EP4285026A1 - Dispositif de transport - Google Patents

Dispositif de transport

Info

Publication number
EP4285026A1
EP4285026A1 EP22722755.0A EP22722755A EP4285026A1 EP 4285026 A1 EP4285026 A1 EP 4285026A1 EP 22722755 A EP22722755 A EP 22722755A EP 4285026 A1 EP4285026 A1 EP 4285026A1
Authority
EP
European Patent Office
Prior art keywords
conveying
fluid
dosing
volume
piston
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
EP22722755.0A
Other languages
German (de)
English (en)
Inventor
Wolfgang Hahmann
Frank Bauer
Peter Kloft
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.)
Hydac Technology GmbH
Original Assignee
Hydac Technology GmbH
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 Hydac Technology GmbH filed Critical Hydac Technology GmbH
Publication of EP4285026A1 publication Critical patent/EP4285026A1/fr
Pending legal-status Critical Current

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
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/10—Pumps having fluid drive
    • F04B43/113—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • F04B43/1136—Pumps having fluid drive the actuating fluid being controlled by at least one valve with two or more pumping chambers in parallel
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping 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
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/10—Pumps having fluid drive
    • F04B43/113—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/022—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows with two or more bellows in parallel
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/024—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows with two or more bellows in series
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/033—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive
    • F04B45/0336—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive the actuating fluid being controlled by one or more valves
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working 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
    • 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
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F04B9/103—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 only one pumping chamber
    • F04B9/105—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 only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • 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
    • F04B9/1172—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 pump piston in the two directions being obtained by a double-acting piston liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators

