[go: up one dir, main page]

WO2025059785A1 - Dispositif à piston liquide et procédé de compression et de dilatation d'un gaz - Google Patents

Dispositif à piston liquide et procédé de compression et de dilatation d'un gaz Download PDF

Info

Publication number
WO2025059785A1
WO2025059785A1 PCT/CH2024/050046 CH2024050046W WO2025059785A1 WO 2025059785 A1 WO2025059785 A1 WO 2025059785A1 CH 2024050046 W CH2024050046 W CH 2024050046W WO 2025059785 A1 WO2025059785 A1 WO 2025059785A1
Authority
WO
WIPO (PCT)
Prior art keywords
liquid
cylinder
pressure
low
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/CH2024/050046
Other languages
German (de)
English (en)
Inventor
Dominik Schnarwiler
Mohameddeq HASSAN
Pablo GASSMANN
Pascal ZÜRCHER
Patrick BAUMANN
Rafik BARHOUMI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Green Y Energy AG
Original Assignee
Green Y Energy AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Green Y Energy AG filed Critical Green Y Energy AG
Publication of WO2025059785A1 publication Critical patent/WO2025059785A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0011—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons liquid pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/141—Intermediate liquid piston between the driving piston and the pumped liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/142—Intermediate liquid-piston between a driving piston and a driven piston

