WO2017016635A1 - Dispositif pour augmenter la pression d'un fluide, se présentant en particulier sous la forme d'une soupape de bouteille de gaz comprimé - Google Patents

Dispositif pour augmenter la pression d'un fluide, se présentant en particulier sous la forme d'une soupape de bouteille de gaz comprimé Download PDF

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Publication number
WO2017016635A1
WO2017016635A1 PCT/EP2016/001149 EP2016001149W WO2017016635A1 WO 2017016635 A1 WO2017016635 A1 WO 2017016635A1 EP 2016001149 W EP2016001149 W EP 2016001149W WO 2017016635 A1 WO2017016635 A1 WO 2017016635A1
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WO
WIPO (PCT)
Prior art keywords
pressure
valve
fluid
compression chamber
hydraulic fluid
Prior art date
Application number
PCT/EP2016/001149
Other languages
German (de)
English (en)
Inventor
Robert Adler
Sascha Dorner
Christoph Nagl
Johannes FRITZER
Original Assignee
Linde Aktiengesellschaft
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 Linde Aktiengesellschaft filed Critical Linde Aktiengesellschaft
Publication of WO2017016635A1 publication Critical patent/WO2017016635A1/fr

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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
    • F04B39/08—Actuation of distribution 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0081—Special features systems, control, safety measures
    • 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
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • F04B45/053—Pumps having fluid drive
    • F04B45/0533—Pumps having fluid drive the fluid being actuated directly by a piston
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0057—Mechanical driving means therefor, e.g. cams
    • F04B7/0061—Mechanical driving means therefor, e.g. cams for a rotating member
    • F04B7/0065—Mechanical driving means therefor, e.g. cams for a rotating member being mounted on the main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F17C13/04—Arrangement or mounting of 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2205/00—Vessel construction, in particular mounting arrangements, attachments or identifications means
    • F17C2205/03—Fluid connections, filters, valves, closure means or other attachments
    • F17C2205/0302—Fittings, valves, filters, or components in connection with the gas storage device
    • F17C2205/0323—Valves
    • F17C2205/0332—Safety valves or pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2205/00—Vessel construction, in particular mounting arrangements, attachments or identifications means
    • F17C2205/03—Fluid connections, filters, valves, closure means or other attachments
    • F17C2205/0302—Fittings, valves, filters, or components in connection with the gas storage device
    • F17C2205/0382—Constructional details of valves, regulators
    • F17C2205/0385—Constructional details of valves, regulators in blocks or units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2221/00—Handled fluid, in particular type of fluid
    • F17C2221/01—Pure fluids
    • F17C2221/012—Hydrogen
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/01—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the phase
    • F17C2223/0107—Single phase
    • F17C2223/0123—Single phase gaseous, e.g. CNG, GNC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level
    • F17C2223/036—Very high pressure (>80 bar)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0128—Propulsion of the fluid with pumps or compressors
    • F17C2227/0157—Compressors
    • F17C2227/0164—Compressors with specified compressor type, e.g. piston or impulsive type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/03—Heat exchange with the fluid
    • F17C2227/0337—Heat exchange with the fluid by cooling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/32—Hydrogen storage

Definitions

  • the invention relates to a device for increasing the pressure of a fluid, in particular in the form of a compressed gas cylinder valve, and a method for increasing the pressure of a fluid by means of a device according to the invention.
  • Prior art compressed gas reservoirs have at least one valve which serves as a shut-off valve or throttling device.
  • valves with a
  • valves are usually screwed in via threads and fixed and sealed with, for example, Teflon.
  • the invention is therefore based on the object to provide a device for increasing the pressure of fluids and a method for increasing the pressure of a fluid with which in a safer, easier and more cost-effective way a removal of Gas from gas storage and in particular an overflow of gas, for example in a second gas storage is possible.
  • a device according to the invention for increasing the pressure of a fluid on a suction channel a compression chamber with a volume and a pressure channel.
  • the compression chamber can be brought into fluid communication with the suction channel, so that via the suction channel fluid in the
  • the compression chamber is sucked. Furthermore, the compression chamber can be brought into flow communication with the pressure channel, so that compressed fluid can be dispensed from the compression chamber via the pressure channel.
