fourth chamber 22 is initially filled with liquid. Air may be used as the gas in the exemplary embodiments of the compressed gas energy conversion device 50 to be described here, and oil may be used as the liquid in the exemplary embodiments of the compressed gas energy conversion device 50 to be described here.

The valve device belonging to the first gas connection device 31, the valve device belonging to the second gas connection device 32, the valve device belonging to the third gas connection device 33, the valve device belonging to the fourth gas connection device 34, the valve device belonging to the sixth gas connection device 38, the valve device belonging to the seventh gas connection device 39 belonging valve device, the valve device belonging to the eighth gas connection device 40 and the valve device belonging to the ninth gas connection device 41 are open and remain - at least for the purposes of the following functional description of the two in the 5 or. 7 shown embodiments of the compressed gas energy conversion device 50 - also constantly open. As can be seen from the following functional description of the two in the 5 or. 7 As will be readily apparent from the exemplary embodiments of compressed gas energy conversion device 50 shown, the first chamber 19, the second chamber 20, the seventh chamber 25 and the eighth chamber 26 can, for example, simply be used to collect compressed air from the compressed air storage device that is relaxing and consequently cooling to pass cold air through to a consumer, or they can--when the compressed gas energy conversion device 50 is operated in a warm environment or in a warm part of the environment--can be used to simply draw in warm outside air and pass it through to a consumer of warm air. However, the options mentioned in the previous paragraph are only possible side effects which—if desired—can also be used during the operation of the compressed gas energy conversion device 50, but do not necessarily have to be used.

However, the second hollow cylinder 5 with the third chamber 21 and the fourth chamber 22 and the third hollow cylinder 8 with the fifth chamber 23 and the sixth chamber 24 are absolutely essential for the operation of the compressed gas energy conversion device 50.

The valve device belonging to the tenth gas connection device 42 is initially closed. The valve device belonging to the twelfth gas connection device 46 is initially also closed. The valve device belonging to the second liquid connection device 28 is initially closed, while the valve device belonging to the first liquid connection device 27 is initially open. The valve device associated with the third fluid connection device 29 is initially closed, and the valve device associated with the fourth fluid connection device 30 is initially open.

The valve device belonging to the fifth gas connection device 35 is initially open. The valve device belonging to the eleventh gas connection device 45 is also initially open. Accordingly, compressed air is introduced from the compressed air storage device through the eleventh gas connection device 45 into the third chamber 21, with the result that the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIG 5 or. 7 moved to the right. Accordingly, air is pressed out of the sixth chamber 24 through the fifth gas connection device 35 and fed via the seventh gas line 55 to the consumer device 59, which uses the air thermally and/or mechanically and/or chemically. The load device 59 just mentioned can be, for example, a turbine driving an electric generator or, for example, an exemplary embodiment of one that is to be described further below Compressed gas energy conversion heat exchanger device 60, 146 or, for example, an exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 to be described further below or, for example, an exemplary embodiment of a compressed gas energy conversion device to be described further below. At the same time, the air pressed out of the sixth chamber 24 is present via the eighth gas line 57 on the air side of the second pressure control valve device 56, which regulates air pressure and oil pressure against one another.

During the above-mentioned movement of the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIG 5 or. 7 to the right, oil is also pressed out of the fourth chamber 22 and reaches a machine 48 to be driven by flowing oil via the first liquid connection device 27 and the first liquid line 47, which machine 48 can be driven by the flowing oil, for example a turbine driving an electric generator or the above-mentioned motor for driving a land , Water and / or aircraft can be. The oil flow through the first liquid line 47 is controlled via the second pressure control valve device 56, which regulates air pressure and oil pressure against one another, because the first liquid connection device 27 communicates via the first liquid line 47, the fourth liquid line 58 branching off therefrom, and the second pressure control valve device 56, which supplies air pressure and oil pressure against each other, with the fifth gas connection device 35.

In addition, in the movement just mentioned, the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIG 5 or. 7 sucked to the right oil from the oil storage device via the fourth liquid connection device 30 into the fifth chamber 23 inside.

Once in the views of 5 or. 7 When the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it has reached its rightmost position, the first chamber 19, the third chamber 21, the fifth chamber 23 and the seventh chamber 25 each have their largest possible volume , while the second chamber 20, the fourth chamber 22, the sixth chamber 24 and the eighth chamber 26 have each assumed their smallest possible volume. The first chamber 19, the third chamber 21 and the seventh chamber 25 are each filled with air, while the fifth chamber 23 is filled with oil.

The valve devices are now switched over as follows: The valve device belonging to the eleventh gas connection device 45 is closed. The valve device belonging to the tenth gas connection device 42 is opened. The valve device 35 belonging to the fifth gas connection device 35 is closed. The valve device 46 belonging to the twelfth gas connection device is opened. The valve device belonging to the fourth liquid connection device 30 is closed. The valve device belonging to the second liquid connection device 28 is opened. The valve device belonging to the first liquid connection device 27 is closed. The valve device belonging to the third liquid connection device 29 is opened.

Accordingly, compressed air is now introduced from the compressed air storage device through the twelfth gas connection device 46 into the sixth chamber 24, which means that the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIGS 5 or. 7 moved to the left. Accordingly, air is pressed out of the third chamber 21 through the tenth gas connection device 42 and fed via the fifth gas line 51 to the consumer device 59, which uses the air thermally and/or mechanically and/or chemically. At the same time, the air pressed out of the third chamber 21 is present via the sixth gas line 53 on the air side of the first pressure control valve device 52, which controls the air pressure and oil pressure against one another.

During the above-mentioned movement of the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIG 5 or. 7 to the left, oil is pressed out of the fifth chamber 23 and reaches the machine 48 to be driven by the flowing oil via the third liquid connection device 29 and the second liquid line 49, which machine 48 can be driven by the flowing oil, for example a turbine driving an electric generator or the motor already mentioned above for driving a land , Water and / or aircraft can be. The oil flow through the second liquid line 49 is controlled via the first pressure control valve device 52, which regulates air pressure and oil pressure against one another, because the third liquid connection device 29 communicates via the second liquid line 49, the third liquid line 54 branching off from it, and the first pressure control valve device 52, which regulates air pressure and oil pressure against each other, with the tenth gas connection device 42.

In addition, in the movement just mentioned, the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIG 5 or. 7 to the left oil from the oil spoke reinrichtung sucked into the fourth chamber 22 via the second liquid connection device 28 inside.

Once in the views of 5 or. 7 the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it has again reached its position, which has been moved as far to the left as possible, the first chamber 19, the third chamber 21, the fifth chamber 23 and the seventh chamber 25 each have their respective positions again assumed the smallest possible volume, while the second chamber 20, the fourth chamber 22, the sixth chamber 24 and the eighth chamber 26 have each assumed their largest possible volume again. The second chamber 20, the sixth chamber 24 and the eighth chamber 26 are each filled with air, while the fourth chamber 22 is filled with oil.

The valve devices are now switched back into their respective initial position, namely as follows: The valve device belonging to the eleventh gas connection device 45 is opened. The valve device belonging to the tenth gas connection device 42 is closed. The valve device belonging to the fifth gas connection device 35 is opened. The valve device 46 belonging to the twelfth gas connection device is closed. The valve device belonging to the fourth liquid connection device 30 is opened. The valve device belonging to the second liquid connection device 28 is closed. The valve device belonging to the first liquid connection device 27 is opened. The valve device belonging to the third liquid connection device 29 is closed.

Accordingly, compressed air from the compressed air storage device is again introduced through the eleventh gas connection device 45 into the third chamber 21, which means that the piston rod 14 with the four pistons 15, 16, 17, 18 fixed to it in the views of FIGS 5 or. 7 moves to the right and the corresponding functional sequence is repeated as already described above with regard to the corresponding movement of the piston rod 14 to the right.

The piston rod 14 moves back and forth with the four pistons 15, 16, 17, 18 fixed to it and converts the energy stored in the compressed air storage device in the form of compressed air in the consumer device 59, which uses gas thermally and/or mechanically and/or or used chemically, as well as in the machine 48 to be driven by flowing liquid into other forms of energy.

It should be expressly pointed out at this point that both the exemplary embodiments of the hydraulic piston device 1 described here and the exemplary embodiments of the compressed gas energy conversion device 50 described here are components of a controllable drive device according to the invention for a land vehicle, water vehicle and/or aircraft and accordingly all - as from The above description and the associated figures readily apparent - use the principle of the double-acting hydraulic-pneumatic tandem cylinder. Accordingly, a control device is installed in the exemplary embodiments of the hydraulic piston device 1 and in the exemplary embodiments of the compressed gas energy conversion device 50, by means of which the driver and/or an automatic driver of the land vehicle, water vehicle and/or aircraft can control a driving force of the above-mentioned motor. The control device can be set up in such a way that the control device can control one or more valves in the hydraulic piston device 1 and/or in the compressed gas energy conversion device 50 during ongoing operation of the engine in such a way that an active supply of compressed gas from the outside into a chamber to which pressurized gas is to be applied during a working stroke of the double-acting hydraulic-pneumatic tandem cylinder can already be ended before a piston that delimits the chamber and is moved by the pressurized gas reaches a stop that mechanically limits its movement path, with the said piston moving after the active supply of compressed gas from the outside then moves only under the influence of the compressed gas already filled into the chamber in the direction of the stop mechanically limiting the movement distance of the piston. The control device can also be set up in such a way that the control device can control one or more valves in the hydraulic piston device 1 and/or in the compressed gas energy conversion device 50 during ongoing operation of the engine in such a way that an active compressed gas supply strength of outside in a chamber to be acted upon during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder with pressurized gas in a certain pressure range steplessly and/or in stages.

In further of its exemplary embodiments, the controllable drive device according to the invention for a land vehicle, water vehicle and/or aircraft is set up in such a way that its compressed gas-based energy conversion device has a compressed gas energy conversion heat exchanger device 60, 146.

Referring to the 8th , 9 and 10 An exemplary embodiment of the compressed gas energy conversion heat exchanger device 60 will now be described. The 8th , 9 and 10 are to be considered in this context. 8th shows schematically and not to scale a longitudinal section through the exemplary embodiment of the compressed gas energy conversion heat exchanger device 60. 9 shows schematically and not to scale a longitudinal section through the central portion of the embodiment of the compressed gas energy conversion heat exchanger device 60 of FIG 8th . 10 shows, schematically and not to scale, a plan view of the in 9 in the longitudinal section to be seen central portion of the embodiment of the compressed gas energy conversion heat exchanger device 60 of 8th .

That in the 8th , 9 and 10 The exemplary embodiment of the compressed gas energy conversion heat exchanger device 60 shown has the following: a fifth hollow cylinder 61 which has a ninth end wall 62 and a tenth end wall 63; a first central part 64, which is arranged centrally in relation to the longitudinal direction of the fifth hollow cylinder 61 and is attached to the inner wall inside the fifth hollow cylinder 61, extends radially in its longitudinal position over the entire circumference of the inner wall of the fifth hollow cylinder 61 but has a through hole in the middle; a second central part 65 positioned in said hole and fixed there by serving both as the front part of a sixth hollow cylinder 66 and as the front part of a seventh hollow cylinder 67, the sixth hollow cylinder 66 extending from the second central part 65, extends in the direction of the ninth end wall 62 and through a first opening in the ninth end wall 62 and is fixed to the ninth end wall 62 and wherein the seventh hollow cylinder 67 extends, starting from the second central part 65, in the direction of the tenth end wall 63 and through a first opening extends through the tenth end wall 63 and is fixed to the tenth end wall 63 and the sixth hollow cylinder 66 is delimited at its end opposite the second middle part 65 by an eleventh end wall 79 and the seventh hollow cylinder 67 at its second middle part 65 opposite end is bounded by a twelfth end wall 80; an eighth hollow cylinder 68, which extends between the first middle part 64 and the second middle part 65 and can be moved back and forth in the longitudinal direction of the fifth hollow cylinder 61, the eighth hollow cylinder 68 being supported at its end pointing towards the ninth end wall 62 by a fifth piston 69 is closed, which has the shape of a circular disc and whose outer circumference nestles against the inner wall of the fifth hollow cylinder 61 and whose inner circumference nestles against an outer wall of the sixth hollow cylinder 66, and the eighth hollow cylinder 68 at its end wall 63 pointing towards the tenth end is closed off by a sixth piston 70, which has the shape of a circular disc and whose outer circumference nestles against the inner wall of the fifth hollow cylinder 61 and whose inner circumference nestles against an outer wall of the seventh hollow cylinder 67, and where, moreover, the fifth hollow cylinder 61, the first middle part 64, the second middle part 65, i The sixth hollow cylinder 66, the seventh hollow cylinder 67, the eighth hollow cylinder 68, the fifth piston 69 and the sixth piston 70 are set up and arranged in such a way that the following six chambers of variable volume that are hydraulically and pneumatically sealed against one another result: a ninth chamber 71, which is delimited by the ninth end wall 62, the fifth piston 69, the inner wall of the fifth hollow cylinder 61 and the outer wall of the sixth hollow cylinder 66, a tenth chamber 72, which is delimited by the tenth end wall 63, the sixth piston 70, the inner Wall of the fifth hollow cylinder 61 and the outer wall of the seventh hollow cylinder 67, an eleventh chamber 73, which is delimited by the fifth piston 69, the first middle part 64, the inner wall of the fifth hollow cylinder 61 and an outer wall of the eighth hollow cylinder 68, a twelfth chamber 74, which is delimited by the sixth piston 70, the first middle part 64, the inner wall of fifth hollow cylinder 61 and the outer wall of the eighth hollow cylinder 68, a thirteenth chamber 75, which is delimited by the fifth piston 69, the second central part 65, the outer wall of the sixth hollow cylinder 66 and an inner wall of the eighth hollow cylinder 68, a fourteenth chamber 76, which is delimited by the sixth piston 70, the second central part 65, the outer wall of the seventh hollow cylinder 67 and the inner wall of the eighth hollow cylinder 68, with the ninth chamber 71, the tenth chamber during operation of the compressed gas energy conversion heat exchanger device 60 72, the thirteenth chamber 75 and the fourteenth chamber 76 for containing gas and the eleventh chamber 73 and the twelfth chamber 74 for containing liquid; a ninth gas line 77, which runs within the sixth hollow cylinder 66 and, starting from the second central part 65, extends through an opening in the eleventh end wall 79, with an interior space of the sixth hollow cylinder 66 not filled by the ninth gas line 77 during operation of the Compressed gas energy conversion heat exchanger device 60 is provided for receiving liquid; a tenth gas line 78, which runs within the seventh hollow cylinder 67 and, starting from the second central part 65, extends through an opening in the twelfth end wall 80, with a non the interior space of the seventh hollow cylinder 67 filled by the tenth gas line 78 is provided during operation of the compressed gas energy conversion heat exchanger device 60 for receiving liquid; a fifth liquid line 81, which branches off from the sixth hollow cylinder 66 at the end of the sixth hollow cylinder 66 opposite the second central part 65 and extends outside the fifth hollow cylinder 61 to the position of the twelfth chamber 74; a ninth liquid line 96 provided with a valve device, which at one end communicates with the twelfth chamber 74 through a first opening provided in the area of the twelfth chamber 74 near the first central part 64 in the side wall of the fifth hollow cylinder 61 and at its other end opens into the fifth liquid line 81; a tenth liquid line 97 provided with a valve device, which at one end communicates with the eleventh chamber 73 through a second opening provided in the area of the eleventh chamber 73 near the first central part 64 in the side wall of the fifth hollow cylinder 61 and at its other end opens into the fifth liquid line 81; a sixth liquid line 82, which branches off from the seventh hollow cylinder 67 at the end of the seventh hollow cylinder 67 opposite the second central part 65 and is provided for connection to a liquid tank; a first gas conduction device 83 arranged within the second central part 65, which is set up and connected to both the ninth gas line 77 and the thirteenth chamber 75 in such a way that gas flows through the first gas conduction device 83 between the ninth gas line 77 and the thirteenth chamber 75 and can flow forth; a second gas conduction device 84 arranged within the second central part 65, which is set up and connected to both the tenth gas line 78 and the fourteenth chamber 76 in such a way that gas flows through the second gas conduction device 84 between the tenth gas line 78 and the fourteenth chamber 76 and can flow forth; a liquid passage device 85 arranged inside the second central part 65, which is set up in such a way that it connects the part of the interior of the sixth hollow cylinder 66 intended to hold liquid and the part of the interior of the seventh hollow cylinder 67 intended to hold liquid in such a way that liquid can flow back and forth between the sixth hollow cylinder 66 and the seventh hollow cylinder 67 through the liquid passage means 85; a seventh fluid line 94 provided with a valve device, which communicates with the eleventh chamber 73 through a third opening provided in the area of the eleventh chamber 73 near the first central part 64 in the side wall of the fifth hollow cylinder 61, so that with a corresponding movement of the fifth piston 69 liquid can be pressed from the eleventh chamber 73 into the seventh liquid line 94; an eighth fluid line 95 provided with a valve device, which communicates with the twelfth chamber 74 through a fourth opening provided in the region of the twelfth chamber 74 near the first central part 64 in the side wall of the fifth hollow cylinder 61, so that with a corresponding movement of the sixth piston 70 liquid from the twelfth chamber 74 can be pushed into the eighth liquid line 95; a thirteenth gas connection device 98 provided with a valve device, which is in communication with the ninth chamber 71 through a second opening in the ninth end wall 62, and a fourteenth gas connection device 99 provided with a valve device, which is connected through a second opening in the tenth end wall 63 with the tenth Chamber 72 communicates.