Definitions

  • the present invention relates to methods for compressing and/or expanding a gas using a liquid piston device, liquid piston devices for carrying out these methods, and various uses of the liquid piston devices.
  • Piston compressors are typically used for compressing a gas, particularly over a high pressure range.
  • this technology enables higher pressures to be achieved by means of suitable sealing of the piston chamber.
  • this sealing in particular presents a challenge in terms of costs and maintenance expenditure, and lubrication of the piston must also be ensured. If pure compressed gas is required, contamination of the gas, which can occur through contact with the drive medium, must also be prevented.
  • Liquid piston systems solve this challenge by using a liquid as the piston instead of a solid piston, which is moved in the cylinder.
  • the rising liquid level compresses the gas in the cylinder. This also ensures the tightness of the pressure chamber.
  • Lubrication is not necessary with the liquid piston, and gry 12/P 2 / 44 2024-09-19 This significantly reduces maintenance requirements.
  • the liquid promotes heat exchange with the compressed gas, which has a beneficial effect on the efficiency of the compression process because temperature fluctuations are reduced. Additionally, it is possible to install a fixed heat exchanger in the cylinder, around which the liquid can flow, further increasing heat exchange. This is not possible in conventional piston compressors due to the fixed piston.
  • Liquid piston systems can also be used as expanders by reversing the process. Compressed gas pushes the liquid column out of the cylinder and drives a liquid motor. This reversal is generally possible in liquid piston systems with the same equipment used for compression, by using appropriate valve circuits. This allows a bidirectional system to be implemented with little effort.
  • Liquid piston compressors are used in the higher pressure range, for example in gry 12/P 3 / 44 2024-09-19 Compressed gas supply, when filling compressed gas cylinders and at compressed gas filling stations.
  • the liquid piston expander can be used wherever compressed gas is expanded from a higher pressure level to a lower pressure level, for example when withdrawing compressed gas from a reservoir or a pipeline.
  • the bidirectional system is primarily used in compressed gas storage systems, such as compressed air energy storage systems.
  • Liquid piston systems that serve exclusively as compressors are known from the prior art, for example from DE 102004046316 A1.
  • hydrogen in particular is compressed and an ionic liquid is used as the liquid in order not to contaminate the gaseous medium to be compressed.
  • WO 2017198725 A1 shows a bidirectional liquid piston system that is used in particular in a multi-stage energy storage system for the compression and expansion of a gas.
  • a heat exchanger in the cylinder increases the heat exchange between gas and liquid.
  • DE 102012003288 B3 shows a bidirectional liquid piston system that further improves heat exchange with an optimized heat exchanger design. gry 12/P 4 / 44 2024-09-19 favors this. In addition, the dead space volume is minimized by an adapted inclined arrangement of the cylinders.
  • WO 2008139267 A1 shows a bidirectional liquid piston system in which a portion of the liquid is sprayed directly into the compression or expansion chamber. This also increases the heat exchange between liquid and gas, and virtually isothermal conditions are achieved, which is advantageous for efficiency.
  • WO 2008031527 A1 shows a liquid piston system that replaces the measurement of the liquid level in several cylinders with a level measurement in the leakage tank.
  • the present invention therefore has the object of providing methods for the compression and/or expansion of a gas, as well as liquid piston devices for carrying out these methods, which minimize the dead space volume.
  • a further, optional object is to provide a liquid piston device and a corresponding method with which the compression and/or expansion process is more isothermal.
  • a further, optional object is to provide a liquid piston device with a simple system for measuring the liquid level therein.
  • FIG. 1 Schematic drawing of a gry 12/P 6 / 44 2024-09-19 Liquid piston device with two cylinders for the compression and expansion of a gas
  • Figure 2 Schematic drawing for the application in a compressed gas energy storage system
  • Figure 3 Schematic drawing of the general energy flows
  • Figure 4 Schematic drawing for the application in compressed gas supply
  • Figure 5 Liquid piston device with the liquid management system
  • Figure 6 Liquid piston device with the heat management system
  • Figure 7 Liquid piston device with the management system for the leakage liquid
  • Figure 8 Liquid piston device with the pressure and liquid level sensors
  • Figure 9 Detail of a cylinder with swirl pin
  • the figures represent possible embodiments, which are explained in the following description.
  • the basis of the invention is a liquid piston device with which gas 13, for example ambient air, gry 12/P 7 / 44 2024-09-19 Nitrogen or oxygen, can be compressed from a low-pressure gas reservoir 40 with a lower pressure to a higher pressure and stored in a high-pressure gas reservoir 50.
  • This liquid piston device comprises at least two cylinders 10, 10', which are connected to one another by a liquid line 21 (see Figure 1).
  • a liquid drive unit 20 comprising a hydraulic pump, with which a liquid 14 can be conveyed from one cylinder 10, 10' to the other cylinder 10, 10'.
  • Each cylinder 10, 10' is connected to the low-pressure gas reservoir 40 by a low-pressure line 41, so that a gas 13 can pass from the low-pressure gas reservoir 40 through the low-pressure line 41 into each cylinder 10, 10'.
  • the low-pressure gas reservoir 40 is preferably a container in which gas 13 is located at low pressure, for example, below 1 to 100 bar.
  • the low-pressure gas reservoir 40 could also simply be the environment, with air from the environment passing through the low-pressure line 41 into the cylinders 10, 10', or a low-pressure compressor and/or expander, which, for example, pre-compresses gas to a certain pressure level and/or a gas generator, which provides a certain gas component, for example, nitrogen, from ambient air (see Figure 2).
  • Low-pressure line 41 is provided with low-pressure valves 11, 11', with which the passage of gas 13 from the low-pressure gas reservoir 40 to each cylinder 10, 10' can be controlled.