  • the device furthermore has a double membrane, which has a first membrane and a second membrane adjacent to the first membrane. The double membrane adjoins the compression chamber and the device is adapted to the
  • Double membrane by means of a hydraulic fluid to deform or move so that the volume of the compression chamber of the device increases in a suction stroke, so that fluid through the suction channel into the compression chamber of the
  • Device is sucked, and that reduces the volume of the compression chamber of the device in a pressure cycle, so that in the compression chamber compressed fluid can be dispensed from the device via the pressure channel.
  • Gas tanks e.g. Hydrogen tanks, by home users (home refueling) dar.
  • the torque required for operating the device for increasing the pressure can be provided via a suitable coupling means, inter alia, by commercially available low-power drills or cordless screwdrivers, so that the device for
  • Pressure increase preferably without an internal motor manages, whereby both the size and the cost of the pressure increase device can be kept low.
  • Another advantage of the invention is the use of a double diaphragm to seal the hydraulic fluid chamber. This effectively counteracts mixing of working fluid and hydraulic fluid, preventing malfunctioning and thus providing greater safety to the user.
  • Pressure relief valve and a safety valve which prevent hazards to the user by increasing pressures in the pressure increase device.
  • Device may also include a heat exchanger for cooling of escaping gas, whereby the user from possible scalds through
  • the fluid to be compressed may be a gas, a gas mixture or a liquid / gas mixture, preferably a gas, more preferably hydrogen gas.
  • the hydraulic fluid is a
  • Hydraulic fluid more preferably an incompressible hydraulic fluid. According to a further advantageous embodiment of the invention is the
  • Double membrane of the device sealed so that mixing of the working fluid to be compressed and the hydraulic fluid is prevented. Furthermore, the double membrane is preferably gas-tight, so that in the
  • Compression chamber located gas can not leave the compression chamber through the double membrane.
  • the device further comprises a hydraulic fluid chamber for receiving the hydraulic fluid and a
  • Displacement piston which is arranged in the hydraulic fluid chamber or projects into this.
  • the displacement piston is designed to press the hydraulic fluid to deform or move the double diaphragm against the double diaphragm.
  • the hydraulic fluid chamber and the displacer have a circular cross-sectional area.
  • the displacer presses the hydraulic fluid in the pressure cycle against the double diaphragm.
  • the displacer is displaceable by the eccentric in a periodic reciprocating motion, so that alternately present a pressure and a suction cycle.
  • the eccentric on a circular cross-sectional area or a cam shape or is formed as a cam, which may have a circumference which deviates from a circular shape
  • the device for increasing the pressure of a fluid for driving or rotating the eccentric on a coupled to the eccentric drive shaft can be fixed to the drive shaft.
  • the drive shaft is preferably adapted to the eccentric by rotation of the drive shaft about its longitudinal or cylindrical axis in the said
  • the drive shaft is adapted to be mechanically connected or preferably coupled to a device for generating a torque.
  • the drive shaft of the device is designed to be coupled or driven with an external, in particular mobile drive, so that the drive shaft rotates as intended, wherein in such a drive, e.g. can be a drill or a cordless screwdriver.
  • a drive e.g. can be a drill or a cordless screwdriver.
  • first fluid container e.g., pressurized gas bottle, see below
  • the device has a
  • Outlet for dispensing compressed fluid or for connecting a second fluid container (or a conduit), so that the pressure channel in
  • the first fluid container is a gas container, preferably a compressed gas container, particularly preferably one
  • the device has a suction valve which is adapted to the flow connection between the
  • the suction valve has a first body, in particular in the form of a ball, and a (first) biasing means, preferably a (first) compression spring, on.
  • first biasing means is so tensioned, that the first body by means of the tensioned first biasing means is stable in a position in which the first body closes the flow connection between the compression chamber and the suction channel.
  • a valve is also referred to as a spring-biased ball valve.
  • the suction valve may in particular also be a flutter valve, in particular of a fiber-reinforced (for example carbon fiber) plastic, in which case the first body also simultaneously forms the (second) biasing means.