The first gas passage device 83 has an elongate first channel 86 arranged within the second central part 65, which is provided with a first riser pipe 87 at its center, with a second riser pipe 88 at one end and with a third riser pipe 89 at its other end , wherein the first riser pipe 87 opens into the ninth gas line 77 and the second riser pipe 88 and the third riser pipe 89 open into the thirteenth chamber 75, respectively.

The second gas passage device 84 has an elongate second channel 90 arranged within the second central part 65, which is provided with a fourth riser pipe 91 at its center, with a fifth riser pipe 92 at one end and with a sixth riser pipe 93 at its other end , wherein the fourth riser pipe 91 opens into the tenth gas line 78 and the fifth riser pipe 92 and the sixth riser pipe 93 open into the fourteenth chamber 76, respectively.

The liquid passage device 85 has a third channel 85a and a fourth channel 85b, with both the third channel 85a and the fourth channel 85b each extending through the second central part 65 and thereby both from the first gas passage device 83 and from the second gas passage device 84 are completely separated and are open to both the sixth hollow cylinder 66 and the seventh hollow cylinder 67 .

At the in the 8th , 9 and 10 shown embodiment of the compressed gas energy conversion heat exchanger device 60, the third channel 85a and the fourth channel 85b a bean-shaped or kidney-shaped cross section.

The sixth hollow cylinder 66 is screwed into the second middle part 65 by means of a thread in a circumferential groove in the second middle part 65 and in this way is fastened to the second middle part 65 . The seventh hollow cylinder 67 is screwed into the second middle part 65 by means of a thread in a circumferential groove in the second middle part 65 and in this way is fastened to the second middle part 65 .

At the in the 8th , 9 and 10 shown embodiment of the compressed gas energy conversion heat exchanger device 60 - as incidentally also in the further below with reference to 16 described further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146 and as in all possible exemplary embodiments of the controllable drive device according to the invention with compressed gas energy conversion heat exchanger device - basically any gas can be used as the gas, for example air and/or biogas and/or methane and /or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of air and one or more hydrocarbon gases. Although oil is preferably used as the liquid, it can be used in the in the 8th , 9 and 10 shown embodiment of the compressed gas energy conversion heat exchanger device 60 - as well as in the below with reference to 16 described further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146 and as in all possible exemplary embodiments of the controllable drive device according to the invention with compressed gas energy conversion heat exchanger device - basically any other liquid, for example water, can also be used as the liquid.

• Es wird für das vorliegende Ausführungsbeispiel davon ausgegangen, dass die Druckgasenergiewandlungs-Wärmetauscher-Einrichtung 60 senkrechtstehend montiert ist, die fünfte Flüssigkeitsleitung 81 sich also, ausgehend von dem sechsten Hohlzylinder 66, nach oben erstreckt und der achte Hohlzylinder 68 - oben verschraubt mit dem fünften Kolben 69 und unten verschraubt mit dem sechsten Kolben 70 - sich am unteren Totpunkt befindet. Dabei liegt der fünfte Kolben 69 an dem ersten Mittelteil 64 und an dem zweiten Mittelteil 65 an, und der sechste Kolben 70 liegt an der zehnten Stirnwand 63 an. Die sechste Flüssigkeitsleitung 82 ist an ihrem von dem siebenten Hohlzylinder 67 abgewandten Ende an einen in den 8, 9 und 10 nicht dargestellten Öltank angeschlossen. Die zur zehnten Flüssigkeitsleitung 97 gehörende Ventileinrichtung ist geöffnet und ermöglicht daher bei einem Hub des fünften Kolbens 69 nach oben ein Ansaugen von Öl aus dem Öltank in die elfte Kammer 73, und zwar über die sechste Flüssigkeitsleitung 82, den siebenten Hohlzylinder 67, den sechsten Hohlzylinder 66 und die fünfte Flüssigkeitsleitung 81. Die zur neunten Flüssigkeitsleitung 96 gehörende Ventileinrichtung ist geschlossen, und auch die zur siebenten Flüssigkeitsleitung 94 gehörende Ventileinrichtung ist geschlossen. Die zur achten Flüssigkeitsleitung 95 gehörende Ventileinrichtung ist geöffnet.

That in the 8th , 9 and 10 The embodiment shown of the compressed gas energy conversion heat exchanger device 60 works as follows:

• For the present exemplary embodiment, it is assumed that the compressed gas energy conversion heat exchanger device 60 is mounted vertically, i.e. the fifth liquid line 81, starting from the sixth hollow cylinder 66, extends upwards and the eighth hollow cylinder 68 - screwed to the fifth piston at the top 69 and screwed down to the sixth piston 70 - is at bottom dead center. The fifth piston 69 rests against the first center part 64 and the second center part 65 , and the sixth piston 70 rests against the tenth end wall 63 . The sixth liquid line 82 is at its end facing away from the seventh hollow cylinder 67 to a in the 8th , 9 and 10 not shown oil tank connected. The valve device belonging to the tenth fluid line 97 is open and therefore allows oil to be drawn in from the oil tank into the eleventh chamber 73 when the fifth piston 69 strokes upwards, specifically via the sixth fluid line 82, the seventh hollow cylinder 67, the sixth hollow cylinder 66 and the fifth liquid line 81. The valve device belonging to the ninth liquid line 96 is closed, and the valve device belonging to the seventh liquid line 94 is also closed. The valve device belonging to the eighth liquid line 95 is open.

In the present exemplary embodiment of the compressed gas energy conversion heat exchanger device 60, the eighth liquid line 95 leads to a motor which is driven by the oil which is pressed up through the eighth liquid line 95 towards the sixth piston 70 when it strokes. The oil pushed through the eighth fluid line 95 is therefore used, generally speaking, to perform work. In the case of the controllable drive device according to the invention with the compressed gas energy conversion heat exchanger device 60, the motor or oil motor driven by the oil flow specifically drives a land vehicle, water vehicle and/or aircraft.

The valve device belonging to the thirteenth gas connection device 98 is opened so that the air in the ninth chamber 71 can escape from the ninth chamber 71 via the thirteenth gas connection device 98 when the fifth piston 69 lifts upwards. In this case, the ninth chamber 71 is simply vented to the outside atmosphere, or the partially expanded air pressed out of the ninth chamber 71 is routed to the next consumer, with the next consumer just mentioned also being equipped, for example, again with a pressurized gas energy conversion heat exchanger device 60, 146 according to the invention or, for example, an exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 to be described further below or, for example, an exemplary embodiment of a compressed gas energy conversion device according to the invention to be described further below.

The tenth gas line 78 is also open for passing on air to the next consumer, which, as already mentioned, for example also can again be a compressed gas energy conversion heat exchanger device 60, 146 or, for example, an exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 to be described further below or, for example, an exemplary embodiment of a compressed gas energy conversion device to be described further below.

Via the ninth gas line 77, compressed air from a cylinder of a preliminary stage or a similar device, for example from an embodiment of the hydraulic piston device 1 or from an embodiment of the compressed gas energy conversion device 50, is conducted into the thirteenth chamber 75 in an optimized quantity and pressure. The air expands there and pushes the eighth hollow cylinder 68 with the fifth piston 69 and the sixth piston 70 upwards. At the same time, air with the same or different pressure can be fed into the tenth chamber 72 via the fourteenth gas connection device 99 . This air acts on the sixth piston 70 and increases the force with which the eighth hollow cylinder 68 is pushed upwards. Meanwhile, the twelfth chamber 74 was filled with warm oil. During this "work cycle" with the piston stroke direction upwards, the eleventh chamber 73 is again sucked full of warm oil via the tenth liquid line 97 from the oil tank. This oil is further sucked via the sixth liquid line 82 through the seventh hollow cylinder 67 , through the second central part 65 and through the sixth hollow cylinder 66 into the fifth liquid line 81 . At the same time, the oil is pressed out of the twelfth chamber 74 via the eighth fluid line 95 to the consumer or to the engine driven by oil. This process lasts until the fifth piston 69 reaches the ninth end wall 62, ie top dead center.

As soon as the fifth piston 69 has reached the ninth end wall 62, i.e. top dead center, the valve device belonging to the ninth liquid line 96 opens, the valve device belonging to the tenth liquid line 97 closes, the valve device belonging to the seventh liquid line 94 opens and closes the valve device belonging to the eighth fluid line 95 associated valve means.

Now the "working cycle" begins with the piston stroke direction downwards, which is basically a mirror image of the "working cycle" described in the penultimate paragraph with the piston stroke direction upwards: Compressed air is now supplied via the thirteenth gas connection device 98 and tenth gas line 78. The ninth gas line 77 opens to the next consumer. The fourteenth gas connection device 99 vents or goes to the next consumer. Oil is now forced through the seventh fluid line 94 to the oil driven motor due to the downward movement of the fifth piston 69 .

Based on 11 a further functional example of the operation of a compressed gas energy conversion heat exchanger device 60 is now described, which can be part of the compressed gas-based energy conversion device of the controllable drive device according to the invention or even the compressed gas-based energy conversion device of the controllable drive device according to the invention. 11 shows schematically and not to scale the longitudinal section through the exemplary embodiment of the compressed gas energy conversion heat exchanger device from FIG 8th , where in 11 additionally supply lines for gas are shown.

Also in the example of 11 Air is used as the gas and oil as the liquid, and the expanding air is heated by the warm oil to prevent icing.

Compressed air is fed into the thirteenth chamber 75 via a first compressed gas supply line 100 and the ninth gas line 77 . The quantity, resulting from the pressure of the compressed air introduced, is measured in such a way that after the last expansion stage has been reached, the pressure is reached that is necessary to serve the next consumer or to ensure that the desired air temperature is reached.

The eighth hollow cylinder 68 with the sixth piston 70 and the fifth piston 69 is pushed upwards. In the process, oil is routed from the twelfth chamber 74 via the eighth fluid line 95 to the engine/consumer. At the same time, the eleventh chamber 73 is filled with oil from the oil tank via the tenth liquid line 97. The thirteenth gas connection device 98 is opened from the ninth chamber 71 to the consumer via a first exhaust air line 104.

A second compressed gas supply line 101 is closed, an eleventh gas line 102 is closed and a twelfth gas line 103 is open.

Air flows from the fourteenth chamber 76 via the tenth gas line 78 via the twelfth gas line 103 and the fourteenth gas connection device 99 into the tenth chamber 72. Pressure equalization occurs in the fourteenth chamber 76 and the tenth chamber 72. A second exhaust air line 105 is closed.

When the eighth hollow cylinder 68 with its fifth piston 69 and the sixth piston 70 has reached top dead center, the first compressed gas supply line 100 and the first exhaust air line 104 close and the eleventh gas line 102 opens.

Compressed air now flows from the thirteenth chamber 75 into the ninth chamber 71 and equalizes the pressure.

The twelfth gas line 103 now closes and the second exhaust air line 105 and the second compressed gas supply line 101 open.

Compressed air is now passed into the fourteenth chamber 76 via the second compressed gas supply line 101 and the tenth gas line 78 . This results in the eighth hollow cylinder 68 being pressed downwards with the fifth piston 69 and the sixth piston 70 . In the process, oil is routed from the eleventh chamber 73 via the seventh fluid line 94 to the engine/consumer. At the same time, the twelfth chamber 74 is sucked full of oil from the oil tank via the ninth liquid line 96.

With this circuit, the "energy yield" from the displaced oil is very low in the sense that the kinetic energy to be obtained via the displaced oil for any conversion into electrical energy or into kinetic energy of a motor or oil motor is very low, because the circuit works with it Dynamic pressure and the movement of the displaced oil is correspondingly slow.

16 shows a further exemplary embodiment of a compressed gas energy conversion heat exchanger device 146, which can be part of the compressed gas-based energy conversion device of the controllable drive device according to the invention or even the compressed gas-based energy conversion device of the controllable drive device according to the invention and which compared to the above with reference to 8th until 11 described embodiment of the compressed gas energy conversion heat exchanger device 60 is provided with some additional components that allow a certain control of the operation of the compressed gas energy conversion heat exchanger device 146 in thermal terms. The background to this additional technical measure is that with regard to ambient temperatures that change over time at the place of use or operation of a compressed gas energy conversion heat exchanger device and/or with regard to operating requirements that may change over time in the technical and technological environment of a compressed gas energy conversion heat exchanger device be useful during the use of the compressed gas energy conversion heat exchanger device and sometimes may even be absolutely necessary to control the temperature of the exhaust air or the exhaust gas in a targeted manner. While, for example, in the depths of winter when the outside temperatures are very cold, it can be advantageous to have the highest possible exhaust air temperature, so that the compressed gas energy conversion heat exchanger device does not partially freeze and thus perhaps even the exhaust air for heating some rooms - for example the interior of a passenger car or the driver's cab of a truck or the driver's cab of a railway locomotive or rooms in a ship or the passenger cabin in an airplane, helicopter or airship - can be used, the same high exhaust air temperature in midsummer with high outside temperatures can be useless or even counterproductive and completely undesirable. At least the danger of a partial freezing of the compressed gas energy conversion heat exchanger device is lower in midsummer than in the dead of winter, and it can therefore, when considering the overall system in which the compressed gas energy conversion heat exchanger device is used as part of an embodiment of the controllable drive device according to the invention, under From an energetic point of view, it can be advantageous to leave more heat in the oil in summer for further use there, while in winter it may well be necessary to transfer more heat from the oil to the air or to the other gas that may be used. If the exhaust air temperature is too high, an unnecessarily large amount of energy in the form of heat is withdrawn from the oil or the liquid as a heat transfer medium. Accordingly, the provision of a thermal control capability is advantageous and desirable. For this purpose, the in 16 illustrated further embodiment of the compressed gas energy conversion heat exchanger device 146, in addition to in 8th components already shown, the following is provided: a thirteenth liquid line 147, one end of which is connected to the sixth liquid line 82 and set up in such a way that this thirteenth liquid line 147 is able to convey liquid from the sixth liquid line 82 to the ninth liquid line 96 and to the tenth liquid line 97 without the liquid passing through the seventh hollow cylinder 67, the liquid conduction device 85 and the sixth hollow cylinder 66 on its way to the ninth liquid line 96 and the tenth liquid line 97, with the connection of the thirteenth liquid line 147 to the sixth liquid line 82 is provided with a first flow control valve device 148, which is controllable and designed in such a way that it can be controlled by means of the first flow control valve device 148 which proportion of one of the liquid flow arriving at the liquid tank via the sixth liquid line 82 at the first flow control valve device 148 into the seventh hollow cylinder 67 and which portion is routed into the thirteenth liquid line 147, with the possibility of controlling the first flow control valve device 148 at least including the possibility of controlling whether the The liquid flow arriving through the sixth liquid line 82 is conducted completely into the seventh hollow cylinder 67 or completely into the thirteenth liquid line 147 . That's in 16 The special exemplary embodiment illustrated of the compressed gas energy conversion heat exchanger device 146 according to the invention is specially set up in such a way that the thirteenth liquid line 147 opens into the fifth liquid line 81 with its end remote from the first flow control valve device 148 .

