DE102016108026B4 - Compressor for compressing a gas - Google Patents

Abstract

The present invention relates to a compressor (101) for compressing a gas, with a piston working space (105) which is delimited by an inner compressor wall (133), the inner compressor wall (133) being closed by a compression face (111), with at least one gas channel (107), which is guided through the compressor inner wall (133) to the piston working chamber (105) and is designed to supply gas to the piston working chamber (105), with a compressor piston (103) which is movably supported and designed in the piston working chamber (105), to compress the gas supplied to the piston working space (105) through the gas channel (107) with a piston face (109) against the compression face (111), and with a liquid channel (115) for guiding a liquid, the liquid channel (115) passing through the compressor inner wall (133) is guided to the piston working chamber (105) and is formed, the liquid (137) over the compressor inner wall (133 ) to the piston face (109).

Description

This invention relates to a compressor for compressing a gas.

A gas can be compressed by a compressor during a compression process. During the compression process, the volume of the gas is reduced and the gas is heated as a result.

Particularly effective compressors are piston compressors which have a piston working space in which a movably mounted compressor piston is arranged. A movement of the compressor piston in the piston working space compresses the gas present in the piston working space. Here, the gas is compressed by a movement of a piston face of the compressor piston against a compression face of an inner wall of the compressor. The compressed gas is then expelled from the piston working space and the compression process can be repeated. The heat generated during the compression process is mostly unused and released to the outside of the compressor via the inner wall of the compressor.

Gaseous hydrogen can be compressed in a compressor, and the compressed hydrogen obtained can then be used in fuel cells. Fuel cells can be used to generate electricity by oxidizing hydrogen with oxygen. An essential and critical aspect when using fuel cells is the storage or storage of hydrogen, which is explosive in the presence of oxygen.

So far, a number of hydrogen storage processes have been investigated: adsorptive, absorptive, as a liquid, as a highly compressed gas. For short usage cycles, e.g. in the pressure tanks of hydrogen-powered vehicles, hydrogen is stored in gaseous form in pressure vessels. In order to ensure effective gaseous storage of the hydrogen in pressure vessels, the hydrogen must be compressed, the pressure of the gaseous hydrogen stored in the pressure vessels being in particular up to 800 bar. In order to ensure effective compression of the hydrogen, powerful compressors are used which release large amounts of heat during the compression process of the hydrogen.

The DE 357 858 A discloses a method and apparatus for cooling air and gas compressors.

The DE 697 15 435 T2 discloses an apparatus for regulating the temperature of a gas and in particular an apparatus which regulates the gas temperature by spraying liquid into the gas.

The U.S. 2,404,660 A discloses a compressor for compressing air and other gases.

It is therefore the object of the present invention to effectively dissipate the heat released during a compression process of a gas from the compressor.

This object is achieved by the objects with the features according to the independent claims. Advantageous embodiments are the subject matter of the description, the figures and the dependent claims.

According to a first aspect of the invention, the object is achieved by a compressor for compressing a gas, with a piston working space which is delimited by a compressor inner wall, the compressor inner wall being closed off by a compression face, at least one gas channel which leads through the compressor inner wall to the piston working space and is designed to supply gas to the piston working chamber, a compressor piston which is movably supported in the piston working chamber and is designed to compress the gas supplied to the piston working chamber through the gas channel with a piston face against the compression face, and a liquid channel for guiding a liquid, the liquid channel is guided through the compressor inner wall to the piston working chamber and is designed to deliver the liquid via the compressor inner wall to the piston face.

This achieves the technical advantage, for example, that the compressor enables particularly advantageous compression of the gas in the piston working space and that the heat generated during the compression of the gas can be effectively transferred to the liquid in the piston working space.

The liquid supplied to the piston working chamber through the liquid channel flows on the compressor inner wall in the piston working chamber, in particular downward, and collects on the piston face of the compressor piston. Since the liquid is thus in contact with the inner wall of the compressor and with the piston face of the compressor piston, the liquid can effectively absorb the heat generated during the compression of the gas. This allows the heat generated during the compression process to be effective are discharged, and the compressor, in particular the compressor inner wall and the piston face of the compressor piston, are effectively cooled. In addition, the liquid on the piston front side can effectively seal the compressor piston in a gastight manner against the inner wall of the compressor.

The liquid heated during the compression of the gas can be discharged from the piston working space together with the compressed gas. The compressor is usually arranged in a system with several elements in order to supply the compressed gas to the other elements. Here, the heated liquid removed from the piston working space in one element of the system can give off the amount of heat absorbed and thus contribute to a positive energy balance for the entire system.

In particular, the compressor is oriented vertically in order to enable an effective compression of a gas and an effective discharge of the compressed gas and the liquid from the piston working space. The vertical orientation of the compressor means that the compressor piston has a longitudinal axis which is arranged perpendicular to the installation plane of the compressor, so that the compressor piston moves the piston face against the force of gravity acting on the compressor piston when the gas is compressed.

An exemplary system is a dehydrator for dehydrating a liquid hydrogen carrier. In this case, gaseous hydrogen is compressed by the compressor in order to store the compressed gaseous hydrogen, for example in a hydrogen pressure vessel, for further use. In order to effectively use the heat generated during the compression process of the hydrogen, a liquid hydrogen carrier, which can reversibly bind and release hydrogen, is supplied to the piston working space as a liquid. The liquid hydrogen carrier flows along the inner wall of the compressor to the piston face and absorbs the heat generated during the compression of the gaseous hydrogen. The heated liquid hydrogen carrier is then fed to the dehydrating device. In the dehydration device, the heated liquid hydrogen carrier can release the stored hydrogen without any additional energy supply, with the released hydrogen being able to be supplied again to the compressor for a new compression process. In this way, a particularly effective dehydrogenation process of the liquid hydrogen carrier and a particularly effective compression of the gaseous hydrogen can be ensured.

In an advantageous embodiment of the compressor, an outlet valve for discharging the compressed gas and the liquid is arranged in the compression face.

As a result, for example, the technical advantage is achieved that the compressed gas and the liquid can be effectively discharged jointly from the piston working space through the outlet valve. In this case, the outlet valve can comprise a pressure valve which is designed to release the outlet when the pressure in the piston working space reaches a system pressure outside the piston working space, whereby it can be ensured that the compressed gas is only discharged from the piston working space together with the liquid, when the gas is sufficiently compressed.

In an advantageous embodiment of the compressor, the piston working chamber can be supplied with an adjustable ratio of gas and liquid through the gas channel and through the liquid channel, and the compressor is designed to discharge gas and liquid in the adjustable ratio through the outlet valve from the piston working chamber.

As a result, for example, the technical advantage is achieved that by varying the ratio of gas and liquid, the amount of heat transferred between gas and liquid in the piston working space can be varied and thus the heat transfer properties of the compressor can be adapted to the system. If, after the compression process, the compressed gas released by the compressor and the heated liquid are to be used in a downstream chemical process, an advantageously set ratio of gas and liquid enables a particularly advantageous reaction yield in the chemical process.

In an advantageous embodiment of the compressor, the liquid channel is designed to deliver the liquid to the inner wall of the compressor in such a way that the liquid flows under the influence of gravity as a falling liquid film along the inner wall of the compressor towards the piston face.

In this way, for example, the technical advantage is achieved that a particularly effective heat transfer from the compressor inner wall to the liquid can take place due to the liquid fall film flowing downward on the compressor inner wall under the influence of gravity. As a result, the heat generated during the compression of the gas can be effectively absorbed by the liquid, as a result of which the inner wall of the compressor is effectively cooled. The liquid flowing downward in the piston working space as a falling liquid film flows to the piston face, where the liquid collects. The liquid on the piston face can also effectively absorb heat from the compressor piston and thereby effectively cool the compressor piston during the compression of the gas.

In an advantageous embodiment of the compressor, the compressor piston is laterally sealed in a gas-tight manner against the inner wall of the compressor by the liquid.

This achieves the technical advantage, for example, that the gas-tight sealing of the compressor piston can prevent an uncontrolled outflow of the gas from the piston working space. In order to ensure a movable mounting of the compressor piston in the piston working space, there are piston gaps laterally between the compressor piston and the compressor inner wall through which gas can escape from the piston working space in an uncontrolled manner. Since the liquid is present at the piston face of the compressor piston, the liquid layer thereby seals the compressor gap in a gas-tight manner, which can prevent the gases from escaping from the piston working space.

According to the invention, a circumferential channel is formed in the inner wall of the compressor, the liquid channel being fluidically connected to the circumferential channel and designed to deliver the liquid to the circumferential channel, and the circumferential channel being designed to deliver the liquid via a channel edge to the compressor inner wall.