Definitions

  • the invention relates to a conveying device for fluids with an inlet and an outlet and a conveying part connected in between, which can be actuated by a drive part.
  • WO 2013/079222 A2 discloses a delivery device for improving the energy efficiency of hydraulic systems, with an actuator that works as a consumer of hydraulic energy in one operating state and as a generator of hydraulic energy in another operating state, and with a hydraulic accumulator that, in one operating state of the The actuator can be charged by this for energy storage and can be discharged in the other operating state for delivering energy to the actuator.
  • a discontinuous, adjustable hydropneumatic piston accumulator is used as the hydraulic accumulator, in which several pressure chambers are formed, which adjoin different sized effective surfaces on the fluid side of the accumulator piston.
  • an adjustment arrangement which connects a selected pressure chamber or several selected pressure chambers of the piston accumulator to the actuator depending on the respective pressure levels prevailing on the gas side of the piston accumulator and on the actuator.
  • the invention is based on the object of improving the known solution in such a way that a leak-free conveying device is created with which contamination is prevented from entering the fluid to be conveyed or compressed.
  • a pertinent task solves a conveyor with the features of claim 1 in its entirety.
  • the delivery part is a fluid-tight media separator with variable Has chamber volume, which enters into a fluid-conducting connection with the inlet or outlet with its receiving space and which, by means of the drive part, takes in fluid via the inlet as part of an intake stroke while increasing the chamber volume and reduces the recorded fluid in the context of a discharge stroke while reducing this chamber volume emits via the outlet, it is ensured that no leaks occur in the conveying part and that no contamination enters the fluid to be conveyed or compressed.
  • the fluid-tight media separating device ensures that no medium can get from the drive side to the delivery side for the fluid, and in this respect any contamination entry on the transport fluid side is avoided.
  • Incompressible fluids such as any type of liquids
  • compressible media for example in the form of high-purity gases such as hydrogen, which are compressed in the process.
  • a promotion or compression of fluids composed of compressible and incompressible parts is also possible, please include. In that regard, an unintentional entry of a working gas on the liquid side is equally avoided.
  • the media separating device is formed from a bellows, which is controlled fluidically from the outside by means of the drive part in such a way that the inner chamber volume of the bellows increases during an intake stroke and decreases during a discharge stroke .
  • the bellows used as a media separating device usually in the form of a conventional bellows, is considered to be absolutely media-tight in practice, i.e. a medium cannot get through the bellows wall either from the inside to the outside or vice versa, and with a corresponding design in stainless steel, the media separating device is also resistant to embrittlement What hydrogen applications to look at.
  • the drive part has a hydraulic working cylinder which can be controlled by means of a hydraulic drive and a main valve.
  • the delivery part which can also act as a compressor part, can be controlled using conventional hydraulic components for the drive part.
  • the components of the drive part mentioned can be standardized and thus easily adapted to the desired conveying and compression capacity for the conveying part or compressor part.
  • the hydraulic working cylinder with its piston-rod unit with a metering chamber with a metering volume that can be predetermined specifies the intake and discharge stroke for the delivery part, preferably on the piston side, and that the operation of the working cylinder is preferably carried out on the rod side via the main valve takes place.
  • the dosing volume mentioned is almost incompressible, so that a movement of the hydraulic working cylinder as a so-called pump cylinder can be transferred to the media separating device without any loss or delay.
  • the function can also be swapped from the piston side to the rod side. In this way, pressure can be increased in both directions.
  • a further delivery part is provided to obtain a uniform delivery volume flow, which carries out a discharge stroke while the other delivery part carries out a suction stroke and vice versa.
  • the conveying device can be operated quasi-continuously, in that one conveying part always ensures the delivery of fluid under pressure, while the other delivery part is loaded with fluid for the subsequent delivery stroke in the intake stroke.
  • the further conveying part is also connected to the working cylinder, which has a second piston, forming a further dosing chamber with a predetermined dosing volume, which is connected to the first piston for one dosing chamber with the piston rod.
  • the delivery device can be operated with two delivery parts in a synchronous sequence with only one working cylinder or pump cylinder.
  • the respective conveyor part acts as a compressor part for the delivery of gases, that two compressor parts form a single-stage compressor, and that the interconnection of several single-stage compressors results in a multi-stage compressor.
  • an existing low pressure on the side of the gas inlet can then be brought to a higher medium pressure by means of the first compressor stage, which in turn is converted into high pressure by means of the second compressor stage on the gas outlet side.
  • the conveyor device in particular to compensate for leaks on the working cylinder, there is at least one dosing unit which introduces small amounts of dosing volume into the respective dosing chamber. brings or takes away from it.
  • the dosing unit preferably small volumes can be added to the dosing volume of the working cylinder or pump cylinder or withdrawn from this dosing volume as required.