The first flow control valve assembly 148 may include a thermostatic valve, for example.

Provision is particularly preferably made for the first flow control valve device 148 to be set up in such a way that, in addition to the already mentioned control option for the complete introduction of the liquid flow arriving at it via the sixth liquid line 82, it can also be controlled either into the seventh hollow cylinder 67 or into the thirteenth liquid line 147 that it can divide the liquid flow arriving at it via the sixth liquid line 82, so that part of the liquid reaches the seventh hollow cylinder 67 and at the same time another part of the liquid gets into the thirteenth liquid line 147, with an associated flow splitting ratio being stepless and/or can be controlled in stages. In this case, the first flow control valve device 148 controls the liquid flow as a function of a gas and/or liquid temperature measurement. If the control just mentioned is to be based on a gas temperature measurement, this can in principle be carried out at any point at which the gas flows. A temperature measurement is preferred where the gas has already “worked”, i.e. has already expanded.

Advantageously, this measurement or measurements just mentioned is or are set up, for example, in such a way that, if a gas temperature measurement is carried out to control the first flow control valve device 148, this gas temperature measurement is carried out at least in a region of the ninth gas line 77 which is further away from the second central part 65 than from the eleventh end wall 79, and that, if a liquid temperature measurement is taken to control the first flow control valve device 148, this liquid temperature measurement takes place at least either in the fifth liquid line 81 or in an area of the sixth hollow cylinder 66, which is further from the second central part 65 is spaced apart than from the eleventh end wall 79.

The control of the first flow control valve device 148 can take place, for example, mechanically and/or electromechanically and/or magnetically and/or electromagnetically and/or electronically and/or optically and/or electro-optically and/or in any other technically suitable manner.

The control of the 16 The special exemplary embodiment of the compressed gas energy conversion heat exchanger device 146 illustrated in thermal terms can take place as follows, for example: First, the first flow control valve device 148, which can be a thermostatic valve, is set in such a way that all oil arriving at that thermostatic valve via the sixth liquid line 82 is exactly as in the embodiment of 8th permanently provided and in that embodiment due to the technical structure provided there otherwise not possible, is directed into the seventh hollow cylinder 67 and from there exactly as it is above with reference to 8th was described, moved on. If a measurement of the temperature of the exhaust air, which takes place in the area of the ninth gas line 77 where the ninth gas line 77 penetrates the eleventh end wall 79, determines that the temperature of the exhaust air is higher than is necessary or permitted based on any previously defined conditions, the thermostat valve mentioned in the previous sentence is controlled mechanically or electromechanically in such a way that it completely or partially interrupts the oil supply from the sixth liquid line 82 to the seventh hollow cylinder 67 and instead the oil arriving from the sixth liquid line 82 is completely or partially fed into the thirteenth liquid line 147 and from there then into the ninth liquid line 96 and the tenth liquid line 97 leads. The oil as such reaches the ninth liquid line 96 and the tenth liquid line 97 both in the embodiment of FIG 8th as well as in the embodiment of FIG 16 always. While in the embodiment of FIG 8th however, there is permanently only one way for the oil to go there, in the embodiment of FIG 16 two different paths for the oil to the ninth fluid line 96 and the tenth fluid line 97, it being possible to control which path the oil should take or how the oil is distributed in terms of quantity over the two possible paths. The less oil in the seventh hollow cylinder 67 and from there via the liquid ducting device 85 to the sixth hollow cylinder 66, the less heat can be transferred there - i.e. in the "piston interior" - from the oil to the air flowing through the tenth gas line 78 and the ninth gas line 77. If the oil flow is completely interrupted in the way just mentioned, this accordingly results in an interruption in the supply of heat to the air flowing through the tenth gas line 78 and the ninth gas line 77 . Accordingly, the temperature of the exhaust air drops when - as already described in this paragraph a little further above - the aforementioned thermostatic valve - i.e. the first flow control valve device 148 - completely or partially interrupts the oil supply from the sixth liquid line 82 into the seventh hollow cylinder 67 and instead oil arriving from the sixth liquid line 82 leads in full or in part into the thirteenth liquid line 147. The exhaust air is then heated less, is discharged "cooler" into the environment or used for other purposes. If at some point later the exhaust air temperature is considered to be too low, the position of the aforementioned thermostatic valve - i.e. the first flow control valve device 148 - can then be changed in such a way that more or even all of the oil that flows via the sixth liquid line 82 at the first flow control valve device 148 arrives, passed into the seventh hollow cylinder 67 and in this way the air flowing in the tenth gas line 78 and in the ninth gas line 77 is supplied with heat or more heat.

12 shows a first exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary device 137, which is preferably a compressed gas energy conversion heat exchanger device, for example the one above with reference to FIG 8th until 11 described embodiment of the compressed gas energy conversion heat exchanger device 60 or above with reference to the 16 described further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146, can be preceded as a preliminary stage and then as such a group of two forms an exemplary embodiment of a compressed gas energy conversion device.

13 shows a second of a compressed gas energy conversion heat exchanger device preliminary device 138 according to the invention, which is also preferably a compressed gas energy conversion heat exchanger device, for example the one above with reference to FIG 8th until 11 described embodiment of the compressed gas energy conversion heat exchanger device 60 or above with reference to the 16 described further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146, can be preceded as a preliminary stage and then as such a group of two forms a further exemplary embodiment of a compressed gas energy conversion device.

17 shows a third exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary device 149, which is also preferably a compressed gas energy conversion heat exchanger device, for example the one above with reference to FIG 8th until 11 described embodiment of the compressed gas energy conversion heat exchanger device 60 or above with reference to the 16 described further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146, can be preceded as a preliminary stage and then as such a group of two forms a further exemplary embodiment of a compressed gas energy conversion device.

As was already readily apparent above in the description of the exemplary embodiment of the compressed gas energy conversion heat exchanger device 60 and in the description of the further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146 and as in the following description of the three exemplary embodiments of a compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 and in the following description of various exemplary embodiments of a compressed gas energy conversion device, all of these exemplary embodiments are exemplary embodiments that use the principle of the double-acting hydraulic-pneumatic tandem cylinder in their basic mode of operation. In the context of the present invention relating to a controllable drive device for a land vehicle, water vehicle and/or aircraft based on a compressed gas-based energy conversion device which uses the principle of the double-acting hydraulic-pneumatic tandem cylinder, the above-described exemplary embodiment of the compressed gas energy conversion device is or are Heat exchanger device 60 and/or the further exemplary embodiment of the compressed gas energy conversion heat exchanger device 146 described above and/or the first exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 137 described below and/or the second exemplary embodiment of the compressed gas energy conversion heat exchanger device described below - Pre-stage device 138 and / or the third embodiment described below Compressed gas energy conversion heat exchanger device preliminary device 149 and/or any exemplary embodiment of the compressed gas energy conversion device described below is part of the compressed gas-based energy conversion device of an exemplary embodiment of the controllable drive device according to the invention or even the compressed gas-based energy conversion device of an exemplary embodiment of the controllable drive device according to the invention per se. There is therefore always a control device of one type or another described above, which is set up and designed in such a way that a driver and/or an automatic driver of the land vehicle, watercraft and/or aircraft can use the control device to generate a driving force of the engine can control. In a variant of the controllable drive device according to the invention, the named control device is set up and designed in such a way that the driving force of the motor is controlled in that the control device can or can control a valve or a plurality of valves in the named compressed-gas-based energy conversion device during ongoing operation of the motor It is possible that an active supply of compressed gas from the outside into a chamber to be pressurized with compressed gas during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder can already be ended before a piston that delimits the said chamber and is moved by the compressed gas hits a stop that mechanically limits its movement path arrives, said piston after switching off the active pressure gas supply from the outside then only under the influence of the pressure gas already filled into the chamber in the direction of the movement path of the piston mecha nically limiting stop moves. In another variant of the controllable drive device according to the invention, the named control device is set up and designed in such a way that the driving force of the motor is controlled by the control device being able to control one or more valves in the named compressed gas-based energy conversion device during ongoing operation of the motor or can that a strength of an active supply of compressed gas from the outside in a working cycle of the double-acting hydraulic-pneumatic tandem cylinder with compressed gas to be acted upon chamber in a certain pressure range can be adjusted continuously and / or in stages changeable.

It is important to mention at this point that each individual exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 described below can be operatively connected upstream of a compressed gas energy conversion heat exchanger device 60, 146 as described above, which then becomes a compressed gas energy conversion device leads, as will be described further below, but that it is just as possible to use each individual exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 described below on its own, i.e. without a downstream compressed gas energy conversion heat exchanger device 60, 146 to operate. In the latter case, the compressed gas energy conversion heat exchanger device preliminary device 137, 138, 149 as such forms part of the compressed gas-based energy conversion device of an exemplary embodiment of the controllable drive device according to the invention, or the compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 can as such alone even represent the compressed gas-based energy conversion device of an embodiment of the controllable drive device according to the invention.

This in 12 The illustrated first exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary device 137 has the following: a ninth hollow cylinder 106 which has a thirteenth end wall 107 at its one end and a fourteenth end wall 108 at its other end; a third central part 112, which is arranged centrally in relation to the longitudinal direction of the ninth hollow cylinder 106 and which is fastened to the inner wall inside the ninth hollow cylinder 106, extends in its longitudinal position over the entire circumference of the inner wall of the ninth hollow cylinder 106 and thus forms a middle wall oriented parallel to the thirteenth end wall 107 and the fourteenth end wall 108, but has a through hole radially in the middle; a second piston rod 109 which extends through the aforesaid hole and is reciprocally movable in its longitudinal direction; a seventh piston 110 fixed to one end of the second piston rod 109, which nestles against the inner wall of the ninth hollow cylinder 106 and hydraulically-pneumatically seals the space between the third central part 112 and the thirteenth end wall 107 into a fifteenth chamber 113 and a seventeenth chamber 115 each of variable volume, the seventeenth chamber 115 adjoining the third central part 112 and the fifteenth chamber 113 adjoining the thirteenth end wall 107 and the seventeenth chamber 115 is intended for holding liquid and the fifteenth chamber 113 for holding gas; an eighth piston 111 fixed on the other end of the second piston rod 109 and adhering to the inner wall of the ninth hollow cylinder 106 and divides the space between the third center part 112 and the fourteenth end wall 108 in a hydraulic-pneumatically sealing manner into a sixteenth chamber 114 and an eighteenth chamber 116, each with a variable volume, with the eighteenth chamber 116 adjoining the third center part 112 and the sixteenth chamber 114 adjoins the fourteenth end wall 108 and the eighteenth chamber 116 is provided for holding liquid and the sixteenth chamber 114 for holding gas; a fifteenth gas connection device 117 provided with an associated valve device, through which, depending on the valve position, gas flows from outside the compressed gas energy conversion heat exchanger device preliminary stage device 137 into the fifteenth chamber 113 or from the fifteenth chamber 113 and thus out of the compressed gas energy conversion heat exchanger device preliminary stage device 137 can flow out, the fifteenth gas connection means 117 being positioned at or near the thirteenth end wall 107; a sixteenth gas connection device 118 provided with an associated valve device, through which, depending on the valve position, gas flows from outside the compressed gas energy conversion heat exchanger device preliminary stage device 137 into the sixteenth chamber 114 or from the sixteenth chamber 114 and thus out of the compressed gas energy conversion heat exchanger device preliminary stage device 137 can flow out, wherein the sixteenth gas connection means 118 is positioned at or near the fourteenth end wall 108; a fifth fluid port means 121 provided with associated valving means for introducing fluid into the seventeenth chamber 115 from outside the compressed gas energy conversion heat exchanger means pre-stage means 137, the fifth fluid port means 121 being positioned proximate the third center portion 112; a sixth fluid port means 122 provided with associated valving means for introducing fluid from outside the compressed gas energy conversion heat exchanger means precursor means 137 into the eighteenth chamber 116, the sixth fluid port means 122 being positioned proximate the third center portion 112; a seventh fluid port means 119 provided with associated valve means for leading fluid outwardly of the compressed gas energy conversion heat exchanger means precursor means 137 out of the seventeenth chamber 115, the seventh fluid port means 119 being positioned near the third center portion 112, and one with associated valve means provided eighth fluid port means 120 for leading fluid out of the compressed gas energy conversion heat exchanger means precursor means 137 out of the eighteenth chamber 116, the eighth fluid port means 120 being positioned near the third middle part 112.

As in the case of the hydraulic piston device 1 described in detail above, as in the case of the compressed gas energy conversion device 50 also described in detail above and as in the case of the compressed gas energy conversion heat exchanger device 60, 146 also already described in detail above, it is of course also possible in the case of the compressed gas energy conversion heat exchanger device preliminary stage device 137 , 138, 149 air can be used as gas, for example. However, it is also just as possible with the compressed gas energy conversion heat exchanger device preliminary device 137, 138, 149 that instead of or together with air, any other gas, for example biogas and/or methane and/or any hydrocarbon gas and/or a A mixture of hydrocarbon gases and/or a mixture of air and one or more hydrocarbon gases can be used in the compressed gas energy conversion heat exchanger device precursor device 137, 138, 149. Oil is preferably used as the liquid, but in principle any other liquid, for example water, can also be used as the liquid in the compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149. If the compressed gas energy conversion heat exchanger device preliminary device 137, 138, 149 is to be used as an operative preliminary stage for a compressed gas energy conversion heat exchanger device 60, 146, it naturally makes sense to coordinate the type of liquid used and in particular the type of gas used to the circumstances of the respective specific compressed gas energy conversion heat exchanger device 60, 146 for which the respective specific compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 is to be switched to serve as a preliminary stage.

• Es befindet sich anfänglich in der achtzehnten Kammer 116 Öl und in der fünfzehnten Kammer 113 Luft. Die zu der fünfzehnten Gasanschlusseinrichtung 117 gehörende Ventileinrichtung ist geöffnet derart, dass Luft aus der fünfzehnten Kammer 113 über die fünfzehnte Gasanschlusseinrichtung 117 entweichen kann. Die zu der sechzehnten Gasanschlusseinrichtung 118 gehörende Ventileinrichtung ist geöffnet derart, dass Druckluft durch die sechzehnte Gasanschlusseinrichtung 118 in die sechzehnte Kammer 114 hineingeführt werden kann. Die zu der sechsten Flüssigkeitsanschlusseinrichtung 122 gehörende Ventileinrichtung ist geschlossen. Die zu der achten Flüssigkeitsanschlusseinrichtung 120 gehörende Ventileinrichtung ist geöffnet. Die zu der fünften Flüssigkeitsanschlusseinrichtung 121 gehörende Ventileinrichtung ist geöffnet, und die zu der siebenten Flüssigkeitsanschlusseinrichtung 119 gehörende Ventileinrichtung ist geschlossen.

If it is assumed that in the exemplary embodiments of the compressed gas energy conversion heat exchanger device preliminary stage device 137, 138, 149 to be described here, air is used as the gas and oil is used as the liquid and that the first exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 137 to be described here as in 12 shown with the ninth hollow cylinder 106 standing vertically and the fourteenth end wall 108 at the bottom and the thirteenth end wall 107 at the top and the second piston rod 109 with the eighth piston 111 fixed on it and the seventh piston 110 fixed on it initially in its bottom dead center position, this first embodiment of the compressed gas energy conversion heat exchanger device pre-stage device 137 functions as follows:

• There is initially oil in the eighteenth chamber 116 and air in the fifteenth chamber 113 . The valve device belonging to the fifteenth gas connection device 117 is open in such a way that air can escape from the fifteenth chamber 113 via the fifteenth gas connection device 117 . The valve device belonging to the sixteenth gas connection device 118 is open in such a way that compressed air can be fed through the sixteenth gas connection device 118 into the sixteenth chamber 114 . The valve device belonging to the sixth liquid connection device 122 is closed. The valve device belonging to the eighth fluid connection device 120 is open. The valve device belonging to the fifth liquid connection device 121 is open, and the valve device belonging to the seventh liquid connection device 119 is closed.

