EP3781815B1 - Kompressorvorrichtung und kompressionsverfahren - Google Patents

Kompressorvorrichtung und kompressionsverfahren Download PDF

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Publication number
EP3781815B1
EP3781815B1 EP19723320.8A EP19723320A EP3781815B1 EP 3781815 B1 EP3781815 B1 EP 3781815B1 EP 19723320 A EP19723320 A EP 19723320A EP 3781815 B1 EP3781815 B1 EP 3781815B1
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EP
European Patent Office
Prior art keywords
drive
compression
chamber
piston
gas
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EP19723320.8A
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German (de)
English (en)
French (fr)
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EP3781815A1 (de
Inventor
Stephan HILLEBRAND
Patrick ZEISBERG
Nils Friedrich
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Sera GmbH
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Sera GmbH
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    • 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
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—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
    • F04B25/00—Multi-stage pumps
    • 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
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/18—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use for specific elastic fluids
    • 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
    • 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
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • 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
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible

Definitions

  • the invention relates to a compressor device and a compression method with the features of independent claims 1 and 13.
  • Such compressor devices are suitable, for example, for applications in the process industry, in mechanical engineering or in the hydrogen economy, where it is necessary to compress a gas for transport, storage, processing or use.
  • the gas to be compressed can be, for example, a non-corrosive, solid-free gas such as hydrogen, helium, carbon dioxide, argon, nitrogen or ethylene. In principle, other gases or gas mixtures can also be compressed.
  • a non-corrosive, solid-free gas such as hydrogen, helium, carbon dioxide, argon, nitrogen or ethylene.
  • other gases or gas mixtures can also be compressed.
  • Hydraulically driven piston compressors are known from the prior art, which can be driven by means of a drive cylinder.
  • the drive is carried out by a movement of a drive piston, which is connected to a compression piston with a mechanical connecting means, such as a piston rod, with which a volume change of a compression space - and thus a gas compression - is periodically brought about.
  • a hydraulically driven piston compressor can, for example, have a compression piston and a drive piston coupled to the compression piston (2-piston principle).
  • a coupling of two compression pistons with a drive piston (3-piston principle) is also possible.
  • the use of a plurality of compression pistons can be used to compress a larger volume of the gas per unit of time or to increase the compression of the gas.
  • the gas can first be compressed in a first compression cylinder and then flow into a second and possibly a plurality of further compression cylinders and be further compressed.
  • any number of such compression levels is conceivable.
  • print EP 0 064 177 A1 For example, a 3-piston compressor device with up to four compression stages is described.
  • a general problem when operating a hydraulically driven piston compressor is possible contamination of the gas, for example a sensitive gas such as hydrogen, by the hydraulic fluid, for example hydraulic oil, or contamination by unwanted particles. Contamination can occur, for example, by spreading into the compression space along the piston rod.
  • the invention is based on the task of providing an improved compressor device in which, in particular, the risk of contamination of the gas is reduced.
  • a compressor device for compressing a gas comprises at least one compression space in at least one compression cylinder.
  • At least one drive piston is arranged in at least two drive cylinders.
  • the drive pistons separate the at least two drive cylinders into two drive chambers.
  • the at least one first or second drive chamber can be periodically pressurized with a hydraulic fluid to move the respective drive piston.
  • Such a compressor device can be formed, for example, by a piston compressor hydraulically driven with hydraulic oil, which is used for compression of gases such as hydrogen or helium in the at least one compression cylinder.
  • the at least one compression space can be formed, for example, by a, in particular cylindrical, cavity in the at least one compression cylinder.
  • the gas can, for example, flow into the at least one compression cylinder through a valve-controlled gas inlet and flow out through a valve-controlled gas outlet.
  • At least one drive piston is arranged in each of the at least two drive cylinders, which separates the at least two drive cylinders into two drive chambers.