This achieves the technical advantage, for example, that the circumferential channel arranged on the inner wall of the compressor ensures that the liquid is discharged from the channel circumferentially via the inner wall of the compressor to the piston face. The liquid flows through the liquid channel into the circumferential channel and fills the circumferential channel. If the circumferential channel is filled with liquid, the liquid flows over the edge of the circumferential channel evenly and circumferentially along the inner wall of the compressor to the piston face. Since the liquid flows circumferentially along the inner wall of the compressor, a particularly uniform and thus effective heat transfer can take place from a large area of the inner wall of the compressor to the liquid.

In an advantageous embodiment of the compressor, the liquid channel is led through the compression face to the piston working space, or the liquid channel is led laterally through the inner wall of the compressor.

As a result, for example, the technical advantage is achieved that the liquid can be effectively fed to the piston working space through the liquid channel. If the liquid channel is led through the compression face to the piston working space, the liquid flows from above through the compression face to the compressor inner wall and can effectively flow over the compressor inner wall to the piston face. If the liquid channel is led laterally through the inner wall of the compressor, the liquid can be received, for example, in a circumferential channel and can flow from the circumferential channel over the inner wall of the compressor to the piston face.

In an advantageous embodiment of the compressor, the compressor also has a liquid distribution channel which is fluidically connected to the liquid channel and is provided to supply the liquid to the liquid channel.

In this way, for example, the technical advantage is achieved that the liquid distribution channel provides a sufficient liquid reservoir to ensure a constant and effective supply of liquid through the liquid channel. The liquid distribution channel can in particular be arranged on the compression face of the compressor, so that the liquid can be effectively conducted from above from the liquid distribution channel through the liquid channel passed through the compression face to the compressor inner wall and from there to the piston face.

In an advantageous embodiment of the compressor, the gas channel is led through the compression face to the piston working chamber.

This achieves the technical advantage, for example, that an effective supply of gas from above into the piston working space can be ensured through the gas channel.

In an advantageous embodiment of the compressor, the compression face has a wall contour, the wall contour being designed in particular as a conical wall contour, rounded wall contour or a horizontal wall contour.

In this way, for example, the technical advantage is achieved that the wall contour on the compression face allows the compressed gas and the heated liquid is ensured from the piston working space. If a discharge valve is arranged on the compression face of the compressor, the liquid is directed against the compression face during the compression of the gas. By means of an advantageously shaped wall contour, in particular a conical wall contour, rounded wall contour or horizontal wall contour, the liquid conveyed to the wall contour can be effectively guided to the outlet valve, and splashing of the liquid in the piston working space can be avoided.

In an advantageous embodiment of the compressor, the piston working chamber comprises a first piston working chamber and a second piston working chamber, which are delimited by the compressor inner wall, the compressor inner wall being closed off at the first piston working chamber by a first compression face, the compressor inner wall being closed off at the second piston working chamber by a second compression face The compressor piston has a first piston section which is movably mounted between the first piston working chamber and the second piston working chamber, the first piston section being designed to compress gas in the first piston working chamber with a lower first piston face against the first compression face in a first compression direction , and wherein the first piston section is formed, gas in the second piston working chamber with an upper first piston end face against the second compressor sion front side to compress in a second compression direction opposite to the first compression direction.

As a result, for example, the technical advantage is achieved that the movable arrangement of the first piston section between the first and second piston working space enables particularly advantageous compression of the gas in the compressor. During a first compression process, the first piston section compresses the gas in the first piston interior in a first compression direction with the lower, first piston face against the first compression face. The movement of the first piston section in the first compression direction increases the volume in the second piston working chamber.

Then, during a second compression process, the first piston section is moved counter to the first compression direction in a second compression direction. As a result of the movement of the first piston section in the second compression direction, the first piston section compresses the gas in the second piston working space during the second compression process. This increases the volume in the first piston working space.

Thus, by moving the first piston section in the first compression movement direction or in the second compression direction, the gas in the first piston working space and in the second piston working space is alternately compressed. If the gas is conveyed from the first piston working chamber into the second compression chamber according to the direction of movement of the first piston section after the first compression process, a particularly effective compression of the gas can be achieved during a second compression process following the first compression process. Furthermore, liquid can be conveyed from the first piston working chamber into the second piston working chamber in order to ensure an effective heat transfer to the liquid. In addition, the compressor can have a further first piston working chamber and a further second piston working chamber, between which a second piston section of the compressor piston is movably mounted in order to additionally compress gas in the further first and second piston interior, whereby particularly high pressures of the compressed gas during several successive compression processes can be achieved.

In an advantageous embodiment of the compressor, the first piston working chamber and the second piston working chamber are fluidically connected by a first piston connection in order to supply compressed gas and liquid through the first piston connection from the first piston working chamber to the second piston working chamber.

This achieves the technical advantage, for example, that gas and liquid compressed by the first piston connection can be conveyed from the first piston working chamber into the second piston working chamber after the first compression process in the low pressure phase of the second piston working chamber. During a second compression process following the first compression process, the gas in the second piston working space can be compressed further, and the heat released in the process can be effectively absorbed by the liquid.

In an advantageous embodiment of the compressor, a gas valve is arranged on the gas channel, the gas valve being designed to fluidically block the gas channel during the compression of the gas in the piston working chamber, and the gas valve being designed to fluidically block the gas channel during a low-pressure phase in the piston working chamber release in order to supply gas to the piston working space.

This achieves the technical advantage, for example, that the supply of gas into the piston working space can be effectively controlled. The gas valve only releases the gas channel in the low-pressure phase when the compressor piston moves downwards in the piston working space and gas can thus be effectively sucked in through the gas channel. In this case, the gas is fed to the piston working chamber together with the liquid conveyed through the liquid channel during the low-pressure phase. The gas valve can thus prevent the gas from being forced out of the piston working space through the gas channel during the compression process.

In an advantageous embodiment of the compressor, a liquid valve is arranged on the liquid channel, the liquid valve being designed to fluidically block the liquid channel during the compression of the gas in the piston working space, and the liquid valve being designed to fluidically block the liquid channel during a low-pressure phase in the piston working space release in order to supply fluid to the piston working space.

In this way, for example, the technical advantage is achieved that the supply of liquid into the piston working chamber can be advantageously controlled. In this case, the liquid valve only releases the liquid channel in the low-pressure phase when the compressor piston moves downwards in the piston working space and liquid can thus be sucked in through the liquid channel. In this case, the liquid is fed to the piston working chamber at the same time as the gas conveyed through the gas channel during the low-pressure phase. The liquid valve can thus prevent liquid from being pressed out of the piston working space through the liquid channel during the compression process.

In an advantageous embodiment of the compressor, a liquid pump is arranged on the compressor which is designed to pump the liquid through the liquid channel into the piston working space.

This achieves the technical advantage, for example, that the liquid pump can provide a flow pressure which is sufficient to pump the liquid through the liquid channel into the piston working space.

In an advantageous embodiment of the compressor, a drive for driving the liquid pump is arranged on the liquid pump, the drive being designed to drive the compressor piston and the liquid pump together.

This achieves the technical advantage, for example, that the drive for jointly driving the liquid pump and the compressor piston enables particularly energy-efficient driving of the two components of the compressor. As a result, a further drive for driving the liquid pump or the compressor piston can be dispensed with. For example, the drive can be connected to both the liquid pump and the compressor piston by a single drive shaft.

In an advantageous embodiment of the compressor, the compressor has a first compressor stage and a second compressor stage, the first compressor stage having a first piston working chamber which is delimited by the compressor inner wall, the compressor inner wall being closed by a first compression face, the first compressor stage at least one Has gas channel which is guided through the compressor inner wall to the first piston working chamber and is designed to supply gas to the first piston working chamber, the compressor piston having a first piston section which is movably supported and designed in the first piston working chamber, the gas supplied to the first piston working chamber through the gas channel to compress with a first piston face against the first compression face, the first compressor stage having a first liquid channel for guiding a liquid, the first liquid Keitskanal is led through the compressor inner wall to the first piston working chamber and designed to discharge the liquid via the compressor inner wall to the first piston face, the first compressor stage in the first compression face, a first outlet valve for discharging the compressed gas and the liquid from the first compressor stage is arranged, wherein the first outlet valve is fluidically connected to a first stage supply, the second compressor stage having a second piston working space which is delimited by the compressor inner wall, the compressor inner wall being closed by a second compression face, the second compressor stage being fluidically connected to a second stage supply, wherein the second stage feed is guided through the inner wall of the compressor to the second piston working chamber and is designed to feed gas and liquid to the second piston working chamber, where in which the compressor piston has a second piston section which is movably mounted in the second piston working chamber and is designed to compress the gas supplied to the second piston working chamber through the second stage feed with a second piston face against the second compression face, the second Compressor stage in the second compression end face a second outlet valve is arranged for discharging the compressed gas and the liquid from the second compressor stage.