Compressed air is now introduced into the sixteenth chamber 114 through the sixteenth gas connection device 118 , which causes the second piston rod 109 together with the seventh piston 110 and the eighth piston 111 to be raised. Accordingly, the air from the fifteenth chamber 113 is pushed out through the fifteenth gas port 117, the oil from the eighteenth chamber 116 is pushed out through the eighth fluid port 120, and oil is sucked into the seventeenth chamber 115 through the fifth fluid port 121. Although the compressed air expanded into the sixteenth chamber 114 cools down during expansion, heat exchange takes place through the eighth piston 111 with the oil in the eighteenth chamber 116, which is usually warm or at least has room temperature, so that on this In any case, the temperature drop in the air during relaxation is mitigated.

As soon as the second piston rod 109 with the eighth piston 111 fixed on it and the seventh piston 110 fixed on it has reached its top dead center, the valve device belonging to the fifteenth gas connection device 117 is switched over in such a way that compressed air enters the fifteenth chamber 113 through the fifteenth Gas connection device 117 can be introduced. The valve device belonging to the sixteenth gas connection device 118 is switched in such a way that the air can be guided out of the sixteenth chamber 114 through the sixteenth gas connection device 118 . The valve device belonging to the sixth liquid connection device 122 is opened. The valve device belonging to the eighth liquid connection device 120 is closed. The valve device belonging to the fifth liquid connection device 121 is closed and the valve device belonging to the seventh liquid connection device 119 is opened.

Compressed air is now introduced into the fifteenth chamber 113 through the fifteenth gas connection device 117, which leads to a downward stroke of the second piston rod 109 together with the seventh piston 110 and the eighth piston 111. Accordingly, the air in the sixteenth chamber 114 is pushed out through the sixteenth gas port 118, the oil in the seventeenth chamber 115 is pushed out through the seventh fluid port 119, and the sixth fluid port 122 sucks oil into the eighteenth chamber 116. Although the compressed air expanded into the fifteenth chamber 113 cools down during expansion, heat is exchanged through the seventh piston 110 with the oil in the seventeenth chamber 115, which is usually warm or at least has room temperature, so that on this In any case, the temperature drop in the air during relaxation is mitigated.

As soon as the second piston rod 109 with the eighth piston 111 fixed on it and the seventh piston 110 fixed on it has reached its bottom dead center again, the valve device belonging to the sixteenth gas connection device 118 is switched over again in such a way that compressed air flows through the sixteenth gas connection device 118 in the sixteenth chamber 114 can be introduced. The valve device belonging to the fifteenth gas connection device 117 is switched in such a way that air can escape from the fifteenth chamber 113 via the fifteenth gas connection device 117 . The valve device belonging to the sixth liquid connection device 122 is closed.

The valve device belonging to the eighth liquid connection device 120 is opened. The valve device belonging to the fifth liquid connection device 121 is opened, and the valve device belonging to the seventh liquid connection device 119 is closed.

Compressed air is then admitted again through the sixteenth gas connection device 118 into the sixteenth chamber 114, and the already described above stroke stroke of the second piston rod 109 together with the seventh piston 110 and the eighth piston 111 begins again.

This in 13 shown second embodiment of the compressed gas energy conversion heat exchanger device preliminary device 138 differs in some details from the above-described first embodiment of the compressed gas energy conversion heat exchanger device preliminary device 137, but the same or essentially the same parts are in the 12 and 13 each provided with the same reference numerals.

This in 13 illustrated second embodiment of the compressed gas energy conversion heat exchanger device preliminary device 138 has compared to in 12 The illustrated first exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 137 also has a tenth hollow cylinder 124, which is arranged inside the ninth hollow cylinder 106, extends through the opening in the third central part 112 and at one end extends through an opening in the thirteenth end wall 107 and at its other end through an opening in the fourteenth end wall 108 through over the thirteenth end wall 107 and over the fourteenth end wall 108, respectively. Another special feature of the second exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary device 138 is that the second piston rod is designed as a first piston tube 123, which encloses the tenth hollow cylinder 124, hydraulically-pneumatically seals against the tenth hollow cylinder 124 and is designed in this way is that it can slide back and forth on the tenth hollow cylinder 124 . Accordingly, of course, both the seventh piston 110 and the eighth piston 111 are each provided with a hole through which the tenth hollow cylinder 124 extends, and both the seventh piston 110 and the eighth piston 111 nestle against the hydraulic-pneumatic seal tenth hollow cylinder 124 and are designed in such a way that they can slide back and forth on the tenth hollow cylinder 124 together with the first piston tube 123 on which they are each fixed. Furthermore, as a special feature of the second embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 138, an eleventh liquid line 125 is provided, which for the purpose of liquid transport is connected to the fifth liquid connection device 121 as well as to the sixth liquid connection device 122 and to that end of the tenth hollow cylinder 124, which protrudes beyond the thirteenth end wall 107, is connected. Via a twelfth liquid line 126, which is connected to that end of the tenth hollow cylinder 124 which protrudes beyond the fourteenth end wall 108 for the purpose of transporting liquid, liquid, for example oil, can be pressed into the tenth hollow cylinder 124 and from there via the eleventh liquid line 125 both flow towards the fifth liquid connection device 121 and also to the sixth liquid connection device 122 .

From a comparison of 12 and 13 It becomes immediately and readily clear that - apart from the purely constructive differences presented - the second exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 138 functions in principle in the same way as the first exemplary embodiment of the compressed gas energy conversion heat exchanger device described in detail above in terms of its function. Pre-stage device 137. However, due to the oil flowing through the tenth hollow cylinder 124 in the second embodiment of the compressed gas energy conversion heat exchanger device pre-stage device 138, a larger and better arranged surface area is available for the heat exchange between the liquid and the gas, so that in the second Embodiment of the compressed gas energy conversion heat exchanger device precursor device 138 effectively takes place during operation a much better heat exchange than in the first embodiment of the Dr Compressed gas energy conversion heat exchanger device pre-stage device 137.

17 shows a third embodiment of a compressed gas energy conversion heat exchanger device preliminary device 149, which compared to the above with reference to the 13 described second embodiment of the compressed gas energy conversion heat exchanger device precursor device 138 is provided with some additional components that allow a certain control of the operation of the compressed gas energy conversion heat exchanger device precursor device 149 in thermal terms. The background to this additional technical measure is that with regard to ambient temperatures that change over time at the place of use or operating site of a compressed gas energy conversion heat exchanger device and/or with regard to operating requirements that may change over time in the technical and technological environment of a compressed gas energy conversion heat exchanger facility pre-stage facility may be useful, and sometimes possibly even essential, during the deployment of the compressed gas energy conversion heat exchanger facility pre-stage facility it may be necessary to specifically control the temperature of the exhaust air or exhaust gas. While, for example, in the depths of winter when outside temperatures are very cold, it can be quite advantageous to have the highest possible exhaust air temperature, so that the compressed gas energy conversion heat exchanger device preliminary stage does not partially freeze and thus perhaps even - if, for example, the compressed gas energy conversion heat exchanger device preliminary stage device is autonomous , ie is operated without a downstream compressed gas energy conversion heat exchanger device - the exhaust air for heating any premises - such as the interior of a passenger car or the driver's cab of a truck or the driver's cab of a railway locomotive or premises in a ship or the passenger cabin in an airplane, helicopter or airship - can be used, the same high exhaust air temperature in midsummer with high outside temperatures can be useless or even counterproductive and completely undesirable. At least the risk of partial freezing of the compressed gas energy conversion heat exchanger device preliminary device is lower in midsummer than in the dead of winter, and it can therefore be advantageous from an energetic point of view when considering the overall system in which the compressed gas energy conversion heat exchanger device preliminary stage device is used to leave more heat in the oil for further use in summer, while in winter it may well be necessary to transfer more heat from the oil to the air or to the other gas that may be used. If the exhaust air temperature is too high, an unnecessarily large amount of energy in the form of heat is withdrawn from the oil or the liquid as a heat transfer medium. Accordingly, the provision of a thermal control capability is advantageous and desirable. For this purpose, the in 17 illustrated third exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary device 149 in addition to the in 13 components already shown, the following is provided: a fourteenth liquid line 150, one end of which is connected to the twelfth liquid line 126 and set up in such a way that this fourteenth liquid line 150 is able to transfer liquid from the twelfth liquid line 126 to the fifth liquid connection device 121 and to the sixth liquid connection device 122 without the liquid passing through the tenth hollow cylinder 124 on its way to the fifth liquid connection device 121 and to the sixth liquid connection device 122, wherein the connection of the fourteenth liquid line 150 to the twelfth liquid line 126 is provided with a second flow control valve device 151, which can be controlled and is designed in such a way that it can be controlled by means of the second flow control valve device 151 which proportion of a liquid via the twelfth line 126 in the second flow control valve device 151 into the tenth hollow cylinder 124 and which portion is routed into the fourteenth liquid line 150, the ability of the second flow control valve device 151 to control at least the ability to control whether the liquid flow arriving at it via the twelfth liquid line 126 is completely fed into the tenth Hollow cylinder 124 or completely passed into the fourteenth liquid line 150. That's in 17 The illustrated third exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 149 is specially set up in such a way that here the fourteenth liquid line 150 opens into the eleventh liquid line 125 with its end remote from the second flow control valve device 151 .

The second flow control valve device 151 can have a thermostatic valve, for example.

Provision is particularly preferably made for the second flow control valve device 151 to be set up in such a way that, in addition to the already mentioned control option for the complete introduction of the liquid flow arriving at it via the twelfth liquid line 126, it can also be controlled either into the tenth hollow cylinder 124 or into the fourteenth liquid line 150 that it can split the liquid flow arriving at it via the twelfth liquid line 126, so that part of the liquid gets into the tenth hollow cylinder 124 and at the same time another part of the liquid gets into the fourteenth liquid line 150, with an associated flow splitting ratio being stepless and/or can be controlled in stages. In this case, the second flow control valve device 151 controls the liquid flow as a function of a gas and/or liquid temperature measurement. If the control just mentioned is to be based on a gas temperature measurement, this can in principle be carried out at any point at which the gas flows. A temperature measurement is preferred where the gas has already “worked”, i.e. has already expanded.

Advantageously, this measurement or measurements just mentioned is or are set up such that, if a gas temperature measurement is made to control the second flow control valve device 151, this gas temperature measurement is at least either in the range of the fifteenth gas connection device 117 or in the area of the sixteenth gas connection device 118 or in an area of the fifteenth chamber 113 which is further away from the third middle part 112 than from the thirteenth end wall 107, or in an area of the sixteenth chamber 114 which is further away from the third middle part 112 is spaced further away than from the fourteenth end wall 108, and that, if a liquid temperature measurement is taken to control the second flow control valve device 151, this liquid temperature measurement takes place at least either in the eleventh liquid line 125 or in an area of the tenth hollow cylinder 124, which extends from the third central part 112 is further spaced than from the thirteenth end wall 107.

The second flow control valve device 151 can be controlled, for example, mechanically and/or electromechanically and/or magnetically and/or electromagnetically and/or electronically and/or optically and/or electro-optically and/or in any other technically suitable manner.

The control of the 17 The illustrated third exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary stage device 149 from a thermal point of view can, for example, take place as follows: First, the second flow control valve device 151, which can be a thermostatic valve, is set in such a way that all oil arriving at that thermostatic valve via the twelfth liquid line 126 is exactly the same , as in the embodiment of FIG 13 permanently provided and in that embodiment due to the technical structure provided there otherwise not possible, is directed into the tenth hollow cylinder 124 and from there exactly as it is above with reference to 13 was described, moved on. If a measurement of the temperature of the exhaust air, which takes place in the area of the fifteenth gas connection device 117, determines that the temperature of the exhaust air is higher than is necessary or permitted due to any previously defined conditions, the thermostatic valve mentioned in the previous sentence becomes mechanical or electromechanical controlled so that it interrupts the oil supply from the twelfth liquid line 126 to the tenth hollow cylinder 124 in whole or in part and instead the oil arriving from the twelfth liquid line 126 flows in whole or in part to the fourteenth liquid line 150 and from there to the fifth liquid connection device 121 and leads to the sixth liquid connection device 122 . The oil as such reaches the fifth liquid connection device 121 and the sixth liquid connection device 122 both in the exemplary embodiment in FIG 13 as well as in the embodiment of FIG 17 always. While in the embodiment of FIG 13 however, there is permanently only one way for the oil to go there, in the embodiment of FIG 17 two different paths for the oil to the fifth fluid connection device 121 and the sixth fluid connection device 122, it being possible to control which path the oil should take or how the oil is distributed in terms of quantity over the two possible paths. The less oil flows into the tenth hollow cylinder 124 , the less heat can be transferred from the oil to the air in the sixteenth chamber 114 and in the fifteenth chamber 113 . If the flow of oil is completely interrupted in the way just mentioned, this accordingly results in an interruption in the supply of heat to the air located in the sixteenth chamber 114 and to the air in the fifteenth chamber 113 . The temperature of the exhaust air falls accordingly if - as already described in this paragraph a little further above - the aforementioned thermostatic valve - i.e. the second flow control valve device 151 - completely or partially interrupts the oil supply from the twelfth liquid line 126 into the tenth hollow cylinder 124 and instead oil arriving from the twelfth liquid line 126 leads in whole or in part into the fourteenth liquid line 150. The exhaust air is then heated less, is discharged "cooler" into the environment or used for other purposes. If at some point later the exhaust air temperature is considered to be too low, the position of the aforementioned thermostatic valve - i.e. the second flow control valve device 151 - can then be changed in such a way that more or even all of the oil that flows via the twelfth liquid line 126 at the second flow control valve device 151 arrives, passed into the tenth hollow cylinder 124 and in this way the air in the sixteenth chamber 114 and the air in the fifteenth chamber 113 is again supplied with heat or more heat.

With reference to the 14 and 15 exemplary embodiments of compressed gas energy conversion devices are described below, which are each part of the compressed gas-based energy conversion device of exemplary embodiments of the controllable drive device according to the invention for a land vehicle, water vehicle and/or aircraft or even the related compressed gas-based energy conversion device per se.

Such a compressed gas energy conversion device stands out from the compressed gas energy conversion devices known from the prior art gene in that it has at least one group of two, which has one of the above-described compressed gas energy conversion heat exchanger devices and one of the above-described compressed gas energy conversion heat exchanger device preliminary stages, which is operatively connected upstream of the said compressed gas energy conversion heat exchanger device as a preliminary stage. In this case, it is particularly preferred to provide two, three, four or more of the groups of two mentioned, these groups of two being combined and interconnected with one another.

Air, for example, can also be used as the gas in the compressed gas energy conversion device. But it is also just as possible that instead of or together with air, any other gas, for example biogas and/or methane and/or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of air and one or more Hydrocarbon gases can be used.

With regard to the liquid to be used, although oil is often used as the liquid in the compressed gas energy conversion device for purely economic reasons, the compressed gas energy conversion device can in principle also be operated with any other liquid, for example water.