  • the first drive piston when the hydraulic fluid flows into the at least one first drive chamber, the first drive piston is moved in the drive cylinder and the at least one first drive chamber enlarges. Since the first drive piston divides the first drive cylinder into two partial spaces, the remaining drive space can be reduced accordingly.
  • the remaining drive spaces in the at least two drive cylinders are non-positively connected to one another through a fluid via a connecting piece. Such a non-positive connection can also be understood as a fluidic coupling.
  • the remaining drive spaces can be, for example, a third and a fourth drive space.
  • the periodic application of hydraulic fluid to the drive spaces can cause the drive pistons to move periodically coupled to one another due to the fluidic coupling.
  • one drive space becomes larger as the other becomes smaller.
  • the fluidic coupling can cause the smaller drive space to release the fluid to the other coupled drive space, which increases accordingly.
  • the movement of the drive pistons can thus be synchronized.
  • the movement can take place in the sense of a differential cylinder, in which the at least one first drive piston carries out an opposite movement to the at least one second drive piston.
  • the at least one first drive piston can also carry out a parallel movement to the at least one second drive piston in the sense of a synchronous hydraulic cylinder.
  • the operation of a synchronous hydraulic cylinder is generally more complex than the operation of a differential cylinder.
  • Undesirable leaks can occur between the at least one first and second drive chamber and the remaining drive chambers. This occurs particularly during operation from a high-pressure to a low-pressure side. The leaks can result in the movement of the drive pistons not being synchronized.
  • a synchronization device can be provided in one embodiment. The synchronization device can correct the movement of the drive pistons.
  • the synchronization device can be formed, for example, by a pressure compensation line.
  • the pressure compensation line can be arranged at one end of a drive chamber, at which the movement of an associated drive piston is reversed.
  • the drive piston can be bridged using the pressure compensation line.
  • the fluid pressure between the two drive chambers of the drive cylinder in question can be synchronized by means of the pressure compensation line.
  • the pressure equalization line can also have a check valve. This principle can be understood as a healing or automatic stroke correction of the drive pistons.
  • the movement of the drive pistons can be transferred via at least one mechanical connecting means to at least one compression piston movably arranged in the at least one compression cylinder.
  • the at least one compression piston delimits the at least one compression space in the at least one compression cylinder on one side, so that movements of the drive pistons can be converted into a change in volume of the at least one compression space.
  • At least one compression piston can be driven by at least two drive pistons. In particular, two drive pistons can each drive a compression piston.
  • the at least one compression cylinder is spatially separated from the at least two drive cylinders by a distance.
  • the distance can refer to a distance between the at least one compression cylinder and the at least two drive cylinders along a direction of movement of the at least one drive piston.
  • the distance can be extended along the force of gravity. This can minimize the risk of contamination of the gas to be compressed.
  • the at least one compression cylinder does not have a common wall with the at least two drive cylinders.
  • a wall can be formed, for example, by a compression cylinder housing of the at least one compression cylinder or a drive cylinder housing of the at least two drive cylinders.
  • a common wall can be present if the compression cylinder housing borders the drive cylinder housing.
  • a common wall can mean that the compression cylinder is in contact with one of the at least two drive cylinders. For example, there may be a metallic contact.
  • the distance between the compression cylinders and the drive cylinder is at least as large as a maximum distance that one of the at least one drive piston covers in the associated drive cylinder.
  • the distance can in particular correspond to a stroke length of the at least one drive piston.
  • the distance can therefore be understood as a distance between two positions of one of the at least one drive piston.
  • the volume of an associated drive space can be minimal.
  • the hydraulic fluid can change from flowing out of the drive chamber to flowing into the drive chamber.
  • the volume of the drive chamber can be maximum. In the second position, the hydraulic fluid can switch from flowing into the drive chamber to flowing out of the drive chamber.
  • the length can therefore also be understood as the maximum stroke or as the maximum distance that the drive piston covers in the drive cylinder.
  • At least one connection space is arranged between the at least one compression cylinder and the at least two drive cylinders, which can be filled with a functional gas, in particular for flushing the at least one connection space, for detecting leaks in the at least one connection space and/or for blocking the at least one connection space.