  • flutter valves are designed to open without separate drive due to pressure differences on the two valve sides in the forward direction and close automatically again.
  • the flutter valve or the corresponding body in this case has elastic properties that allow the closure of the flutter valve.
  • the device has a pressure valve which is designed to close or interrupt the flow connection between the compression chamber and the pressure channel during the suction cycle and to open during, in particular at the end, the pressure cycle, so that the compressed fluid can be dispensed from the compression chamber or from the device via the pressure channel.
  • this pressure valve has a second body, in particular in the form of a ball, and a (second) biasing means, preferably in the form of a (second) compression spring on. This is the second one
  • the pressure valve can also be a flutter valve (see above).
  • the device has a
  • Heat exchanger which is adapted to cool out of the pressure channel emerging fluid. Accordingly, that heat exchanger is arranged in particular downstream of the pressure channel or on the pressure channel. According to a further advantageous According to the inventors, the said heat exchanger is configured to use ambient air as the coolant. Furthermore, the heat exchanger can use a liquid coolant and can be configured in particular for evaporative cooling.
  • the heat exchanger is designed so that the temperature of the emerging from the pressure channel fluid by at least 50 ° C to 175 ° C, in particular 75 ° C to 175 ° C, in particular 100 ° C to 175 ° C, in particular 125 ° C to 175 ° C, in particular 150 ° C to 175 ° C, in particular by at least 175 ° C is lowered.
  • the device comprises a leakage indicating means, which is adapted to a discharge of
  • the device has a pressure relief valve.
  • the pressure limiting valve has a guided in a cylinder piston, wherein the cylinder opens into the hydraulic fluid chamber of the device.
  • the pressure relief valve further includes a (third) biasing means for biasing the piston against hydraulic fluid in the hydraulic fluid chamber.
  • the third biasing means is adapted to bias the piston against the hydraulic fluid so that the piston moves when exceeding a maximum pressure and thereby limits the pressure of the hydraulic fluid.
  • Hydraulic fluid chamber opens and which by the movement of the piston in Fluid communication is made with the hydraulic fluid chamber and is made free.
  • Pressure limiting valve closed by a closure means relative to the surrounding atmosphere, wherein the closure means projects in particular into the cylinder and is preferably sealed by means of a sealing means.
  • the closure means / sealing means separates the hydraulic fluid in the hydraulic fluid chamber from a rear side of the pressure limiting valve, which is loaded with atmospheric pressure.
  • the third biasing means is supported on the closure means.
  • Biasing means is thus arranged in particular between the piston and the closure means, wherein in particular the piston and the closure means in the direction of the longitudinal or cylindrical axis of the cylinder face each other.
  • the third biasing means increases in tension, the piston moves toward the closure means and the cylinder is progressively released, allowing hydraulic fluid to flow into the cylinder to limit pressure.
  • the cross section of the piston or displacer is meant perpendicular to the direction of movement of the respective piston.
  • the third biasing means is configured as a third compression spring, wherein the third compression spring is adapted to press the piston against located in the hydraulic fluid chamber or in the cylinder hydraulic fluid.
  • the pressure limiting valve is preferably designed such that the displaced by the displacer volume can be compensated by a comparatively small stroke of the piston in the pressure relief valve.
  • the biasing force of the third biasing means is provided only as a restoring force for the pressure relief valve.
  • diameter ratios between the displacer piston and the piston of the pressure limiting valve which are less than or equal to 5 (for example between 5 and 1), in particular less than or equal to 1, in particular less than or equal to 0.5, may be mentioned here.
  • a spring which is particularly long in relation to the spring travel third biasing means
  • ratios between spring length in a prestressed state and spring length in the compressed state in the range of preferably 0.6 to 1, preferably in the range of 0.8 to 1, may be mentioned here.
  • the operating pressure is limited to 300bar.
  • the displacement of the displacer is then e.g. 1, 6ccm.
  • the displacer diameter is here e.g. 20mm.
  • the piston of the pressure relief valve has e.g. a piston diameter of 12mm.