This achieves the technical advantage, for example, that the two-stage compressor enables particularly effective compression of gas, in particular hydrogen gas. Thus, through the two stages of the two-stage compressor, a higher pressure of the gas can be achieved, and the heat generated during the compression process can be transferred particularly effectively to the liquid, whereby a particularly advantageous heating of the liquid can take place. The two-stage compressor can be fluidly connected to a further two-stage compressor. Here, the first stage of the first two-stage compressor is fluidically connected to a stage of the further two-stage compressor through the first stage supply in order to supply compressed gas and heated liquid from the first two-stage compressor to the second two-stage compressor. Another stage of the further two-stage compressor is connected through the second stage feed to the second stage of the first two-stage compressor in order to feed compressed gas and heated liquid from the further two-stage compressor to the second stage of the first two-stage compressor. Thus, with a time-shifted control of the compressor piston of the first two-stage compressor and the further compressor piston of the further two-stage compressor, the gas compressed during a high pressure phase in the first two-stage compressor can be supplied to the further two-stage compressor during a low-pressure phase of the further two-stage compressor, and that during a High-pressure phase in the further two-stage compressor, compressed gas can be supplied to the first two-stage compressor during a low-pressure phase of the first two-stage compressor in order to ensure an effective compression of gas.

In an advantageous embodiment of the compressor, the liquid comprises a liquid organic hydrogen carrier (LOHC), the liquid hydrogen carrier being designed to reversibly bind and release hydrogen, the gas comprising hydrogen, and the compressor being designed to supply hydrogen compress to get compressed hydrogen.

This has the technical advantage, for example, that a liquid hydrogen carrier to which hydrogen is bound can absorb heat particularly effectively. The heated liquid hydrogen carrier can effectively release the bound hydrogen during a subsequent dehydrogenation process without an additional amount of heat having to be supplied to the liquid hydrogen carrier. The liquid hydrogen carrier, in particular the liquid organic hydrogen carrier (LOHC), on the one hand provides an effective heat transfer medium and on the other hand provides a reservoir of hydrogen which is bound to the liquid hydrogen carrier and can be effectively released during the dehydration process.

In an advantageous embodiment of the compressor, the liquid hydrogen carrier comprises a hydrocarbon compound with an extended π-conjugated system, the hydrocarbon compound with the extended π-conjugated system being selected in particular from a group comprising aromatic hydrocarbons, polycyclic aromatic hydrocarbons, polycyclic heteroaromatic Hydrocarbons, π-conjugated organic polymers or a combination thereof, and in particular is selected from the group comprising N-ethylcarbazole, dibenzyltoluene, benzyltoluene or mixtures thereof.

As a result, for example, the technical advantage is achieved that particularly efficient liquid hydrogen carriers are provided by the compounds mentioned. In the case of unsaturated hydrocarbon compounds with extensive π-conjugated systems, a large number of unsaturated carbon-carbon double bonds are available, which can react with hydrogen molecules to form saturated carbon-carbon double bonds, whereby hydrogen can be stored. The high ratio of stored hydrogen molecules per hydrocarbon compound enables effective hydrogen storage in a limited volume of liquid. In addition, the compounds mentioned have an advantageous heat capacity, as a result of which large amounts of heat can be effectively stored and released again.

According to a second aspect of the invention, the object is achieved by a dehydrogenation system for dehydrating a liquid hydrogen carrier (LOHC), with the compressor according to the preceding embodiments, wherein the compressor can be supplied with gaseous hydrogen via the gas channel, wherein the compressor can be supplied with liquid hydrogen carrier via the liquid channel is, and wherein the compressor is designed to compress the gaseous hydrogen in order to obtain compressed hydrogen, a gas cleaning device which is fluidly connected to the compressor and designed, the compressed To separate hydrogen from the liquid hydrogen carrier, and a dehydrogenation device which is fluidly connected to the gas cleaning device and is designed to release hydrogen from the liquid hydrogen carrier, the dehydrogenation device being fluidically connected through the gas channel to the compressor in order to supply the released hydrogen to the compressor again .

This achieves the technical advantage, for example, that the dehydrogenation system enables effective dehydrogenation of the liquid hydrogen carrier to release gaseous hydrogen in the dehydrogenation device and effective compression of gaseous hydrogen in the compressor with little energy consumption. The heat generated during the compression process of hydrogen in the compressor is absorbed by the liquid hydrogen carrier. The compressed hydrogen and the heated liquid hydrogen carrier are then discharged from the piston working space and fed to the gas cleaning device. In the gas cleaning device, the compressed gaseous hydrogen is separated from the liquid hydrogen carrier. The compressed gaseous hydrogen can then be discharged from the gas cleaning device and stored for further use. The liquid hydrogen carrier separated from the compressed gaseous hydrogen and heated can then be fed to the dehydrogenation device in order to release gaseous hydrogen from the liquid hydrogen carrier. As a result of the upstream heating of the liquid hydrogen carrier in the compressor, the dehydrogenation of the liquid hydrogen carrier can take place in the dehydrogenation device without additional expenditure of energy. The dehydrated, low-energy form of the liquid hydrogen carrier can then be separated from the released gaseous hydrogen, and the released gaseous hydrogen can be fed back to the compressor in a cycle. The released gaseous hydrogen can be compressed again by the compressor and fed back into the circuit.

In an advantageous embodiment of the dehydration system, the liquid channel is fluidically connected to a liquid reservoir for storing an energy-rich, hydrated form of the liquid hydrogen carrier.

This achieves the technical advantage, for example, that an energy-rich, hydrated form of the liquid hydrogen carrier, which has bound hydrogen, can be stored in the liquid reservoir and can be fed to the piston working space of the compressor through the liquid channel.

In an advantageous embodiment of the dehydration system, the dehydration device is fluidly connected to a further liquid storage device, the further liquid storage device being designed to store a dehydrated, low-energy form of the liquid hydrogen carrier after the gaseous hydrogen has been released.

This achieves the technical advantage, for example, that the liquid hydrogen carrier can be effectively stored in the further liquid storage device after the gaseous hydrogen has been released. After the gaseous hydrogen has been released, the liquid hydrogen carrier stored in the liquid reservoir has a low-energy form in which the liquid hydrogen carrier has a reduced amount of bound hydrogen compared to the high-energy form of the liquid hydrogen carrier. The low-energy form of the liquid hydrogen carrier can then be removed from the further liquid reservoir and recharged with gaseous hydrogen during a hydrogenation process.

In an advantageous embodiment of the dehydrogenation system, the gas cleaning device is fluidically connected to a hydrogen pressure vessel, the hydrogen pressure vessel being designed to store the compressed hydrogen after separation from the liquid hydrogen carrier.

This achieves the technical advantage, for example, that the hydrogen pressure vessel enables the compressed gaseous hydrogen to be effectively stored and ensures that the hydrogen from the hydrogen pressure vessel can, if required, be made available to an element which consumes the gaseous hydrogen.

According to a third aspect of the invention, the object is achieved by a hydrogenation system for hydrogenating a liquid hydrogen carrier (LOHC) with the compressor according to the preceding embodiments, wherein the compressor can be supplied with gaseous hydrogen via the gas channel, wherein the compressor can be supplied with liquid hydrogen carrier via the liquid channel , wherein the compressor is designed to compress the gaseous hydrogen in order to obtain compressed hydrogen, wherein the compressor has a catalyst which is arranged and designed on the compressor inner wall and / or on the piston face, the chemical bond of hydrogen to the liquid hydrogen carrier to catalyze.

This achieves the technical advantage, for example, that the hydrogenation system enables an effective hydrogenation of a dehydrated, low-energy form of the liquid hydrogen carrier with gaseous hydrogen in the compressor, whereby a hydrogenated high-energy form of the liquid hydrogen carrier is obtained. Here, the catalyst is arranged on the inner wall of the compressor and / or on the piston face of the compressor piston and can come into effective contact with both the gaseous hydrogen and the liquid hydrogen carrier, whereby the chemical bond of hydrogen to the liquid hydrogen carrier can be effectively catalyzed. The heat generated during the compression process of hydrogen and the hydrogenation reaction in the compressor is absorbed by the liquid hydrogen carrier. The heated, hydrated and high-energy form of the liquid hydrogen carrier is then discharged from the piston working space and can be stored.

In an advantageous embodiment, the compressor is fluidly connected to a liquid reservoir for storing the liquid hydrogen carrier in a hydrated, high-energy form.