  • the respective dosing unit is preferably connected to a dosing and dispensing unit by means of dosing valves and the respective dosing unit can be protected by a secondary pressure protection.
  • the metering valves metering processes can be carried out very precisely by means of the metering unit, and the secondary pressure safety device mentioned serves to protect against overloading, which can preferably consist of a pressure relief valve.
  • a function monitoring for the working cylinder or pump cylinder is possible, whereby instead of end position monitoring, another form of cylin dermonitoring can also occur.
  • At least one cooling device is used between individual compression stages. It has been shown that, in particular when using multi-stage compression when conveying and compressing gases such as hydrogen, the temperature can rise significantly, which leads to an unwanted expansion of the gas, which in turn leads to an increase in the drive power required in this respect of the individual conveying or compressor parts, which can be avoided by the mentioned intercooling between the compressor stages.
  • the fluid flow, in particular the gas flow, on the delivery side of each compressor part is monitored by means of contamination sensors. If contamination is detected, even if it is improbable, the relevant part of the conveyor system should be shut down immediately so that any parts that are dirty or have become unusable can be replaced as part of maintenance work. Particularly when conveying or transporting high-purity gases, such as hydrogen, there must be no particulate contamination in the gas flow within the scope of the intended use, for example within the scope of fuel cell operation.
  • the compressor solution according to the invention not only facilitates an adaptation to the required compressor mass flows by appropriate scaling of the media separation devices according to size and number, but also allows a simple adaptation of the compression ratios themselves its components for a large number of conveying and compressor parts only once and not repeatedly. Accordingly, a preferred use of the delivery device provides for a gradual compression of hydrogen gas using individual, identical compressor parts. This has no equivalent in the prior art.
  • FIG. 3 shows the solution according to FIG. 2 in implementation with fluid components
  • FIG. 4 shows a sequence of two conveying devices in accordance with FIG. 2, forming an overall conveying device
  • FIG. 5 shows the conveying device realized with individual components according to the basic illustration according to FIG. 4; such as
  • FIGS 6 and 7 show two different types of contamination sensors.
  • the conveying part designated as a whole by 10 in FIG. 1, is connected to an inlet 12 and an outlet 14 to carry fluid. Furthermore, the conveyor part 10 has a media separating device 16 in the form of a bellows, in particular in the form of a bellows.
  • the media separating device 16 in the form of a bellows preferably made of metal, separates the liquid speed of a metering volume on the outside of the bellows from the fluid to be conveyed or compressed inside the bellows in a hermetically sealed manner. If the conveying part 10 is used for conveying gases, such as hydrogen gas, the conveying part 10 also functions as a compressor part 10.
  • the bellows itself consists of a very thin metal sheet and is designed to be highly elastic in such a way that the pressure applied from the outside and the pressure prevailing inside the bellows differ by less than 0.1 bar in one embodiment. This means that a fluid pressure applied from the outside, and that can certainly be a pressure of the order of almost 1000 bar, is transferred to the fluid inside the bellows with almost no loss.
  • the stroke volume of the media separation device 16 or the bellows is designed in such a way that it is greater than the displacement of the metering volume that can be generated by a maximum pump cylinder movement of a drive part 18 (Fig. 2), together with a defined clearance at the end positions, so that there is no forced overstretching of the Bellows can come as a result of a pressure difference that occurs across the bellows.
  • a monitoring device is provided on the drive part 18, which will be discussed in more detail, as well as two end position monitors 20 arranged opposite one another for the media separating device 16, which can determine any deviations in this regard.
  • the media separation device 16 shown in FIG. 1 essentially assumes two functions:
  • the separation of the two fluids in the system from one another namely the hydraulic fluid used in the dosing volume from the ultrapure gas to be conveyed and possibly compressed
  • the media separating device 16 in the form of the bellows, allows a hermetic separation and for the conveying and compression function, the bellows has a highly flexible deformability with a large stroke volume.
  • the relevant requirements can be met with an appropriately designed metal bellows.
  • the media separating device 16 is equipped with valves in the form of two reverse check valves 22 acting in opposite directions as so-called compressor valves. So that the media separation device 16 in the form of the bellows can be removed easily and without major gas losses in the event of service, it has a switchable directional control valve 24 on the side of the inlet 12 in the associated fluid channel, which in the blocked state as shown in FIG. 1 allows the fluid to enter locks into the interior of the bellows via the inlet 12 . Since the service case should be carried out as simply and quickly as possible, a defined parting line 26 is provided for this purpose, which, as a standardizable interface, allows a quick change for the respective media separating device 16 .
  • Such a separation point 27 can also run directly above the bellows.
  • a discharge device 28 is also installed so that fluids, such as residual gases in the conveying part 10, can be safely discharged before any dismantling of the media separation device 16.