The purpose of the compressed gas energy conversion device in its various exemplary embodiments is always to provide possible interconnections and combinations of energy conversion devices working with compressed gas to form a combined unit with the aim of expanding stored compressed air to atmospheric pressure as far as possible in order to avoid severe cooling or freezing and recover as much energy as possible. In all figures of the present application, all liquid connections or oil connections that are welded or otherwise fastened to the hollow cylinders or that are routed through channels in the central part are provided with non-return valves, so that the desired required liquid flow or oil flow can always be achieved without electrically or pneumatically controlled valves. oil flow is reached. If a chamber is sucked full, the valve to the motor / consumer closes due to the resulting vacuum and at the same time the valve to the liquid tank / liquid reservoir or oil tank / oil reservoir opens. Conversely, the opposite chamber is emptied / pressed out to the engine / consumer, whereby the resulting overpressure opens the corresponding valve and at the same time the valve to the liquid tank / liquid reservoir or oil tank / oil reservoir closes. Basically, this system works like a heart, with the check valves being the heart valves.

The basic structure of the compressed gas energy conversion device to be described here as part of exemplary embodiments of the controllable drive device according to the invention includes as a preliminary stage one of the above-described compressed gas energy conversion heat exchanger device preliminary stages, which the main unit, i.e. the compressed gas energy conversion heat exchanger device, so to speak, the compressed air precisely matched to pressure and quantity supplies. Optimally, one of the compressed gas energy conversion devices 50 described above is also connected upstream of this whole, although the latter is not absolutely necessary. The compressed air is adjusted as precisely as possible to the desired pressure in the compressed gas energy conversion device 50 or, if necessary, readjusted in the compressed gas energy conversion heat exchanger device by the piston rod or a piston being equipped with a displacement measuring system that allows, after a previously calculated distance, which the pistons have traveled to close the respective gas inlet valve in order to use the expansion of the compressed air. In principle, this is done in a very similar way to what has already been described above with regard to the work of the control device of the first variant of the drive device according to the invention 18 and 19 presented in a different context.

In the embodiment of the compressed gas energy conversion device of FIG 14 the first exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary device 137 is used, which has already been described above with reference to FIG 12 had been described. This first exemplary embodiment of the compressed gas energy conversion heat exchanger device preliminary device 137 consists of the ninth hollow cylinder 106 which is divided into two equal halves by the third central part 112 . The second piston rod 109, on the ends of which the seventh piston 110 and the eighth piston 111 are mounted, leads through this third central part 112. This creates four chambers. Between the thirteenth end wall 107 and the seventh piston 110, the fifteenth chamber 113 for air. Between the seventh piston 110 and the third middle part 112 the seventeenth chamber 115 for oil. Between the third middle part 112 and the eighth piston 111 the eighteenth chamber 116 for oil and between the eighth piston 111 and the fourteenth end wall 108 the sixteenth chamber 114 for air.

In order to improve the heat exchange function, the second piston rod 109 of the compressed gas energy conversion heat exchanger device preliminary device can be designed as a first piston tube 123 or can be replaced with the first piston tube 123, if necessary. The tenth hollow cylinder 124, through which oil can then be drawn in, and thus the fifteenth chamber 113 and the sixteenth chamber 114, in which air is also "heated" from the inside (cf. the in 13 shown second embodiment of the compressed gas energy conversion heat exchanger device preliminary device 138).

In the further description, however, for the sake of simplicity, it is generally assumed that the oil is sucked in via the fifth liquid connection device 121 and the sixth liquid connection device 122, without the special possibility of sucking in the oil via the twelfth liquid line 126, the tenth hollow cylinder 124 and the eleventh Liquid line 125 to mention.

In the ideal case, compressed air from the compressed air reservoir is now regulated to the desired pressure via the compressed gas energy conversion device 50 and is thus fed to the compressed gas energy conversion heat exchanger device, e.g. via the fifteenth gas connection device 117. The fifteenth chamber 113 is filled with compressed air, and the seventh piston 110, the second piston rod 109 and the eighth piston 111 pressed down. The sixteenth gas connection device 118 is open to the tenth gas line 78.

Meanwhile, the seventh liquid connection device 119, from which an oil pressure line leads to an oil motor, is open. The eighth liquid connection device 120 is closed. The fifth liquid connection device 121 is closed and the sixth liquid connection device 122 is open for the purpose of sucking in oil.

The compressed air supply to the sixteenth gas connection device 118 is of course closed. If the eighth piston 111 has reached the fourteenth end wall 108, the compressed air supply to the fifteenth gas connection device 117 closes at this point at the latest, and a connecting line opens from the fifteenth gas connection device 117 to the ninth gas line 77.

The compressed gas energy conversion heat exchanger device 60 now begins to operate as described above with reference to FIG 11 was described. Once this work cycle described has been completed, the connection between the sixteenth gas connection device 118 and the tenth gas line 78 is closed and the sixteenth gas connection device 118 is pressurized. The eighth piston 111 and the seventh piston 110 are now correspondingly pushed upwards until the seventh piston 110 has reached the thirteenth end wall 107 .

In this case, the seventh liquid connection device 119 is closed to the oil motor. The eighth liquid connection device 120 is open and connected to the oil motor via a pressure line. The fifth liquid connection device 121 is open for suction of oil, and the sixth liquid connection device 122 is closed.

The compressed air supply to the sixteenth gas connection device 118 is now closed and the connection to the tenth gas line 78 is opened. The rest of the process is then as above with reference to 11 described.

Of course, it is not absolutely necessary to interrupt the supply of compressed air when the seventh piston 110 and the eighth piston 111 reach their top or bottom dead centers. In particular when the available pressures are low, it can make sense to maintain the supply of compressed air until the compressed gas energy conversion heat exchanger device has also completed the desired work cycle in whole or in part.

The combination of the compressed gas energy conversion heat exchanger device preliminary device and the compressed gas energy conversion heat exchanger device as a group of two results in an exemplary embodiment of a compressed gas energy conversion device. The combination of these two aggregates, i.e. the compressed gas energy conversion heat exchanger device preliminary device and the compressed gas energy conversion heat exchanger device, and the associated valves is now referred to below as a "unit". It is possible to use the compressed gas energy conversion heat exchanger device or the compressed gas energy conversion heat exchanger device individually or jointly, or to connect an infinite number of units in series or in parallel.

In particular with reference to 15 and with simultaneous recourse to 14 is now such a further possible embodiment of the compressed gas energy conversion device Compressed gas energy conversion device described in which two units are interconnected. In the following, in the left half of the image of 15 seen unit referred to as "first unit", and the one in the right half of the image of 15 The unit to be seen is referred to as the "second unit".

It is assumed that both the seventh piston 110 and the eighth piston 111 are initially at top dead center in both units in the compressed gas energy conversion heat exchanger device preliminary stage device. In the respective compressed gas energy conversion heat exchanger device of the two units, the fifth piston 69 and the sixth piston 70 are each at bottom dead center.

The first compressed gas supply line 100 and the second compressed gas supply line 101 are subjected to gas pressure, e.g. from a reservoir via a pressure reducer or from a compressed gas energy conversion device 50 as described above. The gas pressure just mentioned is present in each of the two units at a total of four supply line valves, namely in each case at a first valve 128 of a first four-way valve block 127 and at a fifth valve 133 of a second four-way valve block 132. These four valves in total, viz the first valve 128 in the first unit, the first valve 128 in the second unit, the fifth valve 133 in the first unit and the fifth valve 133 in the second unit are initially closed.

Air, for example, can be used as the gas. But it is also just as possible that instead of or together with air, any other gas, for example biogas and/or methane and/or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of air and one or more Hydrocarbon gases can be used.

• Da nachfolgend der bereits eingeschwungene Zustand der Druckgasenergiewandlungsvorrichtung beschrieben werden soll, startet die erste Einheit mit Takt 1, während in der zweiten Einheit Takt 4 gestartet wird (genaueres zu Takt 4 siehe weiter unten). Dabei öffnet an dem ersten Vierfach-Ventilblock 127 der ersten Einheit das erste Ventil 128, während ein zweites Ventil 129, ein drittes Ventil 130 und ein viertes Ventil 131 geschlossen sind. Dementsprechend strömt daraufhin Druckgas durch eine dreizehnte Gasleitung 144 in die fünfzehnte Kammer 113 der ersten Einheit. Der siebente Kolben 110 und der achte Kolben 111 der ersten Einheit werden zum unteren Totpunkt gedrückt. Dabei wird Öl aus der siebzehnten Kammer 115 der ersten Einheit über die siebente Flüssigkeitsanschlusseinrichtung 119, von welcher eine Öldruckleitung zum Ölmotor führt, zum Ölmotor gedrückt.

This in 15 The illustrated exemplary embodiment of a compressed gas energy conversion device according to the invention functions as follows after the first start run, i.e. in the steady state:

• Since the already settled state of the compressed gas energy conversion device is to be described below, the first unit starts with cycle 1, while cycle 4 is started in the second unit (for more details on cycle 4 see below). The first valve 128 opens on the first four-way valve block 127 of the first unit, while a second valve 129, a third valve 130 and a fourth valve 131 are closed. Accordingly, pressurized gas then flows through a thirteenth gas line 144 into the fifteenth chamber 113 of the first unit. The seventh piston 110 and the eighth piston 111 of the first unit are pushed to bottom dead center. In the process, oil is pressed from the seventeenth chamber 115 of the first unit to the oil motor via the seventh liquid connection device 119, from which an oil pressure line leads to the oil motor.

In this case, the fifth fluid connection device 121 is closed. The sixth liquid connection device 122 is open, and the eighteenth chamber 116 of the first unit is sucked full of oil via the sixth liquid connection device 122 .

On the second four-valve block 132 of the first unit, the fifth valve 133 is closed, a sixth valve 134 and a seventh valve 135 are open, and an eighth valve 136 is closed. On the first quad valve block 127 of the second unit, the first valve 128 is closed and a second valve 129, a third valve 130 and a fourth valve 131 are open. On the second four-valve block 132 of the second unit, the fifth valve 133 is closed, a sixth valve 134 is open, a seventh valve 135 and an eighth valve 136 are closed.

Gas from the fifteenth chamber 113, from the thirteenth chamber 75 and from the tenth chamber 72 of the second unit can now escape via the fourth valve 131 of the first quadruple valve block 127 of the second unit into the atmosphere or to another consumer, e.g. a turbine or tube 174 with impeller 175 as above with reference to FIG 20 and 21 described, are supplied.

If the fifteenth chamber 113 of the first unit is completely filled with gas, the first valve 128 of the first unit closes and interrupts the supply of compressed air via the first compressed gas supply line 100.

Now bar 2 begins on the first unit, and at the same time bar 1 begins on the second unit. The second valve 129 of the first unit opens, the pressurized gas from the fifteenth chamber 113 of the first unit flows via the thirteenth gas line 144 and the fourteenth gas line 139 and the ninth gas line 77 into the thirteenth chamber 75 of the first unit. The fifth piston 69 and the sixth piston 70 in the first unit are pushed to the top dead center. In the process, oil is pressed out of the twelfth chamber 74 of the first unit via the eighth liquid line 95 to the oil motor. The ninth fluid line 96 is closed, and so is the seventh liquid line 94 to the oil motor is closed. The tenth liquid line 97 is open for sucking in oil, so that the eleventh chamber 73 of the first unit is saturated with oil via the tenth liquid line 97 . The seventh liquid line 94 to the oil motor is closed. At the time mentioned at the beginning of this paragraph, i.e. at the beginning of bar 2 on the first unit and the simultaneous beginning of bar 1 on the second unit, it must or can be assumed that in the sixteenth chamber 114 of the second unit and in the fourteenth chamber 76 of the second unit is gas present after partial expansion. This gas is supplied to the tenth chamber 72 of the first unit via a nineteenth gas line 145 and the fourteenth gas connection device 99 . The fifth valve 133 on the second four-way valve block 132 of the second unit is closed, the sixth valve 134 is open, the seventh valve 135 is open and the eighth valve 136 is closed.

Now bar 3 begins on the first unit, and at the same time bar 2 begins on the second unit. On the second four valve block 132 of the first unit, the fifth valve 133 opens and pressurized gas then flows through the eighteenth gas line 143 into the sixteenth chamber 114 of the first unit. The sixth valve 134 of the first unit is closed.

The sixth valve 134, the seventh valve 135 and the eighth valve 136 of the second unit are open, so that the tenth chamber 72 of the first unit and the ninth chamber 71 of the second unit can vent or their gas, for example, a tube 174 with impeller 175 , as above with reference to the 20 and 21 described, can be supplied or, for example, can be supplied to another consumer. The eighth piston 111 and the seventh piston 110 of the first unit are pushed to the top dead center. In the process, oil is pressed out of the eighteenth chamber 116 of the first unit via the eighth fluid connection device 120 and an oil pressure line connected to it to the oil motor.

The fifth liquid connection device 121 is open, so that the seventeenth chamber 115 of the first unit can soak up oil via the fifth liquid connection device 121 . The seventh liquid connection device 119 and the sixth liquid connection device 122 are closed.

At the beginning of cycle 2 of the second unit and cycle 3 of the first unit, the first quad valve block 127 of the first unit opens the third valve 130 and the still pressurized gas from the thirteenth chamber 75 of the first unit and the now through The gas displaced by the upward movement of the seventh piston 110 and the eighth piston 111 of the first unit - triggered by cycle 3 - now flows from the fifteenth chamber 113 of the first unit via a fifteenth gas line 142 to the fourteenth gas connection device 99 into the tenth chamber 72 of the second unit and there assists the movement of the fifth piston 69 and the sixth piston 70 to top dead center during stroke 2 of the second unit. When the compressed gas energy conversion heat exchanger device preliminary stage device of the first unit has completed stroke 3 with reaching the top dead center of the seventh piston 110 and the eighth piston 111, then stroke 4 begins in the first unit and stroke 3 in the second unit, i.e. at of the first unit opens the sixth valve 134 on the second four-way valve block 132, while the fifth valve 133, the seventh valve 135 and the eighth valve 136 are closed. As a result, compressed gas now flows from the sixteenth chamber 114 of the first unit via the sixteenth gas line 140 and via the tenth gas line 78 into the fourteenth chamber 76 of the first unit and the fifth piston 69 and the sixth piston 70 of the first unit are pressed to bottom dead center . In the process, oil is pressed out of the eleventh chamber 73 via the seventh liquid line 94 to the oil motor.

The tenth liquid line 97 is closed. The eighth liquid line 95 to the oil motor is also closed.

The ninth liquid line 96 is open, so that the twelfth chamber 74 of the first unit can soak up oil via this ninth liquid line 96 .

At the beginning of cycle 4 of the first unit and cycle 3 of the second unit, the first quad valve block 127 of the first unit opens the fourth valve 131 and the residual pressurized gas from the thirteenth chamber 75 of the first unit and the tenth chamber 72 of the second unit can e.g. vented to atmosphere or e.g. a tube 174 with impeller 175 as above with reference to FIG 20 and 21 described, supplied or supplied to another consumer.

Now the first unit begins again with cycle 1, and the second unit begins with cycle 4. The fourth valve 131 in the first four-way valve block 127 of the second unit is opened and so the gas from the thirteenth chamber 75 of the second unit and the gas released from the ninth chamber 71 of the first unit to the outside or put to further use. Furthermore, in the second four-valve block 132 of the first unit, the seventh valve 135 is opened, and a seventeenth Gas line 141 and the thirteenth gas connection device 98, the partially expanded compressed gas from the sixteenth chamber 114 and the fourteenth chamber 76 of the first unit is supplied to the ninth chamber 71 of the second unit and supports the movement of the fifth piston 69 and the sixth piston 70 of the second unit in the direction bottom dead center during cycle 4. When cycle 4 of the second unit is complete, i.e. cycle 1 begins again on the second unit and cycle 2 begins again on the first unit, the eighth valve 136 opens on the second four-way valve block 132 of the first unit and releases the residual pressure gas into the atmosphere or feeds it to the next consumer.

This process described in the previous paragraphs regarding the functioning of the compressed gas energy conversion device is now repeated constantly. The arrival of the pistons at the end points can be determined with a path measuring system, e.g. on the piston rods in the middle parts or with contact switches in the end walls or with non-contact buttons. These switches trigger the next valve switching.

The number of units can be expanded as desired and the scope of the compressed gas energy conversion device can thus be increased as desired.