  • a first connection space can extend from the at least one first drive cylinder to the at least one compression cylinder.
  • the second connection space can extend from the at least one second drive cylinder to the at least one compression cylinder.
  • a common connection space can extend from the at least one first drive cylinder and second drive cylinder to the at least one compression cylinder or several compression cylinders.
  • the at least one mechanical connecting means can extend from the at least one first drive cylinder and/or the at least one second drive cylinder to the at least one compression cylinder through the at least one connection space.
  • the at least one connection space can be surrounded, for example, by a connection housing.
  • the connection housing can delimit the at least one connection space in a gas-tight manner. Therefore, the at least one mechanical connecting means can be protected by the at least one connecting space, for example from external contamination such as unwanted gases and particles.
  • the at least one connection space is filled with a functional gas.
  • the at least one connection space can be filled with a purge gas. Using the flushing gas, undesirable gases and particles can be removed from the at least one connecting space by flushing the connecting space.
  • the at least one connecting space is filled with a leakage gas.
  • a leak gas can be used, for example, to detect leaks in the at least one connection space.
  • the at least one connection space can be filled with a sealing gas. The gas can serve to block the at least one connection space for gaseous media. For example, a sealing gas can prevent the penetration of undesirable substances into the at least one connecting space.
  • the at least one compression cylinder and the at least two drive cylinders can be spaced apart from one another via the at least one connecting space.
  • the at least one connection room can do at least this be long, such as a maximum distance that one of the at least one drive piston covers in the associated drive cylinder.
  • the distance between the at least two drive cylinders and the at least one compression cylinder can therefore be encompassed by the at least one connecting space.
  • the at least one connecting space can form a spacing space via which the at least two drive cylinders are spaced apart from the at least one compression cylinder.
  • the at least one connecting space can in particular be designed as a lantern, so that oil-free compression is possible.
  • At least one measuring device can also be arranged in at least one of the two drive spaces, with which, for example, a position of the at least one drive piston in the associated drive cylinder can be determined.
  • the specific position can serve to determine at what point in time fluid pressure should be applied to the at least one first and second drive chamber.
  • a reversal of movement of the at least one drive piston can be controlled.
  • the at least one measuring device can be formed, for example, by a position sensor.
  • the at least one measuring device can also be formed by a position measuring system, which can be arranged, for example, on the at least one drive cylinder.
  • the at least one measuring device is arranged in the at least one connection space in order to determine a position of the at least one mechanical connection means.
  • a further example of an arrangement of the at least one measuring device is on the at least one compression cylinder in order to determine a position of the at least one compression piston.
  • the at least two drive cylinders are arranged below the at least one compression cylinder. Below can be understood in relation to the earth's gravity.
  • the at least two drive cylinders are therefore arranged lower along the earth's gravity than the at least one compression cylinder. This means that, for example, hydraulic fluid that has escaped from a drive chamber cannot escape due to the gravity of the earth at least two drive cylinders, spread in the direction of the at least one compression cylinder.
  • a seal in particular a labyrinth seal, can be provided between the at least one compression cylinder and the at least one compression piston and/or the at least one mechanical connecting means.
  • a cooling device to be arranged on the at least one compression cylinder, which dissipates waste heat generated during operation of the at least one compression cylinder.
  • the cooling device can be designed, for example, as air or water cooling.
  • the compressed gas it is also possible for the compressed gas to form a multi-stage compression to be conducted from a first compression space as a gas to be further compressed into a second, third or fourth compression space for compression.
  • the gas to be further compressed can be directed into any number of further compression spaces for further compression.
  • a valve device can be provided to decouple the movement of the drive pistons.
  • hydraulic actuation of the drive pistons can be decoupled by means of the valve device.
  • the valve device can be controllable depending on data, information and/or process parameters, which can be generated, for example, by means of the at least one measuring device.
  • the valve device can be controlled by a control system.