  • Each cylinder 10, 10' is connected to the high-pressure gas reservoir 50 by a high-pressure line 51, so that a gas 13 from each cylinder 10, 10' can pass through the high-pressure line 51 into the high-pressure gas reservoir 50.
  • the high-pressure gas reservoir 50 is preferably a container suitable for the withdrawal and/or storage of gas 13 under high pressure of, for example, 10 to 1000 bar.
  • the high-pressure gas reservoir 50 can also be or comprise a high-pressure compressor and/or expander, which, for example, further compresses gas to an even higher pressure level.
  • the high-pressure line 51 is provided with high-pressure valves 12, 12', with which the passage of gas 13 from each cylinder 10, 10' to the high-pressure gas reservoir 50 can be controlled.
  • a liquid 14 for example water or oil or another suitable liquid, is located in the cylinders 10, 10'.
  • the liquid drive unit 20 conveys liquid 14 through the liquid line 21 from a first cylinder 10, 10' to a second cylinder 10, 10'.
  • the low-pressure valve 11 connected to the first cylinder 10 is open, and the high-pressure valve 12 connected to the first cylinder 10 is closed, so that the liquid 14 escaping from the first cylinder 10 is replaced therein with gas 13 from the low-pressure gas reservoir 40.
  • the low- and high-pressure valves 11, 11', 12, gry 12/P 10 / 44 2024-09-19 12' and the conveying direction of the liquid drive unit 20 can be switched in order to continue the compression process with the compression and expulsion of the gas 13 located in the first cylinder 10, and so on.
  • the amount of liquid 14 located in the liquid piston device is greater than the volume of a cylinder 10, 10'.
  • the incoming mechanical or electrical energy with which the liquid drive unit 20 is driven is stored in the form of compressed gas in the high-pressure gas reservoir 50. This stored energy can later be released as outgoing drive energy by expanding the stored compressed gas through the liquid piston device, whereby the liquid drive unit 20 then serves as a hydraulic motor with which a vehicle, a machine, or a power generator can be driven.
  • the high-pressure valve 12' and the low-pressure valve 11' of the second cylinder 10' are closed and the admitted, high-pressure gas 13 expands therein.
  • the liquid 14 in the second cylinder 10' is driven through the liquid line 21 and through the liquid drive unit 20, which then serves as a hydraulic motor.
  • the liquid 14 then enters another cylinder 10, 10', for example, the first cylinder 10 on the left side of Figure 1, in which the high-pressure valve 12 is closed and the gry 12/P 12 / 44 2024-09-19 Low-pressure valve 11 is open.
  • the gas 13 located in the first cylinder 10 is then expelled through the low-pressure line 41 and reaches the low-pressure gas reservoir 40, which then serves as a gas sink.
  • a bidirectional liquid piston device With the compression and subsequent expansion of gas 13, a bidirectional liquid piston device is provided, with which energy can be stored and released again, similar to a battery. gry 12/P 13 / 44 2024-09-19
  • the liquid piston device offers numerous applications, a few of which are briefly mentioned below.
  • the temporary storage of excess energy is one of the greatest challenges in power generation using renewable energy sources, whose output is weather-dependent (sun, wind, etc.) and cannot be adapted to the actual current power demand.
  • One possible application of the present liquid piston device is the storage of excess energy (for example, during the day when the sun generates electricity via a solar system, but there is a low energy demand), which can be used later (for example, in the evening when the solar system is no longer generating electricity but there is a greater electricity demand).
  • the present liquid piston device can also be used, for example, to provide economical peak load management when purchasing electrical energy.
  • the intermediate storage of energy allows energy to be drawn from the electrical grid during off-peak times and stored for use during peak times.
  • the liquid piston device according to the invention has further applications in industrial sectors where compressed gas is required.
  • the compressed gas required for a machine can be produced in advance at low load times, temporarily stored at higher pressure and then gry 12/P 14 / 44 2024-09-19 peak load times at any desired lower pressure level. Since the gas is stored at high pressure, a useful energy density of up to 47 kWh/m 3 at 300 bar is achieved and the required storage volume is reduced to an appropriate size.
  • the presented liquid piston device is also suitable for use in the compressed gas storage system according to WO 2019219801 A1, in which a liquid piston system in conjunction with a liquid-filled compressed gas tank enables gas to be stored at constant pressure.
  • the present liquid piston device can assume all or part of the function of the working machine and/or the displacement device described in WO 2019219801 A1. In order to increase the efficiency of the compression, the dead space volume of the compressed gas 13 in the cylinders 10, 10' should be minimized.
  • a cylinder 10, 10' should ideally be filled with liquid 14 exactly up to the connected high-pressure valve 12, 12', no more and no less.
  • a very precise filling gry 12/P 16 / 44 2024-09-19 of the cylinder 10, 10' is not feasible, so in practice the cylinder 10, 10' is either not completely filled or the cylinder 10, 10' is overfilled.
  • a liquid piston device is specially designed to carry out this method step and for this purpose comprises a control with which the liquid drive unit 20 and the high and low pressure valves 11, 11', 12, 12' can be controlled.
  • the control system is programmed so that the liquid 14, which is conveyed into the cylinder 10, 10' by the liquid drive unit 20, fills the cylinder 10, 10' and is conveyed at least as far as the high-pressure line 51 and after the high-pressure valve 12, 12'.
  • the dead space volume in the cylinder 10, 10' is thus minimized and an optimal expulsion process of the compressed gas 13 into the high-pressure gas reservoir 50 is ensured.
  • the high-pressure line 51 or the high-pressure valve 12, 12' opens at the upper end of the cylinders 10, 10', so that the cylinders 10, 10' are filled with the liquid 14.
  • gry 12/P 17 / 44 2024-09-19 can be completely filled.