In the above-described exemplary embodiments of the controllable drive device according to the invention with a compressed gas energy conversion device with only one group of two or with two groups of two or only one unit or two units, there is always an internal dynamic pressure which does not lead to any loss of performance as long as the "exhaust air" is supplied with further work, eg a buoyancy power plant or a turbine or a tube 174 with impeller 175, as above with reference to the 20 and 21 described. However, if the "exhaust air" is only to be used thermally (removal of heat), it is advisable to connect three, four, five or six units or groups of two in series in order to gain time and ensure that the "exhaust air" is blown off , before the next work cycle begins. If the oil motors, which are driven by the individual compressed gas energy conversion heat exchanger devices and by the individual compressed gas energy conversion heat exchanger device preliminary devices, are connected to one another by means of a continuous shaft, and if the intake quantities of the oil motors correspond to the displaced oil quantities of the individual compressed gas energy conversion heat exchanger Devices and the individual compressed gas energy conversion heat exchanger device preliminary devices are compatible, the processes or clocks of the individual units will always run smoothly and harmoniously, and the oil motors then act like a flow divider.

Reference List

1

hydraulic piston device

2

first hollow cylinder

3

first end wall

4

second end wall

5

second hollow cylinder

6

third end wall

7

fourth end wall

8th

third hollow cylinder

9

fifth end wall

10

sixth front wall

11

fourth hollow cylinder

12

seventh end wall

13

eighth end wall

14

piston rod

15

first piston

16

second piston

17

third piston

18

fourth piston

19

first chamber

20

second chamber

21

third chamber

22

fourth chamber

23

fifth chamber

24

sixth chamber

25

seventh chamber

26

eighth chamber

27

first liquid connection device

28

second liquid connection device

29

third liquid connection device

30

fourth liquid connection device

31

first gas connection device

32

second gas connection device

33

third gas connection device

34

fourth gas connection device

35

fifth gas connection device

36

first gas line

37

second gas line

38

sixth gas connection device

39

seventh gas connection device

40

eighth gas connection device

41

ninth gas connection device

42

tenth gas connection device

43

third gas line

44

fourth gas line

45

eleventh gas connection device

46

twelfth gas connection device

47

first liquid line

48

machine to be driven by flowing liquid

49

second liquid line

50

compressed gas energy conversion device

51

fifth gas line

52

first pressure control valve device, which regulates gas pressure and liquid pressure against each other

53

sixth gas line

54

third liquid line

55

seventh gas line

56

second pressure control valve device, which regulates gas pressure and liquid pressure against each other

57

eighth gas line

58

fourth liquid line

59

Consumer equipment using gas thermally and/or mechanically and/or chemically

60

Compressed gas energy conversion heat exchanger device

61

fifth hollow cylinder

62

ninth end wall

63

tenth end wall

64

first middle part

65

second middle part

66

sixth hollow cylinder

67

seventh hollow cylinder

68

eighth hollow cylinder

69

fifth piston

70

sixth piston

71

ninth chamber

72

tenth chamber

73

eleventh chamber

74

twelfth chamber

75

thirteenth chamber

76

fourteenth chamber

77

ninth gas line

78

tenth gas line

79

eleventh end wall

80

twelfth end wall

81

fifth liquid line

82

sixth liquid line

83

first gas passage means

84

second gas passage device

85

liquid passage device

85a

third channel

85b

fourth channel

86

first channel

87

first riser

88

second riser

89

third riser

90

second channel

91

fourth riser

92

fifth riser

93

sixth riser

94

seventh liquid line

95

eighth fluid line

96

ninth liquid line

97

tenth liquid line

98

thirteenth gas connection device

99

fourteenth gas connection device

100

first compressed gas supply line

101

second compressed gas supply line

102

eleventh gas line

103

twelfth gas line

104

first exhaust pipe

105

second exhaust pipe

106

ninth hollow cylinder

107

thirteenth end wall

108

fourteenth end wall

109

second piston rod

110

seventh piston

111

eighth piston

112

third middle part

113

fifteenth chamber

114

sixteenth chamber

115

seventeenth chamber

116

eighteenth chamber

117

fifteenth gas connection device

118

sixteenth gas connection device

119

seventh liquid connection device

120

eighth liquid connection device

121

fifth fluid port means

122

sixth liquid connection device

123

first piston tube

124

tenth hollow cylinder

125

eleventh liquid line

126

twelfth liquid line

127

first four-valve block

128

first valve

129

second valve

130

third valve

131

fourth valve

132

second four-valve block

133

fifth valve

134

sixth valve

135

seventh valve

136

eighth valve

137

first exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary stage device according to the invention

138

second embodiment of a compressed gas energy conversion heat exchanger device preliminary stage device according to the invention

139

fourteenth gas line

140

sixteenth gas line

141

seventeenth gas line

142

fifteenth gas line

143

eighteenth gas line

144

thirteenth gas line

145

nineteenth gas line

146

further exemplary embodiment of a compressed gas energy conversion heat exchanger device according to the invention

147

thirteenth liquid line

148

first flow control valve means

149

third exemplary embodiment of a compressed gas energy conversion heat exchanger device preliminary stage device according to the invention

150

fourteenth liquid line

151

second flow control valve means

152

eleventh hollow cylinder

153

twelfth hollow cylinder

154

fifteenth end wall

155

sixteenth end wall

156

seventeenth end wall

157

eighteenth front wall

158

ninth piston

159

left partial piston rod

160

nineteenth chamber

161

twentieth chamber

162

tenth piston

163

right split piston rod

164

twenty-first chamber

165

twenty-second chamber

166

screw

167

seventeenth gas connection device

168

eighteenth gas connection device

169

ninth liquid connection device

170

tenth liquid connection device

171

fixed component of the displacement detection device

172

movable component of the displacement detection device

173

watercraft

174

Tube in which an impeller is placed

175

impeller

176

Gas bubbles and/or gas bubbles

177

Device that is set up to introduce gas into the pipe with the impeller, which gas has already performed work to be performed by it in the compressed-gas-based energy conversion device

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102013105186 A1 [0001, 0004, 0005, 0006, 0009, 0012, 0013, 0015, 0016, 0028, 0035]
• US20120210705A1 [0012]

Claims (56)