  • the control system can control the application of the hydraulic fluid to the at least one first and second drive chamber by means of the valve device.
  • the control system can access data, in particular position data or movement data, from the at least one measuring device.
  • the control system can access process parameters such as fluid pressure or amount of hydraulic fluid delivered (flow rate) for control purposes.
  • FIG. 1 An embodiment of a compressor device 100 is shown, which has a compression space 1a, 1b in a respective compression cylinder 2a, 2b for a gas.
  • the compression cylinders 2a, 2b are arranged here vertically, parallel to one another, with the gas entering (to be compressed) from the compression spaces 1a, 1b or the exiting (compressed gas) being shown by double arrows on the end face of the compression cylinder.
  • the compression spaces 1a, 1b each have a gas inlet 5a, 6a and a gas outlet 5b, 6b.
  • the gas inlet 5a, 6a and the gas outlet 5b, 6b can be formed by gas valves (not shown).
  • the volume of the compression spaces 1a, 1b is periodically changed during the compression process via compression pistons 3a, 3b.
  • the compression pistons 3a, 3b each delimit the compression spaces 1a, 1b so that they can move downwards in the compression cylinder 2a, 2b.
  • the compression pistons 3a, 3b only perform work during one stroke, i.e. they are single-acting.
  • the compressor device 100 is aligned so that the earth's gravity points downwards. It is also conceivable and possible to align the compressor device 100 in any way with respect to the gravity of the earth. For example, the compressor device 100 can be aligned horizontally to the earth's gravity.
  • the drive cylinders 12a, 12b are each arranged coaxially to one another below the at least one compression cylinder 2a, 2b. In other In exemplary embodiments (not shown), the drive cylinders 12a, 12b are arranged above the at least one compression cylinder 12a, 12b.
  • drive pistons 13a, 13b which are arranged in the two drive cylinders 12a, 12b, serve to drive the compression pistons 3a, 3b.
  • the two drive pistons 13a, 13b divide the interior spaces of the drive cylinders 12a, 12b into two drive spaces 11a, 11b, 11c, 11d.
  • the volume of the drive spaces 11a, 11b, 11c, 11d can vary.
  • the sum of the volumes of the drive spaces 11a, 11b, 11c, 11d in each drive cylinder 12a, 12b is constant.
  • the first and second drive chambers 11a, 11b are periodically supplied with a hydraulic fluid.
  • the incoming and outgoing hydraulic fluid is shown by double arrows (hydraulic fluid access 18a, 18b).
  • hydraulic fluid access 18a, 18b hydraulic fluid access 18a, 18b.
  • the drive piston 13a moves upward. The movement takes place along the movement axes Ba, Bb.
  • a third and fourth drive chamber 11c, 11d is arranged, which are fluidly connected to one another via a connecting piece (15).
  • the drive pistons 13a, 13b are coupled to the compression pistons 3a, 3b via at least one mechanical connecting means 20a, 20b, here a straight rod.
  • the drive cylinders 12a, 12b and the compression cylinders 2a, 2b are each aligned one above the other.
  • the compression cylinders 2a, 2b are spatially separated from each other by a distance Da, Db from the two drive cylinders 12a, 12b.
  • a distance Da, Db from the two drive cylinders 12a, 12b.
  • the distances Da, Db also ensure that the compression cylinders 13a, 13b do not have a common wall with the drive cylinders 12a, 12b; the compression cylinders 2a, 2b and the drive cylinders 12a, 12b are separated from one another, in particular spatially, fluidically and also thermally.
  • the distance Da, Db can be chosen to be at least as long as the maximum distance that one of the drive pistons 13a, 13b covers in the associated drive cylinder 12a, 12b.
  • At least one connection space 30a, 30b is arranged between the compression cylinders 2a, 2b and the drive cylinders 12a, 12b, which is filled with a functional gas for flushing the at least one connection space 30a, 30b, for detecting leaks in the at least one connection space 30a, 30 and/or can be filled to block the at least one connection space 30a, 30b.