This achieves the technical advantage, for example, that the high-energy, hydrogenated form of the liquid hydrogen carrier can be fed from the compressor to the liquid storage device in order to ensure effective storage of the liquid hydrogen carrier with chemically bound hydrogen.

In an advantageous embodiment, the liquid channel is fluidically connected to a further liquid reservoir, the further liquid reservoir being designed to store the liquid hydrogen carrier in a dehydrated, low-energy form.

This achieves the technical advantage, for example, that the low-energy, dehydrated form of the liquid hydrogen carrier from the additional liquid storage device can be fed to the compressor, in particular in an optimal ratio to the gaseous hydrogen, in order to ensure an effective chemical bond between the gaseous hydrogen and the liquid hydrogen carrier in the piston working space enable.

In a further advantageous embodiment, the catalyst comprises catalyst particles and / or a catalyst foam, and in particular comprises a transition metal catalyst.

This achieves the technical advantage, for example, that the catalyst particles and / or the catalyst foam catalyze a particularly effective hydrogenation of the liquid hydrogen carrier with gaseous hydrogen.

In a further advantageous embodiment, the inner wall of the compressor is designed as a double wall, the double wall having a fluid channel for cooling the inner wall of the compressor.

This achieves the technical advantage, for example, that fluid can be pumped through the fluid channel through the fluid channel accommodated in the double wall, with the fluid, in particular a liquid, in particular water, effectively absorbing heat generated when hydrogen is chemically bonded to the liquid hydrogen carrier and can lead away.

In a further advantageous embodiment, the compressor piston has a piston working chamber cooling system which is designed to cool the compressor piston and the piston working chamber.

In this way, for example, the technical advantage is achieved that the compressor piston can be advantageously cooled by the piston working chamber cooling, whereby the piston working chamber is also effectively cooled.

Embodiments of the invention are shown in the drawings and are described in more detail below.

• 1 Dehydrierungssystem zum Dehydrieren eines flüssigen Wasserstoffträgers (LOHC);
• 2 Kompressor zum Verdichten von Wasserstoffgas gemäß einer Ausführungsform;
• 3 Zwei zweistufige Kompressoren zum Verdichten von Wasserstoffgas;
• 4 Einen mehrstufigen Kompressor zum Verdichten von Wasserstoffgas; und
• 5 Hydrierungssystem zum Hydrieren eines flüssigen Wasserstoffträgers (LOHC).

Show it:

• 1 Dehydration system for dehydrating a liquid hydrogen carrier (LOHC);
• 2 Compressor for compressing hydrogen gas according to an embodiment;
• 3 Two two-stage compressors for compressing hydrogen gas;
• 4th A multi-stage compressor for compressing hydrogen gas; and
• 5 Hydrogenation system for hydrogenating a liquid hydrogen carrier (LOHC).

1 shows a dehydration system for dehydrating a liquid hydrogen carrier (LOHC - Liquid Organic Hydrogen Carrier). The liquid hydrogen carrier comprises organic hydrocarbon compounds, which in particular have an extensive π-conjugated system. For example, the liquid hydrogen carrier can be aromatic hydrocarbons, polycyclic aromatic hydrocarbons, polycyclic heteroaromatic hydrocarbons, π-conjugated organic polymers, or a combination thereof and in particular are selected from the group comprising N-ethylcarbazole, dibenzyltoluene, benzyltoluene or mixtures thereof.

A dehydrated low-energy form of the liquid hydrogen carrier is reversibly converted into a hydrogenated high-energy form of the liquid hydrogen carrier by means of catalyzed hydrogenation by hydrogen. In a, for example, differently catalyzed reverse reaction by increasing the temperature and / or reducing the hydrogen pressure, hydrogen is recovered from the hydrogenated, high-energy form of the liquid hydrogen carrier to form the dehydrated low-energy form of the liquid hydrogen carrier. The reaction is reversible, so that the liquid hydrogen carrier can be circulated from a low-energy to a high-energy location without consuming itself. The liquid hydrogen carrier is a carrier for energy in the form of hydrogen.

Liquid hydrogen carriers that can be used particularly advantageously allow a reversible conversion for binding or releasing hydrogen under technically relevant conditions, such as, for example, at pressures and temperatures that can be represented in a technically simple manner. Hydrogen storage in liquid hydrogen carriers has the advantage that the liquid hydrogen carriers are liquid under the process conditions used, are unpressurized in storage, and their physicochemical properties are very similar to conventional liquid fuels. Therefore pumps can be used for transport and containers for storage in the field of fuel and fuel technology. The hydrogen storage in chemically bound form in an organic liquid allows a pressureless storage under normal conditions over long periods of time without significant loss of hydrogen.

When hydrogen is released from the liquid hydrogen carrier, the released hydrogen is stored in a gaseous state in pressure vessels for short usage cycles, e.g. for use in hydrogen-powered vehicles. Here, the hydrogen obtained from the liquid hydrogen carrier by dehydrogenation is compressed for storage in a hydrogen pressure vessel, in particular compressed to a pressure of up to 800 bar.

A dehydration system 100 to dehydrate a liquid hydrogen carrier (LOHC) has a compressor 101 for compressing hydrogen. The compressor 101 has a compressor piston for this purpose 103 on, which is in a piston working space 105 of the compressor 101 is movably mounted. When the piston working space 105 through an in 1 not shown gas duct 107 gaseous hydrogen is supplied, the compressor piston moves 103 in the piston working space 105 to the gaseous hydrogen with a piston face 109 of the compressor piston 103 against a compression face 111 of the compressor 101 to condense.

The dehydration system 100 also has a liquid reservoir 113 for storing a hydrogenated, high-energy form of the liquid hydrogen carrier, with hydrogen being bound to the liquid hydrogen carrier in the hydrogenated high-energy form of the liquid hydrogen carrier. The liquid storage 113 is with the piston working space 105 through a fluid channel 115 fluidly connected to the liquid hydrogen carrier to the piston groove 105 to feed.

During the compression of the gaseous hydrogen by the compressor 101 becomes heat in the piston working space 105 released. The heat released is in the piston working space 105 transferred to the liquid hydrogen carrier, whereby the liquid hydrogen carrier is heated.

After the compression of the gaseous hydrogen, the compressed gaseous hydrogen and the heated liquid hydrogen carrier through a compressor line 117 to a gas cleaning device 119 directed. The gas cleaning device 119 is designed to separate the compressed gaseous hydrogen from the hydrogenated, high-energy form of the liquid hydrogen carrier. The compressed gaseous hydrogen is used by the gas cleaning device 115 through a hydrogen storage line 121 to a hydrogen pressure vessel 123 in which the compressed gaseous hydrogen can be stored until further use.

The heated, hydrated, high-energy form of the liquid hydrogen carrier is removed from the gas cleaning device 119 through a dehydration line 125 to a dehydrator 127 directed. In the dehydrator 127 the heated hydrogenated high-energy form of the liquid hydrogen carrier can release gaseous hydrogen at normal pressure, the hydrogenated high-energy form of the liquid hydrogen carrier being converted into a dehydrated low-energy form of the liquid hydrogen carrier. In the dehydrated low-energy form of the liquid hydrogen carrier, a reduced amount of hydrogen is bound to the liquid hydrogen carrier compared to the hydrogenated high-energy form of the liquid hydrogen carrier. By heating the hydrated high energy form of the liquid hydrogen carrier in the compressor 101 can cause the release of the Start gaseous hydrogen from the hydrogenated, high-energy form of the liquid hydrogen carrier without any additional energy supply.

The dehydrated, low-energy form of the liquid hydrogen carrier produced during the dehydrogenation process can be discharged through a hydrogen carrier discharge line 129 into another liquid reservoir 131 be convicted. Here, the in the further liquid storage 131 stored dehydrated low-energy form of the liquid hydrogen carrier in another in 1 step, not shown, from the further liquid reservoir 131 removed and reloaded with hydrogen, and thus again converted into the hydrogenated, high-energy form of the liquid hydrogen carrier.

The one in the dehydrator 127 Gaseous hydrogen released at normal pressure can pass through the gas duct 107 now the piston working space again 105 of the compressor 101 are supplied to the gaseous hydrogen by the compressor 101 to condense.

Thus, in 1 a dehydrogenation system for dehydrogenating a liquid hydrogen carrier, in which the released gaseous hydrogen is returned to the compressor within a cycle 101 can be fed to by the compressor 101 to be condensed. The heat generated during the compression of the hydrogen can in turn be transferred to the liquid hydrogen carrier, whereby that of the dehydrogenation device 127 supplied heated liquid hydrogen carrier in the dehydration device 127 can release gaseous hydrogen particularly effectively.