  • the dead space volume of the remaining gas 13 in the cylinders 10, 10' should be minimized. This means that at the start of the expansion process, the cylinders 10, 10' must be filled as completely as possible with liquid 14 before the corresponding high-pressure valve 12, 12' opens.
  • the invention provides that the liquid 14, which enters the cylinder 10, 10' and pushes the gas 13 contained therein into the low-pressure gas reservoir 40, fills the cylinder 10, 10' and is conveyed at least as far as the low-pressure line 41 and past the low-pressure valve 11, 11' (i.e., the liquid 14 flows through the low-pressure valve 11, 11' and continues into the low-pressure line 41).
  • a liquid piston device is specifically designed to carry out this method step and comprises a control system with which the liquid drive unit 20 and the high- and low-pressure valves 11, 11', 12, 12' can be controlled. gry 12/P 18 / 44 2024-09-19
  • the control system is programmed so that the amount of gas 13 admitted into a cylinder 10, 10' through the high pressure valve 12, 12' during the intake process is calibrated so that after the expansion process of this gas 13 in this cylinder, the other cylinder 10, 10' is completely filled with liquid 14 and the liquid 14 is transported at least as far as the low pressure line 41 and after the low pressure valve 11, 11'. In this way, the dead space volume in the cylinders 10, 10' is minimized or completely eliminated.
  • liquid piston device is used only as an expander to draw on stored energy, it may be sufficient if liquid 14 is only driven to the low-pressure valve 11, 11' during the expansion process. If the liquid piston device is used bidirectionally as a compressor and expander, the measure can be used in both the compression process and the expansion process. However, to ensure that no liquid 14 enters the high-pressure gas reservoir 50 or the low-pressure gas reservoir 40, a special liquid management system is provided. This also provides a closed system for the liquid 14, from which it cannot escape and therefore no refilling is necessary.
  • a liquid separator 42, 52 for example a cyclone separator, is arranged either between the high-pressure valve 12, 12' and the high-pressure gas reservoir 50 or between the low-pressure valve 11, 11' and the low-pressure gas reservoir 40 (see Figure 5).
  • a liquid separator 42, 52 is arranged both between the high-pressure valve 12, 12' and the high-pressure gas reservoir 50 and between the low-pressure valve 11, 11' and the low-pressure gas reservoir 40.
  • Each liquid separator 42, 52 is connected to a return line 43, 53, through which the liquid 14 flows from the liquid separator 42, 52 back into one of the cylinders 10, 10'.
  • the liquid 14 can flow back into another cylinder 10, 10' or into the same cylinder 10, 10' from which it was expelled. However, for this to happen, the pressure in the cylinder 10, 10' must be lower than in the liquid separator 42, 52.
  • the liquid 14 could flow directly back into a cylinder 10, 10' in which no compression process is taking place.
  • this liquid 14 could also flow back into a cylinder 10, 10' in which a compression process is taking place, as long as the pressure in the cylinder 10, 10' is lower and a sufficient pressure difference is present.
  • At least one return line 43, 53 of a liquid separator 42, 52 leads to a valve group 60 and after the valve group 60 several branches 61, 62, 63, 61', 62', 63' of the return lines 43, 53 lead to a cylinder 10, 10' and open at different points, for example at different heights, of the cylinder 10, 10'.
  • Several branches 61, 62, 63, 61', 62', 63' of the return lines 43, 53 can also lead to gry 12/P 22 / 44 2024-09-19 different points of different cylinders 10, 10'.
  • Figure 5 shows a valve group 60 with six branches 61, 61', 62, 62', 63, 63', three of which lead to different points of one cylinder 10, 10' and three of which lead to different points of another cylinder 10, 10', for example at the upper end, in the middle and at the lower end of the cylinders 10, 10'. It is also possible for only two branches to lead to each cylinder 10, 10', which open, for example, at the lower and upper ends of the cylinder 10, 10'. With the appropriate control of the valve group 60, the time, cylinder 10, 10', and position on the cylinder 10, 10' for the return of the liquid from the liquid separator 42, 52 can be determined as desired.
  • the ideal time for this return is when the pressure difference between the liquid separator 42, 52 and the cylinder 10, 10' is as small as possible. Thus, the least energy is lost from the first liquid separator 52 on the side of the high-pressure gas reservoir 50, and the first pump 44 connected to the second liquid separator 42 has to consume the least energy.
  • Additional, optional solutions to further minimize the gate volume include narrowing the upper part of the cylinders 10, 10' so that the gas 13 during the gry 12/P 23 / 44 2024-09-19 discharge process is directed toward the high- and low-pressure valves 11, 11', 12, 12'.
  • a swirl body 80 can be attached to the upper end of the cylinder 10, 10' near the high- and low-pressure valves 11, 11', 12, 12' (see Figure 9). This creates a turbulence in the flow at the upper end of the cylinder 10, 10', in particular the turbulence of the separating layer between liquid 14 and gas 13. This improves the distribution of the liquid 14 and reduces the dead space volume of the gas 13.
  • the heat accumulator 15, 15' is preferably located in the upper region of the cylinders 10, 10', because the greatest energy flows occur in this region of compression or expansion:
  • the greatest heating of the gas 13 occurs at the end of compression, when the cylinder 10, 10' is already partially filled with gry 12/P 25 / 44 2024-09-19 liquid and the gas 13 is in its upper region.
  • the greatest cooling occurs at the beginning of the expansion, as soon as the pressurized gas 13 expands in the upper region of the cylinder filled with liquid 14 at the beginning of the expansion process. This also saves heat storage material in the lower region of the cylinders 10, 10' and thus reduces costs.
  • the heat storage 15, 15' is heated in a first step by the heating gas 13.
  • a suitable design of the heat accumulator 15, 15' requires properties such as low liquid retention capacity, low pressure loss, gry 12/P 26 / 44 2024-09-19 simple production and optimized costs must be taken into account. Tests have shown that a heat accumulator made of steel wool, for example, is well suited.