  • the at least one connection space 30a, 30b is surrounded by a connection housing 40a, 40b.
  • a cooling device 8a, 8b with which the compression cylinders 2a, 2b can be cooled in order to dissipate the waste heat generated during operation.
  • the cooling device is designed as water cooling; the water flowing in and out is represented by arrows. Water cooling is particularly useful for higher compressor outputs.
  • a measuring device 17 is shown schematically, with which the position of one of the drive pistons 13a, 13b can be determined.
  • the measuring device 17 is formed by a position sensor.
  • a stroke of 500 mm can be achieved.
  • the total height of the device would then be approximately 1,800 mm. In principle, other dimensions can also be achieved.
  • Fig. 1 a single-acting, single-stage, water-cooled compressor device 100 with a rod-side hydraulic coupling.
  • the term rod-side here refers to the relative arrangement to the mechanical connecting means 20a, 20b (rod).
  • FIG. 2 A second embodiment is shown, which is also single-acting, single-stage and hydraulically coupled on the rod side, but which has air cooling.
  • rib devices are arranged around the compression spaces 1a, 1b as a cooling device. Otherwise the function corresponds to the first embodiment.
  • FIG. 3 A third embodiment is shown, which is a further variant of the embodiment Fig. 1 represents.
  • this one has water cooling.
  • the hydraulic coupling takes place via the connecting piece 15 on the piston side and not rod side.
  • the hydraulic fluid supply lines 18a, 18b lie above the drive pistons 13a, 13b, ie on the rod side.
  • Compressor devices of the type shown here can also be designed as two-stage compressors.
  • Fig. 4 a single-acting, two-stage, water-cooled variant with a rod-side hydraulic coupling.
  • the fourth embodiment corresponds to the first embodiment.
  • a connecting line 60 between the first compression space 1a and the second compression space 1b is shown here, with which two-stage compression can optionally be achieved.
  • FIG. 5 Another variant is shown. As in the first embodiment, there is a water-cooled compression device 100 in which there is a rod-side hydraulic coupling of the drive spaces 11c, 11d.
  • the compression space 1a, 1b is designed such that the compressor device 100 works double-acting, i.e. each stroke of the compression piston 3a, 3b does work. Accordingly, the compression spaces 1a, 1b, 1c, 1d, 1e, 1f each have an inlet and an outlet.
  • a further advantage of the compressor device 100 results from the hydraulically coupled drive cylinders 12a, 12b. Due to the fact that the two compression pistons 3a, 3b are each driven by their own drive cylinder 12a, 12b, the stroke of a first cylinder can be varied during operation independently of the second drive cylinder by setting up a suitable hydraulic circuit. An embodiment of this is in the Fig. 6a, 6b shown.
  • This decoupling is particularly advantageous when compressing gases to a constant outlet pressure with a decreasing inlet pressure (e.g. emptying bottles). Due to the falling inlet pressure, the intermediate pressure also drops in a two-stage system, since the two stages only reach a certain level Application (small area). A deviation from this design point is tolerated to a small extent, for example through a specified pressure range in the gas inlet. Too large a deviation leads to unbalanced and unfavorable compression ratios in one of the two stages, depending on whether the permissible range is exceeded or undershot. This results in excessive, unintended heat development, which can cause damage to components. This principle also applies analogously to container filling, in which the initial pressure varies and in particular increases.
  • the two stages Due to the possibility of driving a variable stroke in one of the two drive cylinders 12a, 12b, the two stages can be adapted to changing operating conditions during operation. This avoids unnecessary heat development due to very different compression ratios in the two stages and the inlet pressure can be operated optimally over a larger range (especially in small pressure ranges).
  • This stroke adjustment is achieved by changing the hydraulic guidance in the drive cylinders 12a, 12b.
  • one of the drive pistons remains stationary during the stroke, and the drive piston coupled to it can complete the stroke by rerouting the oil.
  • the stroke of the two drive pistons 13a, 13b can thus be decoupled from one another by means of a suitable valve device 52.