2 FIG. 10 shows a compressor for compressing hydrogen gas according to an embodiment. The compressor 101 has a piston working space 105 on, which by a compressor inner wall 133 is limited. The inner wall of the compressor 133 delimits the piston working space 105 especially in relation to an outside area 135 of the compressor 101 from. Here is the inner wall of the compressor 133 through a compression face 111 completed. In the piston working space 105 is a compressor piston 103 arranged movably mounted. Through the inner wall of the compressor 133 is a gas duct 107 to the piston working space 105 out, which is formed, the piston working space 105 to supply a hydrogen gas. Here is the gas duct 107 especially due to the compression face 111 to the piston working space 105 led to the gaseous hydrogen from above into the piston working space 105 to promote.

After hydrogen in the piston working space 105 the compressor piston moves 103 in the piston working space 105 up to the gaseous hydrogen in the piston working space 105 to condense. Here, the gaseous hydrogen with a piston face 109 of the compressor piston 103 against the compression face 111 condensed.

The compressor 101 also has a fluid channel 115 for guiding a liquid 137 on. The liquid 137 comprises in particular a liquid hydrogen carrier, in particular a hydrated, high-energy form of the liquid hydrogen carrier. The fluid channel 115 is through the inner wall of the compressor 133 to the piston working space 105 out and is formed, the liquid 137 via the inner wall of the compressor 133 to the piston face 109 to give up. Here, the liquid hydrogen carrier becomes the piston working space, in particular during a low-pressure phase of the compression process 105 fed. In the inner wall of the compressor 133 is a circumferential channel 139 educated. The fluid channel 115 is with the surrounding gutter 139 fluidly connected to the through the liquid channel 115 guided liquid hydrogen carrier to the circumferential channel 139 submit. The surrounding channel 139 has a gutter edge 141 on. The liquid hydrogen carrier flows through the liquid channel 115 in the surrounding channel 139 and fills the surrounding channel 139 on, with the liquid hydrogen carrier over the edge of the channel 141 flows and in the piston working space 105 via the inner wall of the compressor 133 flows downwards. The liquid hydrogen carrier forms a falling liquid film 143 which is under the influence of gravity along the inner wall of the compressor 133 to the piston face 109 flows downwards. On the piston face 109 of the compressor piston 103 the liquid hydrogen carrier collects and seals the compressor piston 103 laterally against the inner wall of the compressor 133 gastight. Thus, the liquid hydrogen carrier serves as a barrier medium, which prevents a loss of gaseous hydrogen through the piston gap 145 between the compressor piston 103 and the inner wall of the compressor 133 prevented.

Through the liquid hydrogen carrier, which is on the piston face 109 pending can occur during the compression of the gaseous hydrogen in the piston working chamber 105 resulting heat are advantageously absorbed by the liquid hydrogen carrier. Thus, the liquid hydrogen carrier and the circulating on the compressor inner wall 133 to the piston face 109 falling liquid film flowing downwards 143 of the liquid hydrogen carrier, a large area is available for heat transfer. This results in an advantageous cooling of the Compressor 101 during the compression of hydrogen and in particular the inner wall of the compressor 133 particularly effective cooled.

By moving the compressor piston 103 in the piston working space 105 the gaseous hydrogen with the piston face 109 of the compressor piston 103 against the compression face 111 condensed. This increases the pressure of the gaseous hydrogen in the piston working space 105 on, and by transferring the heat generated during the compression of the hydrogen to the liquid hydrogen carrier, the temperature of the liquid hydrogen carrier is increased.

On a top of the compressor 101 is an exhaust valve 147 arranged, which is formed after the completion of the compression of the gaseous hydrogen, the gaseous hydrogen together with the heated liquid hydrogen carrier from the piston working space 105 to dissipate. Here, the outlet valve 147 be designed in particular as a pressure valve which releases the outlet when the pressure of the compressed hydrogen gas in the piston working space 105 a system pressure outside the piston working space 105 reached.

To the gaseous hydrogen and the high-energy form of the liquid hydrogen carrier effective from the outlet valve 147 to a gas cleaning device 119 to separate the gaseous hydrogen from the liquid hydrogen carrier, is the outlet valve 147 with a compressor line 117 fluidly connected, which in turn with the gas cleaning device 119 is fluidly connected. In 2 is the compressor line 117 and the gas cleaning device 119 not shown. On the outside of the compressor 101 is located on the outlet valve 147 a valve chamber 149 , in which a hydrogen carrier supernatant 151 of the liquid hydrogen carrier is added. The hydrogen carrier supernatant 151 occurs when the liquid hydrogen carrier emerges from the outlet valve 147 and provides an effective seal on the exhaust valve 147 for sure.

Furthermore, an area of the compression face 111 a wall contour 153 have, which is shaped optimized with regard to the compression process. The wall contour 153 can as in 2 is shown as a conical wall contour 153 be formed, or alternatively, as in 2 is not shown as a rounded wall contour 153 or as a horizontal wall contour 153 be trained.

Thus, through the in 2 shown compressor 101 effective compression of gaseous hydrogen in the piston working space 105 and effective heating of a liquid hydrogen carrier takes place, as a result of which the compression of the gaseous hydrogen and the dehydration of the high-energy form of the liquid hydrogen carrier can take place in a particularly energy-efficient manner.

3 shows two two-stage compressors for compressing hydrogen in a sectional view. The first compressor 101 has a first compressor stage 155 and a second compressor stage 157 on, with the first compressor stage 155 and the second compressor stage 157 in the 3 from each other by a dividing line 159 are separated.

The first compressor stage 155 has a compressor inner wall 133 on which a first piston working space 161 and a second piston working space 163 limited. Inside the inner wall of the compressor 133 is a compressor piston 103 arranged vertically, which has a first piston portion 165 and one with the first piston portion 165 connected second piston portion 167 having. The first piston section 165 has a circumferential first piston face 169 on.

After feeding hydrogen through an in 3 gas canaf not shown 107 into the first piston working space 161 , the compressor piston moves 103 within the first compressor stage 155 vertically upwards. This is done by the first piston section 165 the gas in the first piston working space 161 with the first piston face 169 against a first compression face 170 the inner wall of the compressor 133 condensed.

The inner wall of the compressor 133 the first compressor stage 155 also has a first fluid channel 171 on through which a liquid 137 , in particular a hydrated high-energy form of a liquid hydrogen carrier to the first piston working space 161 can be fed. The first fluid channel 171 is with one in the 3 circumferential channel not shown 139 with a gutter edge 141 fluidly connected. The liquid 137 runs on the vertically arranged inner wall of the compressor 133 in the first piston working space 161 downwards, creating a first fall film of liquid 173 forms, and whereby on an upper side of the first piston face 170 forms a layer of liquid.

The liquid layer seals in 3 piston column not shown 145 between the compressor piston 103 and the inner wall of the compressor 133 and enables effective Absorption of heat that arises during the compression process.

The compressed gas, in particular the compressed gaseous hydrogen, and the liquid, in particular the high-energy form of the liquid hydrogen carrier, are extracted from the first piston working space 161 preferably by a circumferential first outlet valve 175 derived and through a first stage feed 177 another two-stage compressor 179 , in particular a fourth compressor stage 181 further two-stage compressor 179 fed.

This is the first compressor stage 155 of the first compressor 101 counter to the fourth compressor stage 181 another compressor 179 operated. This allows the liquid 137 and the compressed hydrogen from the first compressor stage 155 of the first compressor 101 during a high pressure phase through the first stage feed 177 the fourth compressor stage 181 another compressor 179 be supplied in a low pressure phase.

The other two-stage compressor 179 has a third compressor stage 183 and the fourth compressor stage 181 on, with the third compressor stage 183 and the fourth compressor stage 181 in the 3 from each other by another dividing line 185 are separated.

The fourth compressor stage 181 has a compressor inner wall 133 on which a fourth piston working space 187 limited. A fourth piston section 193 furthermore the compressor piston 191 is with a third piston section 189 furthermore the compressor piston 191 connected. The fourth piston section 193 is in the fourth piston working space 187 arranged. After gas, in particular hydrogen, and liquid, in particular a liquid hydrogen carrier, have been supplied through the first stage supply 177 into the fourth piston working space 187 , the fourth piston section moves 193 furthermore the compressor piston 191 within the fourth compressor stage 181 vertically upwards. This is done by the fourth piston section 193 with a fourth piston face 195 the gas, in particular the gaseous hydrogen, in the fourth piston working space 187 condensed.

The liquid hydrogen carrier runs on the vertically arranged inner wall of the compressor 133 in the fourth piston working space 187 downwards, creating a fourth liquid falling film 197 the liquid, in particular the liquid hydrogen carrier, forms, and as a result of which it is on an upper side of the fourth piston end face 195 of the fourth piston section 193 of the second compressor piston 191 a liquid layer, in particular a liquid hydrogen carrier layer, forms.