  • the liquid 14 already dissipates the heat of the compressed gas or the cold of the expanded gas through contact with the walls of the cylinders 10, 10' and the other components of the liquid piston device (liquid line 21, liquid drive unit 20, high and low pressure valves 11, 11', 12, 12', etc.).
  • a first heat exchanger 22 can be integrated into the liquid line 21 (see Figure 6). Via the first heat exchanger 22, an external circuit can be heated by supplying heat during compression and, similarly, cooled by removing heat during expansion.
  • the liquid is preferably conveyed or sprayed into the cylinders 10, 10' from bottom to top through the liquid line 21. This has the disadvantage that the liquid 14 is sprayed directly onto the heat accumulator 15, 15' and partially fills it with liquid 14 before the rising gry 12/P 27 / 44 2024-09-19 liquid level reaches the heat accumulator 15, 15'.
  • a baffle plate 16, 16' can be arranged in a cylinder 10, 10', for example at the inlet of the liquid 14, 14' at the lower end of the cylinder 10, 10', against which the incoming liquid 14 impacts. This ensures that, regardless of the inlet velocity of the liquid 14, a controlled increase in the liquid level in the cylinder 10, 10' is realized and the liquid 14, 14' does not come into undesired premature contact with the heat accumulator 15, 15'.
  • the liquid piston device is used for heating or cooling gry 12/P 28 / 44 2024-09-19
  • the gas 13 is to be heated to a higher or lower temperature level, it can be advantageous if the isothermal nature of the process is controllable.
  • two inlets for the liquid 14 into each cylinder 10, 10' can be provided in the liquid line 21, which can be controlled by a valve 17, 17': a first inlet with a baffle plate 16, 16' for the controlled increase in the liquid level, and a second inlet through which the liquid 14 intentionally comes into early contact with the heat accumulator 15, 15' (see Figure 6).
  • a valve 17, 17' a first inlet with a baffle plate 16, 16' for the controlled increase in the liquid level
  • One or more returns 43, 53 of the liquid separators 42, 52 can lead to a valve group 60 as described above, and after the valve group 60, several branches 61, 61', 62, 62', 63, 63' of the returns 43, 53 can lead to outlets at various points on the cylinders 10, 10'.
  • gry 12/P 29 / 44 2024-09-19 in particular to a first orifice, through which the returned liquid 14 sprays onto the heat accumulator 15, 15', and to a second orifice, through which the returned liquid does not spray onto the heat accumulator 15, 15'.
  • the liquid return to a cylinder 10, 10' could be controllably above, below, or at the level of the heat accumulator 15, 15'.
  • the liquid drive unit 20 exhibit a leakage flow of the liquid during operation. gry 12/P 30 / 44 2024-09-19 14.
  • the liquid piston device can have a management system for the leakage fluid.
  • the leakage flow can, for example, be guided via a leakage line 71 into a leakage container 70, which has a lower pressure level (see Figure 7).
  • the fluid 14 can be brought back to the required pressure by means of a second pump 73 and then returned to the cylinders 10, 10' via a third return line 72.
  • the third return line 72 can lead to this valve group 60 and the leakage liquid can be returned together with the liquid 14 from the liquid separators 42, 52 to the cylinders 10, 10'.
  • the liquid 14 in the leakage tank 70 also enables a more suitable heat exchange with an external circuit, since this liquid 14 is at a lower pressure level.
  • a third pump 76 can therefore be provided, which transports the liquid 14 from the leakage tank 70 through a second heat exchanger 75 and returns it to the leakage tank 70. Due to the lower pressure in this circuit, the design of the heat exchanger 75 becomes simpler and more cost-effective.
  • This third pump 76 can control the flow through the second gry 12/P 31 / 44 2024-09-19 heat exchanger 75 can be controlled independently.
  • the second heat exchanger 75 can be placed directly in the leakage line 71 or in the third return line 72, thus avoiding the need for the third pump 76.
  • the liquid piston device can be further simplified by returning the liquid from the liquid separator 42 on the low-pressure side through the liquid line 77 directly into the leakage tank 70.
  • no separate first pump 44 and corresponding return line 43 are necessary.
  • the pressure in the liquid separator 42 on the low-pressure side must be higher than in the leakage tank 70.
  • Efficient liquid level measurement in liquid piston systems is generally a challenge, especially when a heat accumulator 15, 15' is mounted inside the cylinders 10, 10'.
  • the present invention solves this efficiently and cost-effectively with two liquid level sensors L1, L2, L3, L4, L5, L6, L7, L8 at different heights in the cylinders 10, 10' and in the liquid separators 42, 52, for example with one liquid level sensor at the upper end and one liquid level sensor at the lower end of the cylinders 10, 10'.
  • a leakage container 70 it can also be provided with two liquid level sensors L9, L10 at different heights. This allows the maximum and minimum levels of the liquid 14 to be detected in each of these containers.
  • the other levels of the liquid level in the cylinders 10, 10' can be estimated with sufficient accuracy using the position and the state of the shaft of the liquid drive unit 20, e.g., using a sensor for the number of revolutions N1. Using the information on the number of revolutions, the quantity of liquid 14 conveyed from or into the cylinders 10, 10' can be determined and thus compared with the maximum and minimum levels determined by the liquid level sensors L1, L2, L3, L4, L5, L6, L7, L8, L9, L10. gry 12/P 33 / 44 2024-09-19 Continuous estimation of the liquid level can be made.
  • the state of the liquid piston device can be detected with the pressure sensors, the simple liquid level sensors, and the sensor for the number of revolutions N1, and the liquid piston device can be optimally controlled with the liquid pumps and valves.
  • the liquid drive unit 20 is preferably designed such that its flow and rotation direction are always the same, regardless of the compression or expansion operating mode. This reduces complexity and allows for savings in components and costs.
  • the liquid drive unit 20 can comprise valves with which the flow direction of the liquid 14 can be controlled as desired.
  • the liquid drive unit 20 can comprise a hydraulic pump and a hydraulic motor, which are used alternatively for compression and expansion, or a reversible hydraulic pump that can also serve as a hydraulic motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