  • Each of the two check valves 22 is assigned an independent fluid line as an inlet 12 and an outlet 14. which leads to the media separator 16.
  • Comparable to Check valves 22 each have a check valve in an associated line branch, the undisturbed supply and removal of fluid and prevents unwanted backflow in the direction of the fluid source during the delivery stroke with the media separator 16.
  • the correct functioning of the media separation device 16 is constantly monitored, in particular by the two signal transmitters 20 monitoring the end positions, which signal that the associated end positions have been reached during the stroke of the metal bellows. If the metal bellows assumes its maximum extended position with a maximum chamber volume, it actuates the lower end position monitor 20 as seen in the direction of view of FIG. Furthermore, a contamination sensor 30 is housed on the outlet side of the conveying part 10, as shown by way of example in FIGS. 6 and 7, and which monitors the tightness of the metal bellows.
  • the upper end of the bellows is connected to a dividing plate 32, which divides a housing 34 of the delivery part 10 into two separate spaces, with the contamination sensor 32 being arranged in the upper space and a tapping point for the drain device 28 on the inlet side of the delivery part.
  • the second lower space accommodates the bellows, which is hermetically sealed on its underside with a bellows plate 36 and between the outside of the bellows and the inside of the pertinent housing part an intermediate or fluid space 38 is formed, which has a fluid-generating connection 40 with is connected to the drive part 18 and forms the connection for the driving metering volume of the drive part 18 for actuating the conveyor or compressor part 10.
  • the possible directions of fluid flow are shown in FIG. 1 with arrow representations. If the bellows is pulled out by means of the drive part 18 and the directional control valve 24 is switched to its fluid-permeable position, the flow occurs via the inlet 12 and this in the viewing direction of the figure
  • two conveying parts 10 are connected in parallel, which are controlled from alternately by a common drive part 18.
  • fluid is supplied to both one and the other inlet 12 of a conveying part 10 via a common supply line 42 .
  • the outlet 14 of each conveying part 10 is in turn connected to a common discharge line 44 .
  • Fluid is conveyed into the discharge line 44, whereas the other conveying part 10 removes fluid from the supply line 42 by means of a suction stroke.
  • gas is supplied at low pressure via the supply line 42
  • a gas outlet under high pressure is achieved by means of the two conveying or compressor parts 10 in the discharge line 44.
  • high compression ratios of about 1:10, for example, can be achieved.
  • the drive part 18 has a hydraulic working or pump cylinder 46 which can be controlled by means of a hydraulic drive 48 and a main valve 50 .
  • FIG. 4 discloses a dosing unit 52, which saves a small correction volume in the connecting lines between the pump cylinder 46 and the dosing volume 54 or 56 or can remove a small correction volume from these connecting lines.
  • the drive part 18 is shown in more detail with its individual components.
  • the drive part 18 has the hydraulically drivable working or pump cylinder 46, which is driven by the volume flow of a drivable hydraulic pump 58 as the main pump, with the piston-rod unit 60 of the cylinder 46 depending on the switching position of the main valve 50 according to Double arrow moves back and forth.
  • the main pump 58 is driven at a variable speed by means of a motor M and can thus be adapted to the desired delivery and compression output.
  • the cylinder 46 brings the power required for the compression and Wei ter simplify of the fluid or gas by the constant Do sierVolume 54, 56 which is between the cylinder 46 and the respective Me serving separation device 16 of a conveyor part 10, pushes back and forth.
  • a control pump 62 which can supply various auxiliary functions with hydraulic energy, namely, according to FIG.
  • the main valve 50 can also be designed in one stage, because smaller volume flows, for example ⁇ 100 l/min, are then only required.
  • the drive part 18 could also have a piston machine, for example in the form of an in-line piston pump (not shown) driven in rotation via a belwelle cure.
  • the dosing volume 54, 56 is a liquid volume which is referred to as the dosing volume 54, 56 and which is located between the cylinder 46 and the respective media separating device 16 being pushed back and forth.
  • This dosing volume 54, 56 is almost incompressible, so that a movement of the cylinder 46 is transmitted to the respective media separating device 16 without loss and without delay.
  • the respective dosing volume is 54,
  • the rod of the piston-rod unit 60 divides the cylinder 46 into two fluid chambers 64 and 66 on the rod side.
  • the dosing unit 52 which can add small volumes to the respective dosing volume 54, 56 or withdraw them from this dosing volume, serves to compensate for leaks in the working or pump cylinder 46.
  • the dosing unit 52 consists of two small, self-contained reciprocating pistons, which can absorb a small, defined displacement volume (preferably ⁇ 10 cm 3 ) to move from one end position to the other and release it on the other side, which can be done by switching associated directional valves 68, 70 triggered for metering in or metering out becomes.
  • the dosing unit with reciprocating piston and associated directional control valve is labeled 72 in FIG. 3 and the corresponding dosing unit is labeled 74.
  • the respective dosing valve 68, 70 can be switched off again.
  • the dosing volumes 54, 56 are additionally protected by a secondary pressure safety device 76, which consists of a pressure limit valve which is connected via check valves 78 to both dosing volumes 54, 56.
  • a secondary pressure safety device 76 which consists of a pressure limit valve which is connected via check valves 78 to both dosing volumes 54, 56.