The gas, in particular the gaseous hydrogen and the liquid, in particular the high-energy form of the liquid hydrogen carrier, are removed from the fourth piston working space after the compression process 187 through a fourth exhaust valve 199 derived.

Another compression process takes place in the third compressor stage 183 another compressor 179 instead of.

The third compressor stage 183 has a compressor inner wall 133 on, which is next to the fourth piston working space 187 a third piston working space 201 limited. Inside the inner wall of the compressor 133 is the other compressor piston 191 arranged vertically, with the further compressor piston 191 the third piston section 189 and the one with the third piston section 189 connected fourth piston section 193 having. The third piston section 189 has a circumferential third piston face 203 on.

The third compressor stage 183 has a third fluid channel 205 on, which through the compressor inner wall 133 Is guided, through which a liquid, in particular an energy-rich form of a liquid hydrogen carrier, the third piston working space 201 can be fed. The third fluid channel 205 is with one in the 3 circumferential channel not shown 139 with a gutter edge 141 fluidly connected. The liquid 137 runs on the vertically arranged inner wall of the compressor 133 in the third piston working space 201 downwards, creating a third liquid falling film 207 forms, and whereby on an upper side of the third piston face 203 forms a layer of liquid.

After feeding hydrogen through an in 3 not shown gas duct 107 into the third piston working space 201 , the other compressor piston moves 191 within the third compressor stage 183 vertically upwards. This is done by the third piston section 189 the gas in the third piston working space 201 with the third piston face 203 condensed.

The compressed gas, in particular the compressed gaseous hydrogen, and the liquid, in particular the high-energy form of the liquid hydrogen carrier, are extracted from the third piston working space 201 by a circumferential third exhaust valve 209 derived and through a second stage feed 211 the second compressor stage 157 of the first two-stage compressor 101 fed.

The second compressor stage 157 of the second compressor 101 has a compressor inner wall 133 on which a second piston working space 163 limited. The first piston section 165 of the compressor piston 103 is with the second piston section 167 of the compressor piston 103 connected. The second piston section 167 is in the second piston working space 163 arranged. After gas, in particular hydrogen, and liquid, in particular a liquid hydrogen carrier, have been supplied through the second stage supply 211 into the second piston working space 163 during the low pressure phase, the second piston section moves 167 of the compressor piston 103 within the second compressor stage 157 vertically upwards. This is done by the second piston section 167 with a second piston face 213 the gas, in particular the gaseous hydrogen, in the second piston working space 163 condensed.

The liquid hydrogen carrier runs on the vertically arranged inner wall of the compressor 133 in the second piston working space 163 downwards, creating a second liquid falling film 215 the liquid, in particular the liquid hydrogen carrier, forms, and as a result of which on an upper side of the second piston end face 213 of the second piston section 167 of the compressor piston 103 a liquid layer, in particular a liquid hydrogen carrier layer, forms.

The compressed gas, in particular the compressed gaseous hydrogen and the liquid, in particular the high-energy form of the liquid hydrogen carrier, are removed from the second piston working space after the compression process 163 through a second exhaust valve 217 derived.

4th shows a multi-stage compressor for compressing hydrogen in a sectional view.

The compressor 101 has a compressor inner wall 133 on which a piston working space 105 limited and in which a compressor piston 103 is mounted vertically movable. With regard to the design of the compressor 101 is based on the embodiments according to 2 , 3 and 4th referenced.

The compressor piston 103 has a first piston portion 165 and one with the first piston portion 165 vertically connected second piston section 167 on. The first piston section 165 has a circumferential lower first piston face 219 on and a circumferential upper first piston face 221 on. The second piston section 167 has a circumferential lower second piston face 223 on and a circumferential upper second piston face 225 on.

After supplying hydrogen through a gas duct 107 into the first piston working space 161 , the compressor piston moves 103 vertically downwards during an initial compression process. This is done by the first piston section 165 with the lower first piston face 219 the gas in the first piston working space 161 in a first compression direction 227 against a first compression face 170 the inner wall of the compressor 133 condensed.

The compressor 101 also has a first fluid channel 171 on, through which a liquid, in particular an energy-rich form of a liquid hydrogen carrier, the first piston working space 161 can be fed. The first fluid channel 171 is by means of a liquid valve 231 with a pressure accumulator 233 fluidly connected to absorb the liquid, in particular the high-energy form of the liquid hydrogen carrier.

The gas, in particular the gaseous hydrogen and the liquid heated by the compression process, in particular the high-energy form of the liquid hydrogen carrier, are removed from the first piston working space after the first compression process 161 by a first piston connection 235 a second piston working space 163 fed.

After supplying hydrogen and the high-energy form of the liquid hydrogen carrier through the first piston connection 235 into the second piston working space 163 , the compressor piston moves 103 vertically upwards. This is done by the first piston section 165 with the upper first piston face 221 the gas in the second piston working space 163 in a direction opposite to the first compression direction 227 directed second compression direction 237 against a second compression face 239 condensed.

The compressed gas, in particular the gaseous hydrogen and the further heated liquid, in particular the high-energy form of the liquid hydrogen carrier, are removed from the second piston working space after the compression process 163 by a second piston connection 241 a third piston working space 201 fed.

After supplying hydrogen and the high-energy form of the liquid hydrogen carrier through the second piston connection 241 into the third piston working space 201 , the compressor piston moves 103 vertically down. This is done by the second piston section 167 with the lower second piston face 223 the gas in the third piston working space 201 in the first compression direction 227 condensed.

The compressed gas, in particular the gaseous hydrogen and the further heated liquid, in particular the high-energy form of the liquid hydrogen carrier, are removed from the third piston working space after the compression process 201 by a third piston connection 243 a fourth piston working space 187 fed.

After supplying hydrogen and the high-energy form of the liquid hydrogen carrier through the third piston connection 243 into the fourth piston working space 187 , the compressor piston moves 103 vertically upwards. This is done by the second piston section 167 with the upper second piston face 225 the gas in the fourth piston working space 187 in the second compression direction 237 condensed.

After the gas is compressed, the compressed hydrogen and the high-energy form of the liquid hydrogen carrier are released through the first outlet valve 175 from the fourth piston working space 187 discharged.

The compressor piston 103 is with a liquid pump 245 connected, which is a pump housing 247 and one in the pump housing 247 arranged impeller 249 includes. The liquid pump 245 is formed the liquid hydrogen carrier through the liquid inlet 251 suction and through the liquid outlet 253 to pump with pressure. The liquid outlet 253 is with the accumulator 233 to absorb the liquid 137 fluidly connected and can be via the liquid valve 231 and the first fluid channel 171 again the first piston working space 161 are fed.

In 4th is also a drive 255 shown, which with the liquid pump 245 and with the compressor piston 103 is connected and formed, in addition to the liquid pump 245 in particular also the compressor piston for pumping the liquid hydrogen carrier 103 with the first piston section 165 and the second piston section 167 to drive.

Thus, both the liquid pump 245 as well as the compressor piston 103 with the same drive 255 are effectively driven, thereby driving the liquid pump in a particularly energy-efficient manner 245 and the compressor 101 can be ensured and also can be dispensed with a further drive.

Between the compressor piston 103 and the inner wall of the compressor 133 is a piston seal 257 arranged, which causes an uncontrolled backflow of liquid 137 from the respective piston interiors 161 , 163 , 201 , 187 into the first piston working space 161 should prevent. Instead, it is between the second piston working space 163 and the first piston working space 161 a first hole 259 arranged by the first piston portion 165 is guided and designed to be liquid 137 from the second piston working space 163 into the first piston working space 161 to direct. Furthermore, there is between the third piston working space 201 and the second piston working space 163 a second hole 261 arranged, which through the compressor inner wall 133 is guided, and is formed, liquid 137 from the third piston working space 201 into the second piston working space 163 to direct.

As an alternative to making the holes 259 , 261 in the compressor 101 can on the piston seals 255 dispensed with, creating fluid 137 from the respective piston interiors 161 , 163 , 201 , 187 into the first piston working space 161 flows back. This makes it possible, in addition to the piston connections 235 , 241 , 243 from the piston interiors 161 , 163 , 201 , 187 pumped liquid 137 always a residual volume of the liquid 137 in the piston interiors 161 , 163 , 201 , 187 remains to effectively absorb heat from the liquid 137 to ensure.