  • a pressure compensation line 16a, 16b is arranged at one end of the third and fourth drive chambers 11c, 11d, at which the movement of the respective drive piston 13a, 13b is reversed.
  • the pressure compensation line 16a, 16b bridges in a position of the drive piston 13a, 13b in which the reversal of the Movement takes place, the drive piston 13a, 13b, so that the two drive spaces 11a, 11c, 11b, 11d of a drive cylinder 12a, 12b can be connected via the pressure compensation line 16a, 16b.
  • the pressure compensation line 16a, 16b has a check valve 161a, 161b.
  • Fig. 7 is a modification of the embodiment according to Fig. 5 shown so that reference can also be made to the above description.
  • a four-stage compression is implemented here, in which the first compression space 1a forms the first stage.
  • the compressed gas is fed to a second stage in the compression space 1b via the gas outlet 5b and the gas inlet 6a.
  • the gas is then fed to a third stage via the gas outlet 6b of this compression space 1b, which is implemented in a third compression space 1c.
  • the gas is then fed back to the first compression cylinder, in which a fourth compression stage is implemented in the compression space 1d.
  • the gas flow between the two compression cylinders is shown by arrows.
  • the size of the compression spaces 1a, 1b, 1c, 1d may need to be adapted to the compression task.
  • At least two-stage compression is realized, in which the first compression space 1a and the fourth compression space 1d form the first stage.
  • the gas to be compressed is supplied to the first compression space 1a and the fourth compression space 1d via a gas inlet 5a, 5a ⁇ .
  • the gas to be compressed is in particular alternately supplied to the first compression space 1a and the fourth compression space 1d.
  • the compressed gas is supplied to a second stage in the compression spaces 1b, 1c as gas to be further compressed via a respective gas outlet 5b, 5b'.
  • the gas to be further compressed is supplied to the second compression space 1b and the third compression space 1c via a respective gas inlet 6a, 6a'.
  • the gas from the first compression space 1a is supplied to the second compression space 1b and the gas from the fourth compression space 1d is supplied to the third compression space 1c.
  • the gas from the second compression space 1b and the third compression space 1c is continued through a gas outlet 6b, 6b'.
  • the compressor devices of the Fig. 8A and Fig. 8B include four compression cylinders 2a, 2b, 2c, 2d.
  • the compressor devices therefore essentially correspond to the exemplary embodiment of Fig. 7 , whereby the two compression cylinders 2c, 2d are supplemented.
  • a cooling device 8c, 8d is arranged on the compression cylinders 2c, 2d, with which the compression cylinders 2c, 2d can be cooled.
  • the movement of the drive pistons 13a, 13b can be transferred via a mechanical connecting means 20a, 20b to four compression pistons 3a, 3b, 3c, 3d, each of which is movably arranged in a compression cylinder 2a, 2b, 2c, 2d.
  • Two compression pistons 3a, 3b, 3c, 3d are arranged on each of the mechanical connecting means 20a, 20b.
  • the compression pistons 3a, 3b, 3c, 3d can divide the compression cylinders 2a, 2b, 2c, 2d into two compression spaces, in each of which gas can be compressed independently of one another or in several stages.
  • An order in which the gas is passed through the compression spaces of the compressor device for compression can be chosen arbitrarily.
  • a number of stages of compression and / or a number of simultaneously operated, possibly multi-stage, compressions can be selected arbitrarily.
  • Fig. 8A Gas is compressed in the first compression space 1a and then supplied to the second compression space 1b. Regardless of this, gas is compressed in a fifth compression space 1e of the third compression cylinder 2c. The gas to be compressed is fed to the fifth compression space 1e via a gas inlet 7a. The compressed gas is compressed via a gas outlet 7b Gas is supplied as gas to be further compressed to a further stage in a sixth compression space 1f. The gas to be further compressed is supplied to the sixth compression chamber 1f via a gas inlet 7a'. The further compressed gas is continued from the sixth compression chamber 1f via a gas outlet 7b'.