  • an end position monitor 80 or a stroke measuring device (not shown) of the piston-rod unit 60 is used, which cooperates with the end position monitor 20 of the media separating device 16 as part of a total control.
  • the feed pump 62 like the main pump 58, is provided with a primary pressure safety device 82, with a tank accumulator 84 in the form of a conventional hydraulic accumulator being connected on the fluid access side for the main pump 58 and the control pump 62. Furthermore, a filter 86 and a cooler 88 are present on the inlet side for the individual pumps 58 , 62 .
  • a hydraulic accumulator 90 is connected to the discharge line 44 to moderate the flow rate by comparison.
  • the conveying device consists essentially of the drive part 18 and the conveying or compressor part 10, with the fluid on the compressor side regularly in the form of a gas to be compressed, of the fluid on the drive side, the dosing volume regularly in the form of a hydraulic medium, by the respective media separating device 16 in the form of the bellows from each other are separated.
  • the modular design for the compressor allows scaling to larger, single-stage compressor units as shown in FIGS. 2, 3 and to multi-stage units as shown in FIGS. 4 and 5 in a simple manner.
  • the conveying device according to FIG. 4
  • the gas supplied via the supply line 42 is in the low-pressure range and is raised to a medium pressure by means of the first compressor in front of the intermediate cooler 92 as the cooling device.
  • the working cylinder 46 of the first compressor stage acts as a pump cylinder or generator for the relevant intermediate pressure.
  • the gas After passing through the intermediate cooler 92, the gas reaches the input or inlet side of the second compressor stage with the two conveying or compressor parts 10 via a medium-pressure line 94.
  • the gas discharge pressure in a high-pressure line 96 is thus raised to high pressure on the output side of the second compressor stage.
  • a low gas pressure of 50 bar can be raised, for example, to a medium pressure of about 160 bar and to a delivery pressure of 500 bar on the high pressure side.
  • compression ratios of 1:3.16 can be expected in both compression stages.
  • a contamination sensor 30 is shown in more detail in FIGS. As already stated, leaks could cause high consequential costs at the separation points between metering volume 54, 56 and the respective gas volume to be conveyed. Accordingly, a contamination sensor 30 is arranged immediately after the metal bellows in the line of the outflowing gas streams on the side of the outlet 14, which monitors the purity of the gas.
  • Such contamination sensors 30 can be constructed according to various principles, whereby in the present case at least two functions should be fulfilled:
  • contamination of the clean surface of a filter fleece 98 causes a significant color change, which is detected by a light sensor system.
  • a light source provided with the reference number 100 sends light beams to the upper side of the filter fleece 98, which in this respect forms a dirt-sensitive surface, and reflected light beams are detected by a light sensor 102.
  • the light beam guidance is also indicated in FIG. 6, as is the direction of flow through the contamination sensor 30, which is represented by arrows.
  • the filter fleece 98 is not pulled out of the sensor housing 103 on the outlet side when it flows through, the latter is supported on a reinforced base layer 104.
  • the contamination sensor 30 according to FIG. 7 works with a similar structure; but now a pressure difference when flowing through the filter fleece 98 is measured by two pressure measuring devices 106 in front of and behind the filter fleece 98 . If a corresponding increase in the flow resistance is detected due to contamination, a signal is emitted.
  • the pressure difference is measured by means of the pressure measuring device 106 with a circuit output and the filter fleece 98 can be a saturable filter mat which, when saturated with oil, generates a higher flow resistance than the pure filter fleece 98 according to Figure 6.
  • the filter fleece 98 which triggered the signal due to contamination, can be replaced so that the respective sensor 30 can continue to be used if necessary.
  • the multi-stage compressors according to the exemplary embodiments according to FIGS. 4 and 5 are used, because the thermodynamics of compression at higher compression ratios require excessive drive power. The gas temperatures then rise to such an extent that special materials have to be used. A multi-stage compressor with intermediate cooling between the compressor stages then requires less drive power, which is extremely favorable in terms of energy.
  • the conveyor is particularly suitable for hydrogen applications; however, other fluids can also be transported and promoted, including those that are completely incompressible and are accordingly not compressed during delivery.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif de transport de fluides pourvu d'une entrée (12) et d'une sortie (14) et d'une partie de transport (10) reliée entre elles et pouvant être actionnée par une partie d'entraînement, se caractérisant en ce que la partie de transport (10) comporte un dispositif de séparation de milieux (16) étanche aux fluides, avec un volume de chambre variable, qui se retrouve en communication de fluide par son espace de réception (21) avec l'entrée (12) ou la sortie (14) et qui, au moyen de la partie d'entraînement, reçoit un fluide par l'intermédiaire de l'entrée (12) dans le cadre d'une course d'admission, augmentant ainsi le volume de la chambre et évacuant le fluide reçu par l'intermédiaire de la sortie (14) dans le cadre d'une course d'évacuation, ce qui réduit la taille dudit volume de chambre.
EP22722755.0A 2021-04-24 2022-04-13 Dispositif de transport Pending EP4285026A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021002178.9A DE102021002178A1 (de) 2021-04-24 2021-04-24 Fördereinrichtung
PCT/EP2022/059908 WO2022223404A1 (fr) 2021-04-24 2022-04-13 Dispositif de transport