As an alternative to the in 4th illustrated embodiment of the multi-stage compressor 101 that can be in the compressor 101 piston interiors arranged vertically one above the other 161 , 163 , 201 , 187 in an opposite arrangement in the compressor 101 be arranged. Here is the drive 255 at a lower end of the compressor 101 arranged, and is the first piston working space 161 at an upper end of the compressor 101 is arranged, the second piston working chamber 163 under the first piston working space 161 arranged, is the third piston working space 201 under the second piston working space 163 arranged and is the fourth piston working space 187 under the third piston working space 167 arranged, the gas and the liquid 137 from the first piston working space 161 to the fourth piston working space 187 from top to bottom in the compressor 101 can be directed.

5 shows a hydrogenation system for hydrogenating a liquid hydrogen carrier (LOHC - Liquid Organic Hydrogen Carrier).

A hydrogenation system 263 to hydrogenate a liquid hydrogen carrier (LOHC) has a compressor 101 for compressing hydrogen.

The compressor 101 has a compressor piston for this purpose 103 on, which is in a piston working space 105 of the compressor 101 moveable is stored. When the piston working space 105 through a gas duct 107 gaseous hydrogen is supplied, the compressor piston moves 103 in the piston working space 105 to the gaseous hydrogen with a piston face 109 of the compressor piston 103 against a compression face 111 to condense.

The hydrogenation system 263 has another liquid reservoir 131 on, which fluidly through a hydrogen carrier supply line 265 with the compressor 101 is connected to the dehydrated low-energy form of the liquid hydrogen carrier from the further liquid storage 131 the compressor 101 to feed. Here, the gaseous hydrogen is released through the gas duct 107 and the dehydrated low energy form of the liquid hydrogen carrier through the hydrogen carrier supply line 265 through a valve block 267 the piston working space 105 fed.

The compressor 101 points in the piston working space 105 a catalyst 269 on, which is particularly on a compressor inner wall 133 of the compressor 101 and / or on the piston face 109 of the compressor piston 103 is arranged. The catalyst 269 comprises in particular catalyst particles or a catalyst foam.

The one through the valve block 267 in the piston working space 105 flowing liquid hydrogen carriers form a falling liquid film 143 which is under the influence of gravity along the inner wall of the compressor 133 to the piston face 109 flows downwards. On the piston face 109 of the compressor piston 103 The liquid hydrogen carrier collects, so that the catalyst 269 is in contact with both the liquid hydrogen carrier and the gaseous hydrogen.

The catalyst 269 is designed to catalyze the binding of the gaseous hydrogen to the dehydrated form of the liquid hydrogen carrier (LOHC), whereby a hydrogenated form of the liquid hydrogen carrier is obtained. During the compression of the gaseous hydrogen and during the chemically exothermic hydrogenation reaction, heat is generated which can advantageously be absorbed by the liquid hydrogen carrier. Thus, the liquid hydrogen carrier and the circulating on the compressor inner wall 133 to the piston face 109 falling liquid film flowing downwards 143 of the liquid hydrogen carrier, a large area is available for heat transfer. In order to provide effective cooling, the inner wall of the compressor is essential 133 designed as a double wall, the double wall being a fluid channel 271 has through which fluid, in particular a liquid 137 such as water, flows around the inner wall of the compressor 133 to cool sufficiently. In addition, the compressor piston 103 a piston working space cooling 273 have, which is additionally designed, the compressor piston 103 and the piston working space 105 to cool sufficiently.

After the compression of the gaseous hydrogen has been completed, the gaseous hydrogen can pass through the valve block together with the heated, hydrogenated form of the liquid hydrogen carrier 267 from the piston working space 105 be discharged.

The ratio of hydrogen and liquid hydrogen carrier is preferably chosen such that the hydrogen reacts completely with the liquid hydrogen carrier during the hydrogenation process. The valve block 267 is with a compressor line 117 fluidly connected to the possibly still present gaseous hydrogen and the liquid hydrogen carrier to a gas cleaning device 119 to separate the gaseous hydrogen from the liquid hydrogen carrier. The gas cleaning device 119 can also use gaseous hydrogen via a hydrogen feed line 275 be forwarded. After separating the liquid hydrogen carrier from the gaseous hydrogen in the gas cleaning device 119 becomes the liquid hydrogen carrier through a liquid channel 115 a fluid reservoir 113 supplied to store the hydrogenated high-energy form of the liquid hydrogen carrier. Thus, an effective hydrogenation of the liquid hydrogen carrier by the in the hydrogenation device 263 absorbed catalyst 269 be made possible.

List of reference symbols

100

Dehydration system

101

compressor

103

Compressor piston

105

Piston working space

107

Gas duct

109

Piston face

111

Compression face

113

Liquid storage

115

Fluid channel

117

Compressor line

119

Gas cleaning device

121

Hydrogen storage line

123

Hydrogen pressure vessel

125

Dehydration line

127

Dehydrator

129

Hydrogen carrier discharge line

131

Further liquid storage

133

Inner wall of the compressor

135

Outside of the compressor

137

liquid

139

Circumferential channel

141

Gutter edge

143

Liquid falling film

145

Piston gap

147

outlet valve

149

Valve space

151

Hydrogen carrier supernatant

153

Wall contour

155

First compressor stage

157

Second compressor stage

159

parting line

161

First piston working space

163

Second piston working space

165

First piston section

167

Second piston section

169

First piston face

170

First compression face

171

First fluid channel

173

First liquid fall film

175

First exhaust valve

177

First stage feed

179

Another two-stage compressor

181

Fourth compressor stage

183

Third compressor stage

185

Another dividing line

187

Fourth piston working space

189

Third piston section of the second compressor piston

191

Another compressor piston

193

Fourth piston section of the second compressor piston

195

Fourth piston face

197

Fourth liquid fall film

199

Fourth exhaust valve

201

Third piston working space

203

Third piston face

205

Third fluid channel

207

Third liquid fall film

209

Third exhaust valve

211

Second stage feed

213

Second piston face

215

Second liquid fall film

217

Second exhaust valve

219

Lower first piston face

221

Upper first piston face

223

Lower second piston face

225

Upper second piston face

227

First direction of compression

231

Liquid valve

233

Pressure accumulator

235

First piston connection

237

Second direction of compression

239

Second compression face

241

Second piston connection

243

Third piston connection

245

Liquid pump

247

Pump housing

249

Impeller

251

Liquid inlet

253

Liquid outlet

255

drive

257

Piston seal

259

First hole

261

Second hole

263

Hydrogenation system

265

Hydrogen carrier supply line

267

Valve block

269

catalyst

271

Fluid channel

273

Piston working space cooling

275

Hydrogen feed

Claims (28)