La présente invention concerne un procédé de compression et/ou de dilatation d'un gaz à l'aide d'un dispositif à piston liquide, comprenant : au moins deux cylindres (10, 10') ; une conduite de liquide (21), qui raccorde les cylindres (10, 10') ; une unité d'entraînement de liquide (20), avec laquelle un liquide (14) peut être transporté d'un cylindre (10, 10') à l'autre cylindre (10, 10') ; un réservoir basse pression de gaz (40), qui est raccordé à chaque cylindre (10, 10') par l'intermédiaire d'une conduite basse pression (41) ; une soupape basse pression (11, 11') pour chaque cylindre (10, 10'), avec laquelle la conduite basse pression (41) peut être ouverte et fermée par rapport au cylindre (10, 10') ; un réservoir haute pression de gaz (50), qui est raccordé à chaque cylindre (10, 10') par l'intermédiaire d'une conduite haute pression (51) ; et une soupape haute pression (12, 12') pour chaque cylindre (10, 10'), avec laquelle la conduite haute pression (51) peut être ouverte et fermée par rapport au cylindre (10, 10').
PCT/CH2024/050046 2023-09-22 2024-09-20 Dispositif à piston liquide et procédé de compression et de dilatation d'un gaz Pending WO2025059785A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CHCH001045/2023 2023-09-22
CH001045/2023A CH721148A1 (de) 2023-09-22 2023-09-22 Flüssigkolbenvorrichtung und Verfahren zur Kompression und Expansion eines Gases