Controllable drive device for a land vehicle, water vehicle and/or air vehicle based on a compressed gas-based energy conversion device which uses the principle of the double-acting hydraulic-pneumatic tandem cylinder, the drive device for the land vehicle, water vehicle and/or air vehicle having a motor driven by liquid flow and the liquid flow for driving the motor is provided by the said compressed-gas-based energy conversion device and the drive device also has a control device which is set up and designed in such a way that a driver and/or an automatic driver of the land vehicle, water vehicle and/or aircraft by means of the control device can control a driving force of the engine in that the control device can control a valve or a plurality of valves in the named compressed-gas-based energy conversion device in this way during ongoing operation of the engine, or k that an active supply of pressurized gas from the outside into a chamber (160, 165) to be pressurized with pressurized gas during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder can already be ended before a said chamber (160, 165) delimiting and through the pressurized gas moving piston (158, 162) reaches a stop that mechanically limits its movement path, with said piston (158, 162) then only moving under the influence of the pressure gas already filled into the chamber (160, 165) after the active compressed gas supply has been switched off from the outside Compressed gas in the direction of the movement of the piston (160, 165) moves mechanically limiting stop. Controllable drive device for a land vehicle, water vehicle and/or air vehicle based on a compressed gas-based energy conversion device which uses the principle of the double-acting hydraulic-pneumatic tandem cylinder, the drive device for the land vehicle, water vehicle and/or air vehicle having a motor driven by liquid flow and the liquid flow for driving the motor is provided by the said compressed-gas-based energy conversion device and the drive device also has a control device which is set up and designed in such a way that a driver and/or an automatic driver of the land vehicle, water vehicle and/or aircraft by means of the control device can control a driving force of the engine in that the control device can control a valve or a plurality of valves in the named compressed-gas-based energy conversion device in this way during ongoing operation of the engine, or k that the strength of an active supply of compressed gas from the outside into a chamber (160, 165) to be pressurized with compressed gas during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder can be adjusted continuously and/or in stages within a certain pressure range. Controllable drive device claim 2 , characterized in that the control device is also set up and designed in such a way that it can be used to control a valve or a plurality of valves in the said compressed-gas-based energy conversion device during ongoing operation of the engine in such a way that an active supply of compressed gas from the outside into a during a working cycle of the double-acting hydraulic-pneumatic tandem cylinder, the chamber (160, 165) to which pressurized gas is to be applied can already be terminated before a piston (158, 162) delimiting said chamber (160, 165) and moved by the pressurized gas comes to a stop mechanically limiting its travel after the active compressed gas supply has been switched off from the outside, said piston (158, 162) then only moves mechanically in the direction of the movement path of the piston (158, 162) under the influence of the compressed gas already filled into the chamber (160, 165). limiting stop moves. Controllable drive device according to one of the preceding claims, characterized in that the control device is set up and designed in such a way that the control of switching off the compressed gas supply or the control of the intensity of the compressed gas supply or both the control of the intensity of the compressed gas supply and the control of the switching off of the compressed gas supply by means of an electronic pressure control. Controllable drive device claim 1 or after claim 3 or after claim 4 , characterized in that the control device has a travel detection device (171, 172) which is set up and designed in such a way that with the aid of this travel detection device (171, 172) the piston travel can be adjusted steplessly or in stages during ongoing operation of the engine, according to which switches off the active compressed gas supply. Controllable drive device claim 5 , characterized in that the path detection device (171, 172) on a magnetic and / or mechanical and / or optical and / or electronic and / or optical position detection device (171, 172) based on electronic functioning. Controllable drive device according to one of the preceding claims, characterized in that the control device has an operating device, by means of which the driver of the land vehicle, water vehicle and/or aircraft can operate the said control device. Controllable drive device according to one of the preceding claims, characterized in that the vehicle is a watercraft (173) and is set up in such a way that gas, which has already performed work to be performed by it in the compressed gas-based energy conversion device, is used to under the hull or under to produce a carpet of gas bubbles and/or gas bubbles (176) on part of the hull of the watercraft (173). Controllable drive device according to one of the preceding claims, characterized in that the vehicle is a watercraft (173) which has a tube (174) in which an impeller (175) is arranged, with the purpose of driving the watercraft (173) by means of the impeller (175) at one end of the tube (174) water is sucked in from the body of water in which the watercraft (173) is swimming and is ejected again at the opposite end of the tube (174), and wherein a device (177) is also provided, which is set up to inject gas, which has already performed the work to be performed by it in the compressed-gas-based energy conversion device, in relation to the direction of water flow in the named pipe (174) behind the impeller (175), preferably immediately behind the impeller (175), into the to initiate said tube (174). Controllable drive device claim 9 , characterized in that the impeller is controllably arranged such that it can be used to cause water to flow in said tube both in one direction and in the opposite direction, and in that the impeller is switchable between both said water flow directions and that furthermore the said device, which is set up to introduce gas, which has already performed work to be performed by it in the compressed-gas-based energy conversion device, into the said tube behind the impeller, based on the direction of water flow in the said tube, preferably directly behind the impeller, is set up in a suitable manner in order to adapt the specific point of introduction of the gas into said pipe to the respective current direction of water flow. Controllable drive device claim 9 or after claim 10 , characterized in that the watercraft (173) is arranged in such a way that gas introduced into said pipe (174) after its exit from said pipe (174) forms a carpet of gas bubbles and/or gas bubbles under a part of the hull of the watercraft (173). or gas bubbles (176) generated. Controllable drive device according to any one of the preceding claims, characterized in that the compressed gas is air and/or biogas and/or methane and/or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of air and one or more hydrocarbon gases is. Controllable drive device according to any one of the preceding claims, characterized in that the liquid used to drive the motor is oil. Controllable drive device according to one of the preceding claims, characterized in that the compressed gas-based energy conversion device has a hydraulic piston device (1) which can be used at least for the purpose of gas compression, the hydraulic piston device (1) having - a first hollow cylinder (2) which has a first end wall (3) at one end and a second end wall (4) at its other end, - a second hollow cylinder (5) which has a third end wall (6) at one end and a fourth end wall at its other end (7), - a third hollow cylinder (8), which has a fifth end wall (9) at one end and a sixth end wall (10) at its other end, - a fourth hollow cylinder (11), which at one end a seventh end wall (12) and at its other end an eighth end wall (13), and - a piston rod (14) on which a first piston (15), a second piston (16), a third piston (17) and a fourth piston (18) are fixed, the first hollow cylinder (2), the second hollow cylinder (5), the third hollow cylinder (8) and the fourth hollow cylinder (11 ) are arranged in a row in such a way that - the second end wall (4) and the third end wall (6) face each other, - the fourth end wall (7) and the fifth end wall (9) face each other, - the sixth end wall ( 10) and the seventh end wall (12) face each other and - accordingly, the first end wall (3) one end of said row of hollow cylinders (2, 5, 8, 11) and the eighth end wall (13) another end of the said series of hollow cylinders (2, 5, 8, 11), and wherein - the piston rod (14) with the four pistons (15, 16, 17, 18) fixed to it is arranged in such a way that one end is in the first hollow cylinder (2) and its other end is located in the fourth hollow cylinder (11) and the piston rod (14) accordingly passes through an opening in the second end wall (4), through an opening in the third end wall (6), through the second Hollow cylinder (5), through an opening in the fourth end wall (7), through an opening in the fifth end wall (9), through the third hollow cylinder (8), through an opening in the sixth end wall (10) and through an opening in extends through the seventh end wall (12), - the first piston (15) is located in the first hollow cylinder (2) and divides it into a first chamber (19) and a second chamber (20), the first chamber (19) and the second chamber (20) is sealed off from one another by the first piston (15), - the second piston n (16) is located in the second hollow cylinder (5) and divides it into a third chamber (21) and a fourth chamber (22), the third chamber (21) and the fourth chamber (22) being filled by the second piston (16 ) are sealed against each other, - the third piston (17) is located in the third hollow cylinder (8) and divides this into a fifth chamber (23) and a sixth chamber (24), the fifth chamber (23) and the sixth chamber ( 24) are sealed from one another by the third piston (17), - the fourth piston (18) is located in the fourth hollow cylinder (11) and divides it into a seventh chamber (25) and an eighth chamber (26), the seventh chamber (25) and the eighth chamber (26) are sealed from one another by the fourth piston (18), - the piston rod (14) with the four pistons (15, 16, 17, 18) fixed to it can be moved back and forth in the longitudinal direction , so that the size of the respective volume of each of the eight chambers (19, 20, 21, 22, 23, 24, 25, 26) corresponds to is variable according to the respective piston stroke, - both the fourth chamber (22) and the fifth chamber (23) are each provided for complete filling with liquid, - both the first chamber (19) and the second chamber (20) as well the third chamber (21) as well as the sixth chamber (24) as well as the seventh chamber (25) and the eighth chamber (26) are completely filled with gas, - the fourth chamber (22) with a first liquid connection device (27) and is provided with a second liquid connection device (28), - the fifth chamber (23) is provided with a third liquid connection device (29) and with a fourth liquid connection device (30), - the first chamber (19) with a first gas connection device (31) and is provided with a second gas connection device (32), - the seventh chamber (25) is provided with a third gas connection device (33) and with a fourth gas connection device (34), - the sixth chamber (24) is provided with a fifth gas connection device (35), - a first gas line (36) leads from the second gas connection device (32) to the fifth gas connection device (35), - a second gas line (37) from the fourth gas connection device ( 34) leading to the fifth gas connection device (35), - the second chamber (20) is provided with a sixth gas connection device (38) and with a seventh gas connection device (39), - the eighth chamber (26) with an eighth gas connection device (40) and is provided with a ninth gas connection device (41), - the third chamber (21) is provided with a tenth gas connection device (42), - a third gas line (43) leads from the seventh gas connection device (39) to the tenth gas connection device (42). - a fourth gas line (44) leads from the ninth gas connection device (41) to the tenth gas connection device (42), - the third chamber (21) with an eleventh gas connection device (45), - the sixth chamber (24) is provided with a twelfth gas connection device (46), - the first gas connection device (31) is set up by means of a valve device belonging to it in such a way that the first gas connection device (31) at correspondingly suitable valve setting for sucking gas into the first chamber (19), - the third gas connection device (33) is set up by means of a valve device belonging to it in such a way that the third gas connection device (33) with a correspondingly suitable valve setting for sucking gas into the seventh chamber (25), - the sixth gas connection device (38) is set up by means of a valve device belonging to it in such a way that the sixth gas connection device (38) serves to suck gas into the second chamber (20) with a correspondingly suitable valve setting, - the eighth Gas connection device (40) is set up by means of a valve device belonging to it t that the eighth gas connection device (40) is used for sucking gas into the eighth chamber (26) with a correspondingly suitable valve setting, - the second gas connection device (32) is set up by means of a valve device belonging to it in such a way that the second gas connection device (32) with a suitable valve setting is used to discharge compressed gas from the first chamber (19) into the first gas line (36), - the fourth gas connection device (34) is set up by means of a valve device belonging to it in such a way that the fourth gas connection device (34) can be discharged when the valve is set appropriately compressed gas from the seventh chamber (25) into the second gas line (37), - the fifth gas connection device (35) is set up by means of a valve device belonging to it in such a way that the fifth gas connection device (35) with a correspondingly suitable valve setting for introducing compressed gas from the first gas line (36) or from the second gas line (37) into the sixth chamber (24), - the seventh gas connection device (39) is set up by means of a valve device belonging to it in such a way that the seventh gas connection device (39) at according to appropriate valve setting for exhausting compressed gas from the second chamber (20) into the third gas line (43), - the ninth gas connection device (41) is set up by means of a valve device belonging to it in such a way that the ninth gas connection device (41) with a correspondingly suitable valve setting for discharging compressed gas from the eighth chamber (26th ) into the fourth gas line (44), - the tenth gas connection device (42) is set up by means of a valve device belonging to it in such a way that the tenth gas connection device (42) with a correspondingly suitable valve setting for introducing compressed gas from the third gas line (43) or from the fourth gas line (44) into the third chamber (21), - the eleventh gas connection device (45) is set up by means of a valve device belonging to it in such a way that the eleventh gas connection device (45) with a correspondingly suitable valve setting for discharging compressed gas the third chamber (21) is used, - the twelfth gas connection device (46) means s a valve device belonging to it is set up in such a way that the twelfth gas connection device (46) serves to discharge compressed gas from the sixth chamber (24) when the valve is set appropriately, - the first liquid connection device (27) is set up in such a way by means of a valve device belonging to it that the first liquid connection device (27) serves as a liquid inlet for pumping liquid into the fourth chamber (22) with a correspondingly suitable valve setting, - the third liquid connection device (29) is set up by means of a valve device belonging to it in such a way that the third liquid connection device (29 ) with a correspondingly suitable valve setting as a liquid inlet for pumping liquid into the fifth chamber (23), - the second liquid connection device (28) is set up by means of a valve device belonging to it in such a way that the second liquid connection direction (28) serves as a liquid outlet for forcing liquid out of the fourth chamber (22) with a correspondingly suitable valve setting and - the fourth liquid connection device (30) is set up by means of a valve device belonging to it in such a way that the fourth liquid connection device (30) with a correspondingly suitable Valve setting serves as a liquid outlet for pushing out liquid from the fourth chamber (23). Controllable drive device Claim 14 , characterized in that the hydraulic piston device (1) is set up in such a way that compressed gas discharged from the eleventh gas connection device (45) is supplied to a consumer of compressed gas and/or to a compressed gas storage device. Controllable drive device Claim 14 or after claim 15 , characterized in that the hydraulic piston device (1) is set up in such a way that compressed gas discharged from the twelfth gas connection device (46) is supplied to a consumer of compressed gas and/or to a compressed gas storage device. Controllable drive device according to one of Claims 14 until 16 , characterized in that the hydraulic piston device (1) is set up in such a way that liquid pressed out of the second liquid connection device (28) is supplied to a liquid storage device. Controllable drive device according to one of Claims 14 until 17 , characterized in that the hydraulic piston device (1) is set up in such a way that liquid pressed out of the fourth liquid connection device (30) is supplied to a liquid storage device. Controllable drive device Claim 17 or after Claim 18 , characterized in that the hydraulic piston device (1) is set up in such a way that it can remove liquid from the liquid storage device for pumping into the first liquid connection device (27) and/or into the third liquid connection device (29). Controllable drive device according to one of Claims 14 until 19 , characterized in that the hydraulic piston device (1) is set up such that - all four hollow cylinders (2, 5, 8, 11) each have the same length, - the second hollow cylinder (5) and the third hollow cylinder (8) each have the same diameter, - the first hollow cylinder (2) and the fourth hollow cylinder (11) each have the same diameter and - the diameter of the first hollow cylinder (2) is larger than the diameter of the second hollow cylinder (5). Controllable drive device claim 20 , characterized in that the hydraulic piston device (1) is set up in such a way that the diameter of the first hollow cylinder (2) is at least twice as large as the diameter of the second hollow cylinder (5). Controllable drive device according to one of Claims 14 until 21 , characterized in that the hydraulic piston device (1) is set up in such a way that the first hollow cylinder (2) and the second hollow cylinder (5) are seated directly against one another, so that the second end wall (4) and the third end wall (6) at least partially coincide. Controllable drive device according to one of Claims 14 until 22 , characterized in that the hydraulic piston device (1) is set up in such a way that the third hollow cylinder (8) and the fourth hollow cylinder (11) are seated directly against one another, so that the sixth end wall (10) and the seventh end wall (12) at least partially coincide. Controllable drive device according to one of Claims 14 until 23 , characterized in that the hydraulic piston device (1) is set up in such a way that the diameter of the piston rod (14) varies over the length of the piston rod (14) such that - the piston rod (14) immediately following the first piston ( 15) in the direction of the second piston (16) has a larger diameter than immediately following the second piston (16) in the direction of the first piston (15) and - the piston rod (14) immediately following the fourth piston ( 18) in the direction of the third piston (17) has a larger diameter than immediately following the third piston (17) in the direction of the fourth piston (18). Controllable drive device Claim 14 , characterized in that the compressed gas-based energy conversion device has a compressed gas energy conversion device (50), which in turn has - the hydraulic piston device (1), - a compressed gas storage device and - a liquid storage device, with - the eleventh gas connection device (45) being connected to the compressed gas storage device and connected by means of the to the valve device belonging to the eleventh gas connection device (45) is set up in such a way that the eleventh gas connection device (45) serves to introduce compressed gas from the compressed gas storage device into the third chamber (21) when the valve is set appropriately, - the twelfth gas connection device (46) is connected to the compressed gas storage device and is set up by means of the valve device belonging to the twelfth gas connection device (46) in such a way that the twelfth gas connection device (46) compresses when the valve setting is appropriate for the introduction th gas from the compressed gas storage device into the sixth chamber (24), - the second liquid connection device (28) is connected to the liquid storage device and is set up by means of the valve device belonging to the second liquid connection device (28) in such a way that the second liquid connection device (28) at correspondingly suitable valve position for sucking liquid from the liquid storage device into the fourth chamber (22), - the fourth liquid connection device (30) is connected to the liquid storage device and is set up by means of the valve device belonging to the fourth liquid connection device (30) in such a way that the fourth liquid connection device ( 30) with a correspondingly suitable valve setting for sucking liquid from the liquid storage device into the fifth chamber (23), - the first liquid connection device (27) by means of which it belongs gen valve device is set up in such a way that the first liquid connection device (27), with a correspondingly suitable valve setting, is used to introduce liquid from the fourth chamber (22) into a first liquid line (47), which is set up in such a way that it is introduced into and through it liquid flowing through it to a machine (48) to be driven by the flowing liquid, whereby this machine (48) can be, for example, a drive device for an electrical energy generator, - the third liquid connection device (29) is set up by means of the associated valve device in such a way that the third Liquid connection device (29), with a correspondingly suitable valve setting, is used to introduce liquid from the fifth chamber (23) into a second liquid line (49), which is set up in such a way that liquid introduced into it and flowing through it becomes a liquid flowing through it t to be driven machine (48), which can be, for example, a drive device for an electric power generator, directs - the tenth gas connection device (42) by means the valve device belonging to it is set up in such a way that the tenth gas connection device (42) serves to introduce gas from the third chamber (21) into a fifth gas line (51) with a correspondingly suitable valve setting, - a first pressure control valve device (52) is present, which regulates gas pressure and liquid pressure against each other, is connected to the fifth gas line (51) on the gas side by means of a sixth gas line (53) and is connected to the second liquid line (49) on the liquid side by means of a third liquid line (54), - the fifth gas connection device (35) is set up by means of the associated valve device in such a way that the fifth gas connection device (35) serves to introduce gas from the sixth chamber (24) into a seventh gas line (55) when the valve is set appropriately, - a second pressure control valve device (56) is present , which regulates gas pressure and liquid pressure against each other, g gas side is connected to the seventh gas line (55) by means of an eighth gas line (57) and is connected to the first liquid line (47) by means of a fourth liquid line (58) on the liquid side, - the fifth gas line (51) also to one from the fifth - the seventh gas line (55) also leads to a gas thermally and/or mechanically and/or mechanically and/or or chemically using, consumer device (59). Controllable drive device according to one of the preceding claims, characterized in that the compressed gas-based energy conversion device has a compressed gas energy conversion heat exchanger device (60, 146), which in turn has - a fifth hollow cylinder (61) which has a ninth end wall (62) and a tenth end wall (63), - a first central part (64) which is arranged centrally in relation to the longitudinal direction of the fifth hollow cylinder (61) and which is fastened inside the fifth hollow cylinder (61) to its inner wall, in its longitudinal position over the extends over the entire circumference of the inner wall of the fifth hollow cylinder (61), but has a through hole radially in the middle, - a second central part (65), which is positioned in said hole and is fixed there by being used both as an end part of a sixth hollow cylinder ( 66) and as a front part of a seventh hollow cylinder (67), the sixth Ho The hydraulic cylinder (66) extends, starting from the second central part (65), in the direction of the ninth end wall (62) and through a first opening in the ninth end wall (62) and is fixed to the ninth end wall (62) and wherein the seventh hollow cylinder (67) extends, starting from the second central part (65), in the direction of the tenth end wall (63) and through a first opening in the tenth end wall (63) and is fixed to the tenth end wall (63) and wherein the sixth hollow cylinder (66) is delimited at its end opposite the second central part (65) by an eleventh end wall (79) and the seventh hollow cylinder (67) at its end opposite the second central part (65) by a twelfth end wall (80) is delimited, - an eighth hollow cylinder (68) which extends between the first middle part (64) and the second middle part (65) and can be moved back and forth in the longitudinal direction of the fifth hollow cylinder (61), the ac