Publications (1)

Publication Number Publication Date
EP4285026A1 true EP4285026A1 (fr) 2023-12-06

Family

ID=81603578

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22722755.0A Pending EP4285026A1 (fr) 2021-04-24 2022-04-13 Dispositif de transport

Country Status (5)

Country Link
US (1) US20240200542A1 (fr)
EP (1) EP4285026A1 (fr)
JP (1) JP2024516189A (fr)
DE (1) DE102021002178A1 (fr)
WO (1) WO2022223404A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022115715A1 (de) 2022-06-23 2023-12-28 Pressure Wave Systems Gmbh Kompressorvorrichtung und Kühlvorrichtung mit Kompressorvorrichtung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9518577B2 (en) * 2008-06-27 2016-12-13 Lynntech, Inc. Apparatus for pumping a fluid
DE102011120228A1 (de) 2011-12-03 2013-06-06 Hydac Fluidtechnik Gmbh System zur Verbesserung der Energieeffizienz bei Hydrauliksystemen sowie für ein derartiges System vorgesehener Kolbenspeicher
WO2015078487A1 (fr) 2013-11-26 2015-06-04 Oest Holding Gmbh Pompe de dosage et d'alimentation pour des fluides chimiquement agressifs et/ou abrasifs
EP2913525A1 (fr) 2014-02-26 2015-09-02 Garniman SA Pompe à soufflet à entraînement hydraulique
DE102014217897A1 (de) * 2014-09-08 2016-03-10 Pressure Wave Systems Gmbh Kompressorvorrichtung, eine damit ausgerüstete Kühlvorrichtung und ein Verfahren zum Betreiben der Kompressorvorrichtung und der Kühlvorrichtung
NO20171100A1 (en) 2017-07-04 2019-01-07 Rsm Imagineering As A dual-acting pressure boosting liquid partition device, system, fleet and use
NO20171099A1 (en) * 2017-07-04 2019-01-07 Rsm Imagineering As Pressure transfer device and associated system, fleet and use, for pumping high volumes of fluids with particles at high pressures
US20190282926A1 (en) * 2018-03-15 2019-09-19 Waters Technologies Corporation Systems for compressing low pressure gaseous co2

Also Published As

Publication number Publication date
WO2022223404A1 (fr) 2022-10-27
JP2024516189A (ja) 2024-04-12
US20240200542A1 (en) 2024-06-20
DE102021002178A1 (de) 2022-10-27

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