Publications (1)

Publication Number Publication Date
WO2025059785A1 true WO2025059785A1 (fr) 2025-03-27

Family

ID=88290395

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CH2024/050046 Pending WO2025059785A1 (fr) 2023-09-22 2024-09-20 Dispositif à piston liquide et procédé de compression et de dilatation d'un gaz

Country Status (2)

Country Link
CH (1) CH721148A1 (fr)
WO (1) WO2025059785A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993006367A1 (fr) * 1991-09-25 1993-04-01 Grupping Arnold Systeme d'emmagasinage souterrain d'energie
DE102004046316A1 (de) 2004-09-24 2006-03-30 Linde Ag Verfahren und Vorrichtung zum Verdichten eines gasförmigen Mediums
WO2008031527A1 (fr) 2006-09-13 2008-03-20 Linde Aktiengesellschaft Compresseur sans piston
WO2008139267A1 (fr) 2007-05-09 2008-11-20 Ecole Polytechnique Federale De Lausanne (Epfl) Systèmes d'accumulation d'énergie
WO2012160311A2 (fr) * 2011-05-23 2012-11-29 Storewatt Dispositif pour le stockage et la restitution de fluides et méthode pour stocker et restituer un gaz comprimé dans un tel dispositif
DE102012003288B3 (de) 2012-02-20 2013-03-14 Iván Cyphelly Flüssigkolbenanordnung mit Plattentauscher für die quasi-isotherme Verdichtung und Entspannung von Gasen
WO2017198725A1 (fr) 2016-05-17 2017-11-23 Enairys Powertech Sa Systèmes et procédés de compression/détente de gaz à étages multiples hybrides
WO2019219801A1 (fr) 2018-05-16 2019-11-21 Ryba Solutions Gmbh Procédés, systèmes et appareils de compression, expansion et/ou stockage d'un gaz