  • the gas can also be compressed in more than two stages.
  • a four-stage compressor device is in Fig. 8B shown.
  • gas is supplied to the gas inlet 7a of the fifth compression space 1e, in which a third compression stage is realized.
  • the gas is then fed to a fourth stage via a gas outlet 7b of the compression space 1e, which is implemented in a sixth compression space 1f.
  • the gas is supplied to the sixth compression space 1f via a gas inlet 7a ⁇ .
  • the gas compressed in the sixth compression chamber 1f is passed on for further processing via a gas outlet 7b'.
  • the diameters of the drive pistons 3a, 3d are larger than the diameters of the drive pistons 3b, 3c. Basically, the size of the drive pistons 3a, 3b, 3c, 3d as well as the size of the compression spaces 1a, 1b, 1c, 1d must be adapted to the compression task if necessary.
  • FIG. 8C An alternative routing of the gas through the compressor device is in Fig. 8C shown.
  • the compressed gas is supplied therein as gas to be further compressed via the gas outlets 5b, 5b' to a second stage in the compression space 1c.
  • the gas to be further compressed is supplied to the second compression space 1b and the third compression space 1c via a respective gas inlet 6a, 6a'. From the third compression space 1c, the further compressed gas is fed to the fifth compression space 1e. Thereafter, the gas is supplied to the fourth stage of the sixth compression space 1f.
  • the gas can be made available for further processing starting from the third stage from the fifth compression chamber 1e, as in Fig. 8D is shown.
  • the movement of the drive piston 13a can be transferred to a compression piston 3a via the mechanical connecting means 20a, the movement of the drive piston 13b being transferable to two compression pistons 3b, 3c via the mechanical connecting means 20b.
  • any one Number of compression pistons connected to the mechanical connecting means 20a, 20b as well as any guidance of the gas to be compressed, compressed and further compressed in the compression spaces is conceivable and possible.
  • the size of the compression spaces 1a, 1b, 1c, 1d, 1e, 1f may need to be adapted to the compression task.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)
EP19723320.8A 2018-04-19 2019-04-18 Kompressorvorrichtung und kompressionsverfahren Active EP3781815B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018109443.4A DE102018109443B4 (de) 2018-04-19 2018-04-19 Kompressorvorrichtung und Kompressionsverfahren
PCT/EP2019/060176 WO2019202115A1 (de) 2018-04-19 2019-04-18 Kompressorvorrichtung und kompressionsverfahren

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DE102019133576B3 (de) * 2019-12-09 2020-12-17 Maximator Gmbh Kompressor und Verfahren zur Förderung und Verdichtung eines Förderfluids in ein Zielsystem
DE102021132879B3 (de) 2021-12-14 2023-03-23 Sven Anders Einstufiger Kolbenkompressor
KR102442561B1 (ko) * 2022-05-19 2022-09-13 주식회사 덕양에코 액체 가압형 가스압축장치
DE102022207571A1 (de) 2022-07-25 2024-01-25 Sera Gmbh Vorrichtung zur Kompression und Speicherung eines gasförmigen Mediums
DE102022004729A1 (de) * 2022-12-16 2024-06-27 Oerlikon Textile Gmbh & Co. Kg Dosierpumpe zum Zuführen eines Fadenfixierfluids
KR102540129B1 (ko) * 2022-12-30 2023-06-07 한영테크노켐(주) 액체씰을 적용한 수소 압축 시스템

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DE102018109443B4 (de) 2020-10-01
JP2021522446A (ja) 2021-08-30
WO2019202115A1 (de) 2019-10-24
CN112005010B (zh) 2023-10-10
CA3097754A1 (en) 2019-10-24
US20210164455A1 (en) 2021-06-03
ES2966997T3 (es) 2024-04-25
EA202092337A1 (ru) 2021-02-15
DE102018109443A1 (de) 2019-10-24
EP3781815A1 (de) 2021-02-24
CN112005010A (zh) 2020-11-27

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