Compressor (101) for compressing a gas, having: a piston working space (105) which is delimited by an inner compressor wall (133), wherein the compressor inner wall (133) is closed by a compression end face (111); at least one gas channel (107) which is led through the compressor inner wall (133) to the piston working space (105) and is designed to supply gas to the piston working space (105); a compressor piston (103) which is movably mounted in the piston working space (105) and is designed to compress the gas supplied to the piston working space (105) through the gas channel (107) with a piston face (109) against the compression face (111); and a liquid channel (115) for guiding a liquid (137), the liquid channel (115) being guided and formed through the compressor inner wall (133) to the piston working space (105), the liquid (137) via the compressor inner wall (133) to the piston face (109), a circumferential channel (139) being formed in the inner wall of the compressor (133), the liquid channel (115) being fluidically connected to the circumferential channel (139) and the liquid (137) to the circumferential channel (139), and the circumferential channel (139) is designed to deliver the liquid (137) via a channel edge (141) to the compressor inner wall (133). Compressor (101) Claim 1 wherein an outlet valve (147) for discharging the compressed gas and the liquid (137) is arranged in the compression end face (111). Compressor (101) Claim 2 , wherein an adjustable ratio of gas and liquid can be supplied to the piston working space (105) through the gas channel (107) and through the liquid channel (115), and the compressor (101) is designed to deliver gas and liquid in the adjustable ratio through the outlet valve (147) to be discharged from the piston working space (105). Compressor (101) according to one of the preceding claims, wherein the liquid channel (115) is designed to deliver the liquid (137) to the compressor inner wall (133) in such a way that the liquid (137) under the influence of gravity as a liquid fall film (143) along the The inner wall of the compressor (133) flows towards the piston face (109). Compressor (101) according to one of the preceding claims, wherein the compressor piston (103) is laterally sealed in a gastight manner by the liquid (137) against the compressor inner wall (133). Compressor (101) according to one of the preceding claims, wherein the liquid channel (115) is led through the compression face (111) to the piston working space (105), or wherein the liquid channel (115) is led laterally through the compressor inner wall (133). Compressor (101) according to one of the preceding claims, further comprising a liquid distribution channel which is fluidically connected to the liquid channel (115) and is provided to supply the liquid (137) to the liquid channel (115). Compressor (101) according to one of the preceding claims, wherein the gas channel (107) is led through the compression end face (111) to the piston working space (105). Compressor (101) according to one of the preceding claims, wherein the compression face (111) has a wall contour (153), the wall contour (153) in particular as a conical wall contour (153), rounded wall contour (153) or a horizontal wall contour (153) is trained. Compressor (101) according to one of the preceding claims, wherein the piston working chamber (105) comprises a first piston working chamber (161) and a second piston working chamber (163) which are delimited by the compressor inner wall (133), the compressor inner wall (133) on the first Piston working space (161) is closed off by a first compression end face (170), the compressor inner wall (133) being closed off at the second piston working space (163) by a second compression end face (239), wherein the compressor piston (103) has a first piston section (165) which is movably mounted between the first piston working chamber (161) and the second piston working chamber (163), wherein the first piston section (165) is designed to compress gas in the first piston working chamber (161) with a lower, first piston end face (219) against the first compression end face (170) in a first compression direction (227), and wherein the first piston section (165) is designed to compress gas in the second piston working chamber (163) with an upper, first piston end face (221) against the second compression end face (239) in a second compression direction (237) opposite to the first compression direction (227). Compressor (101) Claim 10 , wherein the first piston working chamber (161) and the second piston working chamber (163) are fluidly connected by a first piston connection (235) to transfer compressed gas and liquid (137) through the first piston connection (235) from the first piston working chamber (161) to the second Supply piston working space (163). Compressor (101) according to one of the preceding claims, wherein a gas valve is arranged on the gas channel (107), the gas valve being designed to fluidically close the gas channel (107) during the compression of the gas in the piston working space (105, 161, 163) block, and wherein the gas valve is designed to fluidly release the gas channel (107) during a low-pressure phase in the piston working chamber (105, 161, 163) in order to supply gas to the piston working chamber (105, 161, 163). Compressor (101) according to one of the preceding claims, wherein a liquid valve (231) is arranged on the liquid channel (115), wherein the liquid valve (231) is formed, the liquid channel (115) during the compression of the gas in the piston working space (105, 161, 163) fluidly to block, and wherein the liquid valve (231) is designed to fluidically release the liquid channel (115) during a low-pressure phase in the piston working space (105, 161, 163) in order to fluid (137) the piston working space (105, 161 , 163). Compressor (101) according to one of the preceding claims, wherein a liquid pump (245) is arranged on the compressor (101), which is designed to pump the liquid (137) through the liquid channel (115) into the piston working space (105). Compressor (101) Claim 14 wherein a drive (255) for driving the liquid pump (245) is arranged on the liquid pump (245), the drive (255) being designed to drive the compressor piston (103) and the liquid pump (245) together. Compressor (101) according to one of the preceding claims, wherein the compressor (101) has a first compressor stage (155) and a second compressor stage (157), wherein the first compressor stage (155) has a first piston working chamber (161) which is delimited by the compressor inner wall (133), the compressor inner wall (133) being closed by a first compression face (170), the first compressor stage (155) having at least one gas duct (107) which is guided through the compressor inner wall (133) to the first piston working chamber (161) and is designed to supply gas to the first piston working chamber (161), wherein the compressor piston (103) has a first piston section (165) which is movably mounted and designed in the first piston working chamber (161), counteracting the gas supplied to the first piston working chamber (161) through the gas channel (107) with a first piston face (169) compressing the first compression face (170), wherein the first compressor stage (155) has a first liquid channel (171) for guiding a liquid (137), the first liquid channel (171) being guided and formed through the compressor inner wall (133) to the first piston working chamber (161), the liquid (137) ) via the compressor inner wall (133) to the first piston face (169), the first compressor stage (155) in the first compression face (170) having a first outlet valve (175) for discharging the compressed gas and the liquid (137) from the first Compressor stage (155) is arranged, wherein the first outlet valve (175) is fluidly connected to a first stage supply (177), wherein the second compressor stage (157) has a second piston working chamber (163) which is delimited by the compressor inner wall (133), the compressor inner wall (133) being closed by a second compression end face (239), wherein the second compressor stage (157) is fluidically connected to a second stage feed (211), the second stage feed (211) being guided and formed through the compressor inner wall (133) to the second piston working chamber (163), the second piston working chamber (163) being gas and To supply liquid (137), wherein the compressor piston (103) has a second piston section (167) which is movably mounted and designed in the second piston working chamber (163), the gas fed to the second piston working chamber (163) through the second stage feed (211) with a second piston face (213) to compress against the second compression end face (239), wherein the second compressor stage (157) a second outlet valve (217) is arranged in the second compression end face (239) for discharging the compressed gas and the liquid (137) from the second compressor stage (157). Compressor (101) according to one of the preceding claims, wherein the liquid (137) comprises a liquid hydrogen carrier (LOHC), wherein the liquid hydrogen carrier is designed to reversibly bind and release hydrogen, wherein the gas comprises hydrogen, and wherein the compressor (101 ) is designed to compress hydrogen to obtain compressed hydrogen. Compressor (101) Claim 17 , wherein the liquid hydrogen carrier comprises a hydrocarbon compound with an extended π-conjugated system, wherein the hydrocarbon compound with the extended π-conjugated system is selected in particular from a group comprising aromatic Hydrocarbons, polycyclic aromatic hydrocarbons, polycyclic heteroaromatic hydrocarbons, π-conjugated organic polymers or a combination thereof, and in particular is selected from the group comprising N-ethylcarbazole, dibenzyltoluene, benzyltoluene or mixtures thereof. Dehydration system (100) for dehydrating a liquid hydrogen carrier (LOHC) with: - the compressor (101) according to one of the preceding Claims 1 to 18th wherein the compressor (101) can be supplied with gaseous hydrogen via the gas duct (107), wherein the compressor (101) can be supplied with liquid hydrogen carrier via the liquid duct (115), and the compressor (101) is designed to compress the gaseous hydrogen to obtain compressed hydrogen; - A gas cleaning device (119) which is fluidly connected to the compressor (101) and is designed to separate the compressed hydrogen from the liquid hydrogen carrier; and - a dehydrogenation device (127) which is fluidly connected to the gas cleaning device (119) and is designed to release hydrogen from the liquid hydrogen carrier, the dehydrogenation device (127) being fluidically connected to the compressor (101) through the gas duct (107), in order to supply the released hydrogen to the compressor (101) again. Dehydration system (100) Claim 19 wherein the liquid channel (115) is fluidly connected to a liquid reservoir (113) for storing an energy-rich, hydrated form of the liquid hydrogen carrier. Dehydration system (100) Claim 19 or 20th , wherein the dehydration device (127) is fluidly connected to a further liquid reservoir (131), the further liquid reservoir (131) being designed to store a dehydrated, low-energy form of the liquid hydrogen carrier after the gaseous hydrogen has been released. Dehydration system (100) according to one of the Claims 19 to 21 wherein the gas cleaning device (119) is fluidly connected to a hydrogen pressure vessel (123), the hydrogen pressure vessel (123) being designed to store the compressed hydrogen after separation from the liquid hydrogen carrier. Hydrogenation system (263) for hydrogenating a liquid hydrogen carrier (LOHC) with: - the compressor (101) according to one of the preceding Claims 1 to 18th , wherein the compressor (101) can be supplied with gaseous hydrogen via the gas duct (107), wherein the compressor (101) can be supplied with liquid hydrogen carrier via the liquid duct (115), the compressor (101) being designed to compress the gaseous hydrogen, in order to obtain compressed hydrogen, wherein the compressor (101) has a catalyst (269) which is arranged on the compressor inner wall (133) and / or on the piston face (109) and is designed to chemically bond hydrogen to the liquid hydrogen carrier catalyze. Hydrogenation system (263) Claim 23 wherein the compressor (101) is fluidly connected to a liquid reservoir (113) for storing the liquid hydrogen carrier in a hydrogenated high-energy form. Hydrogenation system (263) Claim 23 or 24 wherein the liquid channel (115) is fluidically connected to a further liquid reservoir (131), the further liquid reservoir (131) being designed to store the liquid hydrogen carrier in a dehydrated, low-energy form. Hydrogenation system (263) according to one of the Claims 23 to 25th wherein the catalyst (269) comprises catalyst particles or a catalyst foam, and in particular comprises a transition metal catalyst. Hydrogenation system (263) according to one of the Claims 23 to 26th , wherein the compressor inner wall (133) is designed as a double wall, the double wall having a fluid channel (271) for cooling the compressor inner wall (133). Hydrogenation system (263) according to one of the Claims 23 to 27 , wherein the compressor piston (103) has a piston working chamber cooling system (273) which is designed to cool the compressor piston (103) and the piston working chamber (105).

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