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993006367A1 (fr) * 1991-09-25 1993-04-01 Grupping Arnold Systeme d'emmagasinage souterrain d'energie
DE102004046316A1 (de) 2004-09-24 2006-03-30 Linde Ag Verfahren und Vorrichtung zum Verdichten eines gasförmigen Mediums
WO2008031527A1 (fr) 2006-09-13 2008-03-20 Linde Aktiengesellschaft Compresseur sans piston
WO2008139267A1 (fr) 2007-05-09 2008-11-20 Ecole Polytechnique Federale De Lausanne (Epfl) Systèmes d'accumulation d'énergie
WO2012160311A2 (fr) * 2011-05-23 2012-11-29 Storewatt Dispositif pour le stockage et la restitution de fluides et méthode pour stocker et restituer un gaz comprimé dans un tel dispositif
DE102012003288B3 (de) 2012-02-20 2013-03-14 Iván Cyphelly Flüssigkolbenanordnung mit Plattentauscher für die quasi-isotherme Verdichtung und Entspannung von Gasen
WO2017198725A1 (fr) 2016-05-17 2017-11-23 Enairys Powertech Sa Systèmes et procédés de compression/détente de gaz à étages multiples hybrides
WO2019219801A1 (fr) 2018-05-16 2019-11-21 Ryba Solutions Gmbh Procédés, systèmes et appareils de compression, expansion et/ou stockage d'un gaz
EP3794238A1 (fr) * 2018-05-16 2021-03-24 Green-Y Energy Ag Procédés, systèmes et appareils de compression, expansion et/ou stockage d'un gaz

Also Published As

Publication number Publication date
CH721148A1 (de) 2025-03-31

Similar Documents

Publication Publication Date Title
EP2748434B1 (fr) Installation de stockage d'énergie thermique
DE102008042828B4 (de) Verfahren und Vorrichtung zum Betreiben eines Stirling-Kreisprozesses
WO2013045463A1 (fr) Installation de stockage d'énergie thermique et son procédé de fonctionnement
EP2489840A1 (fr) Accumulateur d'énergie et son procédé de fonctionnement
WO2019219801A1 (fr) Procédés, systèmes et appareils de compression, expansion et/ou stockage d'un gaz
WO2012100275A2 (fr) Moteur thermique
WO2025059785A1 (fr) Dispositif à piston liquide et procédé de compression et de dilatation d'un gaz
DE10018612C1 (de) Anlage zur Befüllung von Gastanks
DE102021102231A1 (de) Elektrisches Energiespeichersystem und Verfahren zur Ein- und Ausspeicherung elektrischer Energie sowie Computerprogramm
WO2021228569A1 (fr) Système de stockage et de récupération d'énergie
DE102019002370A1 (de) Hydraulische Kolbeneinrichtung, welche mindestens zum Zwecke einer Gasverdichtung verwendbar ist, Druckgasenergiewandlungseinrichtung, Druckgasenenergiewandlungs-Wärmetauscher-Einrichtung, Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung und Druckgasenenergiewandlungsvorrichtung
DE102011075557A1 (de) Leitungskreis und Verfahren zum Betreiben eines Leitungskreises zur Abwärmenutzung einer Brennkraftmaschine
DE10338388B3 (de) Verfahren zur Regelung einer Klimaanlage
DE10160593B4 (de) Wärmekraftanlage
DE102019006695A1 (de) Hydraulische Kolbeneinrichtung, welche mindestens zum Zwecke einer Gasverdichtung verwendbar ist, Druckgasenergiewandlungseinrichtung, Druckgasenergiewandlungs-Wärmetauscher-Einrichtung, Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung und Druckgasenergiewandlungsvorrichtung
AT510459B1 (de) Wärmemotor sowie eine anlage, in welcher der erfindungsgemässe wärmemotor betrieben wird
DE102023131626B4 (de) Anordnung und Verfahren zur Umwandlung thermischer Energie
EP4279741B1 (fr) Système de compression de gaz et procédé de récupération de l'hydrogène
DE2711287A1 (de) Kuehlkreislauf fuer ein kraftwerk sowie verfahren zum betrieb des kuehlkreislaufes
AT527260A1 (de) Vorrichtung mit einer Wärmekraftmaschine und einer damit antreibbaren Pumpe
EP3147466B1 (fr) Machine a energie hydraulique
WO2023011997A1 (fr) Moteur thermique
WO2025223840A1 (fr) Circuit de fluide frigorigène
DE102024200056A1 (de) Versorgungssystem für einen Energiewandler
DE102015009975A1 (de) Hydrostirling-Maschine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 24794701

Country of ref document: EP

Kind code of ref document: A1