hth hollow cylinder (68) is closed at its end pointing towards the ninth end wall (62) by a fifth piston (69), which has the shape of a circular disc and whose outer circumference nestles against the inner wall of the fifth hollow cylinder (61) and whose inner circumference nestles against an outer wall of the sixth hollow cylinder (66), and the eighth hollow cylinder (68) is closed off at its end pointing towards the tenth end wall (63) by a sixth piston (70), which has the shape of a circular disk and whose outer circumference the inner wall of the fifth hollow cylinder (61) and the inner circumference of which nestles against an outer wall of the seventh hollow cylinder (67), and wherein the fifth hollow cylinder (61), the first middle part (64), the second middle part (65) , the sixth hollow cylinder (66), the seventh hollow cylinder (67), the eighth hollow cylinder (68), the fifth piston (69) and the sixth piston (70) are set up and arranged such that s I result in the following six chambers of variable volume that are hydraulically and pneumatically sealed against one another: a ninth chamber (71), which is delimited by the ninth end wall (62), the fifth piston (69), the inner wall of the fifth hollow cylinder (61) and the outer Wall of the sixth hollow cylinder (66), a tenth chamber (72) which is delimited by the tenth end wall (63), the sixth piston (70), the inner wall of the fifth hollow cylinder (61) and the outer wall of the seventh hollow cylinder ( 67), an eleventh chamber (73) delimited by the fifth piston (69), the first central part (64), the inner wall of the fifth hollow cylinder (61) and an outer wall of the eighth hollow cylinder (68), a twelfth Chamber (74) delimited by the sixth piston (70), the first middle part (64), the inner wall of the fifth hollow cylinder (61) and the outer wall of the eighth hollow cylinder (68), a thirteenth chamber (75), which is limited by the f fifth piston (69), the second middle part (65), the outer wall of the sixth hollow cylinder (66) and an inner wall of the eighth hollow cylinder (68), a fourteenth chamber (76), which is delimited by the sixth piston (70), the second middle part (65), the outer wall of the seventh hollow cylinder (67) and the inner wall of the eighth hollow cylinder (68), wherein during operation of the compressed gas energy conversion heat exchanger device (60, 146) the ninth chamber (71), the tenth chamber (72), the thirteenth chamber (75) and the fourteenth chamber (76) for containing gas and the eleventh chamber (73) and the twelfth chamber (74) for containing Liquid are provided, - a ninth gas line (77) which runs within the sixth hollow cylinder (66) and, starting from the second central part (65), through an opening in the eleventh end wall (79) extends, with a not from the ninth gas line (77) filled interior of the sixth hollow cylinder (66) during operation of the compressed gas energy conversion heat exchanger device (60, 146) for receiving liquid, - a tenth gas line (78) which is inside the seventh hollow cylinder rs (67) and, starting from the second central part (65), extends through an opening in the twelfth end wall (80), with an interior space of the seventh hollow cylinder (67) not filled by the tenth gas line (78) during operation the compressed gas energy conversion heat exchanger device (60, 146) is provided for receiving liquid, - a fifth liquid line (81) which branches off from the sixth hollow cylinder (66) at the end of the sixth hollow cylinder (66) opposite the second central part (65). and extending outside the fifth hollow cylinder (61) to the position of the twelfth chamber (74), - a ninth liquid line (96) provided with valve means, which at one end passes through a region of the twelfth chamber (74) near the first central part (64) provided first opening in the side wall of the fifth hollow cylinder (61) with the twelfth chamber (74) and at its other end in the fifth - a tenth liquid line (97) provided with a valve device, which at one end passes through a second opening provided in the area of the eleventh chamber (73) near the first central part (64) in the side wall of the fifth hollow cylinder ( 61) is connected to the eleventh chamber (73) and at its other end opens into the fifth liquid line (81), - a sixth liquid line (82) which is located at the end of the seventh hollow cylinder (67) opposite the second central part (65) branches off from the seventh hollow cylinder (67) and is intended for connection to a liquid tank, - a first gas passage device (83) which is arranged inside the second central part (65) and which is set up in this way and connected both to the ninth gas line (77) and to the thirteenth Chamber (75) is connected so that gas flows through the first gas conduit device (83) between the ninth gas line (77) and the thirteenth chamber (7th 5) can flow back and forth, - a second gas passage device (84) arranged within the second middle part (65), which is set up and connected to both the tenth gas line (78) and the fourteenth chamber (76) in such a way that through the second gas passage device (84) allows gas to flow back and forth between the tenth gas line (78) and the fourteenth chamber (76), - a liquid passage device (85) which is arranged within the second central part (65) and is set up in such a way that it connects the part of the interior of the sixth hollow cylinder (66) provided for receiving liquid and the part of the interior of the seventh hollow cylinder (67) provided for receiving liquid in such a way that liquid passes through the liquid passage device (85) between the sixth hollow cylinder (66) and the seventh hollow cylinder (67), - one provided with a valve device seventh liquid line (94), which communicates with the eleventh chamber (73) through a third opening provided in the side wall of the fifth hollow cylinder (61) in the area of the eleventh chamber (73) near the first central part (64), so that at corresponding movement of the fifth piston (69), liquid can be pressed from the eleventh chamber (73) into the seventh liquid line (94), - an eighth liquid line (95) provided with a valve device, which passes through a fourth opening provided near the first central part (64) in the side wall of the fifth hollow cylinder (61) communicates with the twelfth chamber (74), so that with a corresponding movement of the sixth piston (70), liquid flows out of the twelfth chamber (74) into the eighth liquid line (95) can be pressed in, - a thirteenth gas connection device (98) provided with a valve device, which can be connected through a second opening in de r ninth end wall (62) communicates with the ninth chamber (71) and - a fourteenth gas connection device (99) provided with a valve device, which communicates with the tenth chamber (72) through a second opening in the tenth end wall (63). stands. Controllable drive device Claim 26 , characterized in that the compressed gas energy conversion heat exchanger device (60, 146) is set up in such a way that the first gas passage device (83) has an elongate, inside the second central part (65) arranged first channel (86), which in its middle with a first riser (87), at its one end with a second riser (88) and at its other end with a third riser (89) is provided, wherein the first riser (87) opens into the ninth gas line (77) and the second riser (88) and the third riser (89) each open into the thirteenth chamber (75). Controllable drive device Claim 26 or after Claim 27 , characterized in that the compressed gas energy conversion heat exchanger device (60, 146) is set up in such a way that the second gas passage device (84) has an elongate second channel (90) which is arranged within the second central part (65) and which in its center has a fourth riser pipe (91), at one end with a fifth riser pipe (92) and at its other end with a sixth riser pipe (93), the fourth riser pipe (91) opening into the tenth gas line (78) and the fifth riser pipe (92) and the sixth riser pipe (93) each open into the fourteenth chamber (76). Controllable drive device according to one of Claims 26 , 27 or 28 , characterized in that the compressed gas energy conversion heat exchanger device (60, 146) is set up in such a way that the liquid passage device (85) has a third channel (85a) and a fourth channel (85b), with both the third channel (85a) and the fourth channel (85b) each extend through the second central part (65) and are completely separated both from the first gas conduction device (83) and from the second gas conduction device (84) and both towards the sixth hollow cylinder (66) and are also open to the seventh hollow cylinder (67). Controllable drive device claim 29 , characterized in that the compressed gas energy conversion heat exchanger device (60, 146) is set up in such a way that the third channel (85a) and/or the fourth channel (85b) has or have a bean-shaped or kidney-shaped cross section. Controllable drive device according to one of Claims 26 until 30 , characterized in that the compressed gas energy conversion heat exchanger device (60, 146) is set up in such a way that the sixth hollow cylinder (66) is screwed into a circumferential groove in the second central part (65) in the second central part (65) and on is attached to the second central part (65) in this way. Controllable drive device according to one of Claims 26 until 31 , characterized in that the compressed gas energy conversion heat exchanger device (60, 146) is set up in such a way that the seventh hollow cylinder (67) is screwed into a circumferential groove in the second center part (65) in the second center part (65) and on is attached to the second central part (65) in this way. Controllable drive device according to one of Claims 26 until 32 , characterized in that the compressed gas energy conversion heat exchanger device (146) has a thirteenth liquid line (147) which is connected at one end to the sixth liquid line (82) and is set up in such a way that this thirteenth liquid line (147) is able to is to conduct liquid from the sixth liquid line (82) to the ninth liquid line (96) and to the tenth liquid line (97) without the liquid passing through the seventh hollow cylinder on its way to the ninth liquid line (96) and the tenth liquid line (97). (67), the liquid passage device (85) and the sixth hollow cylinder (66), the connection of the thirteenth liquid line (147) to the sixth liquid line (82) being provided with a first flow control valve device (148), which is controllable and designed in such a way that by means of the first flow control valve means (148) ge it is possible to control which portion of a liquid flow arriving from the liquid tank via the sixth liquid line (82) at the first flow control valve device (148) is routed into the seventh hollow cylinder (67) and which portion is routed into the thirteenth liquid line (147), the control option of first flow control valve device (148) includes at least the possibility of controlling whether the liquid flow arriving at it via the sixth liquid line (82) is passed completely into the seventh hollow cylinder (67) or completely into the thirteenth liquid line (147). Controllable drive device Claim 33 , characterized in that the first flow control valve device (148) is set up in such a way that, in addition to the already mentioned possibility of controlling the complete introduction of the liquid flow arriving at it via the sixth liquid line (82), it either into the seventh hollow cylinder (67) or into the thirteenth liquid line (147) can also be controlled in such a way that it can divide the flow of liquid arriving at it via the sixth liquid line (82) so that part of the liquid reaches the seventh hollow cylinder (67) and at the same time another part of the liquid gets into the thirteenth liquid line (147), wherein an associated flow distribution ratio can be controlled steplessly and/or in stages. Controllable drive device Claim 33 or after Claim 34 , characterized in that the compressed gas energy conversion heat exchanger means (146) is arranged such that the first flow control valve means (148) controls the liquid flow in dependence on a gas and/or liquid temperature measurement. Controllable drive device Claim 35 , characterized in that the compressed gas energy conversion heat exchanger device (146) is set up in such a way that, if a gas temperature measurement is carried out to control the first flow control valve device (148), this gas temperature measurement takes place at least in a region of the ninth gas line (77) which is from is further spaced from the second middle part (65) than from the eleventh end wall (79), and that if a liquid temperature measurement is taken to control the first flow control valve means (148), this liquid temperature measurement is taken at least either in the fifth liquid line (81) or in one area of the sixth hollow cylinder (66), which is further spaced from the second central part (65) than from the eleventh end wall (79). Controllable drive device according to one of Claims 33 until 36 , characterized in that the first flow control valve means (148) comprises a thermostatic valve. Controllable drive device according to one of Claims 33 until 37 , characterized in that the compressed gas energy conversion heat exchanger device (146) is set up in such a way that the control of the first flow control valve device (148) is mechanical and/or electromechanical and/or magnetic and/or electromagnetic and/or electronic and/or optical and/or or electro-optically. Controllable drive device according to one of Claims 33 until 38 Characterized in that the thirteenth liquid line (147) is arranged to open into the fifth liquid line (81) at its end remote from the first flow control valve means (148). Controllable drive device according to one of the preceding claims, characterized in that the compressed gas-based energy conversion device has a compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149), which in turn has - a ninth hollow cylinder (106) which at its one end has a thirteenth end wall (107) and at its other end a fourteenth end wall (108), - a third central part (112) which is arranged centrally in relation to the longitudinal direction of the ninth hollow cylinder (106) and which is located inside the ninth hollow cylinder (106) at its inner wall, extends in its longitudinal position over the entire circumference of the inner wall of the ninth hollow cylinder (106) and thus forms a middle wall oriented parallel to the thirteenth end wall (107) and the fourteenth end wall (108), but radially centrally has a through hole, - a second piston rod (109), we l which extends through the aforementioned hole and can be moved back and forth in its longitudinal direction, - a seventh piston (110) which is fixed on one end of the second piston rod (109) and which nestles against the inner wall of the ninth hollow cylinder (106) and divides the space between the third center part (112) and the thirteenth end wall (107) into a fifteenth chamber (113) and a seventeenth chamber (115), each with a variable volume, in a hydraulic-pneumatically sealing manner, with the seventeenth chamber (115) adjoining the third center part (112) and the fifteenth chamber (113) is adjacent to the thirteenth end wall (107) and the seventeenth chamber (115) is for holding liquid and the fifteenth chamber (113) is for holding gas, - one on the other end the second piston rod (109) fixed eighth piston (111), which nestles against the inner wall of the ninth hollow cylinder (106) and the space between the third middle part (112) and of the fourteenth end wall (108) in a hydraulic-pneumatically sealing manner into a sixteenth chamber (114) and an eighteenth chamber (116), each of variable volume, with the eighteenth chamber (116) adjoining the third middle part (112) and the sixteenth chamber (114 ) adjoins the fourteenth end wall (108) and the eighteenth chamber (116) is provided for holding liquid and the sixteenth chamber (114) for holding gas, - a fifteenth gas connection device (117) provided with an associated valve device, through which according to the valve position, gas from outside the compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149) flows into the fifteenth chamber (113) or out of the fifteenth chamber (113) and thus out of the compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149) can flow out, the fifteenth gas connection device (117) being on or near the thirteenth end wall (1st 07) is positioned, - A sixteenth gas connection device (118) provided with an associated valve device, through which, depending on the valve position, gas flows from outside the compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149) into the sixteenth chamber (114) or out of the sixteenth chamber ( 114) and thus can flow out of the compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149), the sixteenth gas connection device (118) being positioned at or near the fourteenth end wall (108), - one provided with an associated valve device fifth fluid port means (121) for introducing fluid from outside of the compressed gas energy conversion heat exchanger means precursor means (137, 138, 149) into the seventeenth chamber (115), the fifth fluid port means (121) positioned proximate to the third center portion (112). is, - one with an associated Ventileinr Sixth liquid connection device (122) provided with a device for introducing liquid from outside the compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149) into the eighteenth chamber (116), the sixth liquid connection device (122) being close to the third central part (112 ) is positioned, - a seventh liquid connection device (119) provided with an associated valve device for leading liquid out outside the compressed gas energy conversion heat exchanger device preliminary stage device (137, 138, 149) out of the seventeenth chamber (115), the seventh liquid connection device (119) is positioned near the third middle part (112), and - an eighth fluid connection means (120) provided with associated valve means for leading fluid out to the outside of the compressed gas energy conversion heat exchanger means preliminary stage means (137, 138, 149) of de r eighteenth chamber (116), wherein the eighth fluid port means (120) is positioned near the third center portion (112). Controllable drive device Claim 40 , characterized in that the compressed gas energy conversion heat exchanger device preliminary device (138, 149) comprises a tenth hollow cylinder (124) which is arranged inside the ninth hollow cylinder (106) and extends through the opening in the third middle part (112). and extending at its one end through an opening in the thirteenth end wall (107) and at its other end through an opening in the fourteenth end wall (108) beyond the thirteenth end wall (107) and beyond the fourteenth end wall (108), respectively extends, wherein - the second piston rod is designed as a first piston tube (123) which encloses the tenth hollow cylinder (124), hydraulically-pneumatically seals against the tenth hollow cylinder (124) and is designed in such a way that it rests on the tenth hollow cylinder ( 124) can slide back and forth, and accordingly both the seventh piston (110) and the eighth piston (111) each ver can be seen, through which the tenth hollow cylinder (124) extends, and both the seventh piston (110) and the eighth piston (111) nestle against the tenth hollow cylinder (124) with a hydraulic-pneumatic seal and are designed such that they can slide back and forth on the tenth hollow cylinder (124) together with the first piston tube (123), on which they are each fixed, - an eleventh liquid line (125) is provided, which for the purpose of liquid transport is connected both to the fifth liquid connection device (121 ) as well as to the sixth fluid connection device (122) and to that end of the tenth hollow cylinder (124) which protrudes beyond the thirteenth end wall (107), and - a twelfth fluid line (126) is provided, which for the purpose of transporting fluid to that end of the tenth hollow cylinder (124) which projects beyond the fourteenth end wall (108) is connected. Controllable drive device Claim 41 , characterized in that the compressed gas energy conversion heat exchanger device preliminary stage device (149) has a fourteenth liquid line (150) which is connected at one end to the twelfth liquid line (126) and set up in such a way that this fourteenth liquid line (150) is able to conduct liquid from the twelfth liquid line (126) to the fifth liquid connection device (121) and to the sixth liquid connection device (122) without the liquid on its way to the fifth liquid connection device (121) and the sixth liquid connection device (122) having the tenth hollow cylinder (124), the connection of the fourteenth liquid line (150) to the twelfth liquid line (126) being provided with a second flow control valve device (151), which is controllable and designed in such a way that, by means of the second flow control valve device (151 ) it is possible to control what proportion of a liquid flow arriving at the second flow control valve device (151) via the twelfth liquid line (126) is directed into the tenth hollow cylinder (124) and what proportion is directed into the fourteenth liquid line (150), the control option of the second flow control valve device (151) includes at least the possibility of controlling whether the flow of liquid arriving at it via the twelfth liquid line (126) is conducted completely into the tenth hollow cylinder (124) or completely into the fourteenth liquid line (150). Controllable drive device Claim 42 , characterized in that the second flow control valve device (151) is set up in such a way that, in addition to the already mentioned possibility of controlling the complete introduction of the liquid flow arriving at it via the twelfth liquid line (126), it either into the tenth hollow cylinder (124) or into the fourteenth liquid line (150) can also be controlled in such a way that it can divide the liquid flow arriving at it via the twelfth liquid line (126), so that part of the liquid reaches the tenth hollow cylinder (124) and at the same time another part of the liquid gets into the fourteenth liquid line (150) arrives, with an associated flow splitting ratio being controllable steplessly and/or in stages. Controllable drive device Claim 42 or after Claim 43 , characterized in that the compressed gas energy conversion heat exchanger device preliminary stage means (149) is arranged such that the second flow control valve means (151) controls the liquid flow in dependence on a gas and/or liquid temperature measurement. Controllable drive device Claim 44 , characterized in that the compressed gas energy conversion heat exchanger device preliminary stage device (149) is set up in such a way that, if a gas temperature measurement is carried out to control the second flow control valve device (151), this gas temperature measurement is carried out at least either in the area of the fifteenth gas connection device (117) or in the area of the sixteenth gas connection device (118) or in an area of the fifteenth chamber (113) which is further away from the third central part (112) than from the thirteenth end wall (107), or in an area of the sixteenth chamber (114), which is further spaced from the third middle part (112) than from the fourteenth end wall (108), and that if a liquid temperature measurement is taken to control the second flow control valve means (151), this liquid temperature measurement takes place at least either in the eleventh liquid line (125) or in e in an area of the tenth hollow cylinder (124) which is spaced farther from the third central part (112) than from the thirteenth end wall (107). Controllable drive device according to one of Claims 42 until 45 , characterized in that the second flow control valve means (151) comprises a thermostatic valve. Controllable drive device according to one of Claims 42 until 46 , characterized in that the compressed gas energy conversion heat exchanger device pre-stage device (149) is set up such that the control of the second flow control valve device (151) is mechanical and/or electromechanical and/or magnetic and/or electromagnetic and/or electronic and/or optical and/or electro-optically. Controllable drive device according to one of Claims 42 until 47 Characterized in that the fourteenth fluid line (150) is arranged to open into the eleventh fluid line (125) at its end remote from the second flow control valve means (151). Controllable drive device with both all the features according to at least one of Claims 26 until 39 as well as all characteristics according to at least one of the Claims 40 until 48 , characterized in that the compressed gas-based energy conversion device is or has a compressed gas energy conversion device, which has at least one group of two, one of said compressed gas energy conversion heat exchanger devices and one of said compressed gas energy conversion heat exchanger device precursor devices, which of the just mentioned compressed gas energy conversion heat exchanger device is operatively connected upstream as a preliminary stage. Controllable drive device Claim 49 , characterized in that the compressed gas energy conversion device has two or three or four or five or six or more of said groups of two, these groups of two being combined with one another and interconnected. Controllable drive device Claim 49 or after Claim 50 , characterized in that said groups of two are connected in series and/or in parallel. Controllable drive device according to one of Claims 49 until 51 , which also includes all the features of the Claim 25 having, characterized in that the compressed gas energy conversion device has the compressed gas energy conversion device (50), which of the or mentioned groups of two is operatively preceded as a preliminary stage. Controllable drive device according to one of Claims 49 until 52 , characterized in that the compressed gas energy conversion device has a gas reservoir, from which the compressed gas energy conversion device, preferably, if present, the compressed gas energy conversion device, gas can be supplied via a pressure reducer. Controllable drive device Claim 53 , which also includes all the features of at least one of Claims 14 until 24 characterized in that the hydraulic piston device (1) is provided for filling the gas storage tank with compressed gas. Controllable drive device according to any one of the preceding claims, characterized in that the gas is air and/or biogas and/or methane and/or any hydrocarbon gas and/or a mixture of hydrocarbon gases and/or a mixture of air and one or more hydrocarbon gases. Controllable drive device according to one of the preceding claims, characterized in that the liquid is oil.

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