  • a safety device according to the invention in the form of the pressure limiting valve does not cause any mechanical damage to the system in the event of pressure being exceeded. Furthermore, the pressure relief valve in the event of a pressure exceeding advantageously reusable. Furthermore, the simple design of the pressure relief valve allows a particularly favorable solution for ensuring the pressure protection. As a result, this prevents
  • said maximum pressure is 100 bar to 300 bar, in particular 150 bar to 300 bar, in particular 200 bar to 300 bar, in particular 250 bar to 300 bar,
  • the upper pressure limit can also be 350 bar in single-stage operation (a device according to the invention).
  • the stroke volume of the displacement piston of the pressure increase device is 1 cubic centimeter to 20 cubic centimeters, in particular 1.6
  • Cross section of the displacer of the pressure increase device 10 millimeters to 50 millimeters, in particular 20 millimeters.
  • Pressure increase 10 mm to 80 mm, in particular 12 mm.
  • the device has a safety valve and in particular a valve cam. That's it
  • Safety valve can be brought into an open position in which a flow connection between the compression chamber of the device and the pressure channel of the
  • Compression chamber of the device and the pressure channel of the device is interrupted by the safety valve, so that no fluid passes through the safety valve in the pressure channel.
  • the drive shaft of the device is preferably coupled to the valve cam, for example mechanically connected, such that the valve cam moves the safety valve periodically during the rotation of the drive shaft, in particular during the pressure stroke into the open position.
  • the valve cam and the eccentric of the device are designed to perform a common rotation.
  • the valve cam has a circular cross-sectional area.
  • the valve cam is as
  • Cam formed e.g. ground in the form of a cam.
  • the cam may have a circumference that deviates from a circular shape.
  • valve cam is integrally, that is, integrally formed with the eccentric, wherein preferably the eccentric and the valve cam are fixed via a fastening means on the drive shaft or are integrally formed therewith or integrally therewith.
  • valve cam and the eccentric are formed separately, wherein the valve cam and the eccentric can be connected to each other and / or separately via a connecting means with the drive shaft or each integrally formed thereon.
  • the safety valve is biased by a (fourth) biasing means, preferably in the form of a (fourth) compression spring against the valve cam, ie in the direction of the closed position, so that the safety valve moves by spring force in the closed position, unless it is moved by the action of the valve cam against the spring force in the open position.
  • a biasing means preferably in the form of a (fourth) compression spring against the valve cam, ie in the direction of the closed position, so that the safety valve moves by spring force in the closed position, unless it is moved by the action of the valve cam against the spring force in the open position.
  • the safety valve has a valve piston, with a first end portion which is slidably disposed in a valve cylinder.
  • the valve cylinder preferably extends through the pressure channel and opens into a
  • Valve chamber through which the compression chamber is in fluid communication with the pressure channel when the safety valve is in its open position (in particular during the pressure stroke).
  • the valve piston is further preferably configured with one with the
  • Drive shaft connected valve cam cooperate, which is preferably adapted to press upon rotation of the drive shaft against the first end portion of the valve piston and thereby to move the valve piston in a first position corresponding to the open position of the safety valve.
  • the valve piston furthermore preferably has a second end section, which projects into the valve chamber in this first position, so that compressed fluid can pass the second end section via the valve cylinder and into the pressure channel.
  • the valve piston is further preferably biased by means of the fourth biasing means, which is preferably formed as a fourth compression spring, which is arranged in particular in the valve chamber and presses against the second end portion of the valve piston in the direction of a second position corresponding to the closed position of the safety valve , Due to this bias, the valve piston moves due to the valve cam shape in the suction cycle from its first position back to its second position in which the second end portion interrupts a flow connection between the valve chamber and the valve cylinder (and thus also with the pressure channel).
  • the fourth biasing means which is preferably formed as a fourth compression spring, which is arranged in particular in the valve chamber and presses against the second end portion of the valve piston in the direction of a second position corresponding to the closed position of the safety valve , Due to this bias, the valve piston moves due to the valve cam shape in the suction cycle from its first position back to its second position in which the second end portion interrupts a flow connection between the valve chamber and the valve cylinder (and thus also with the pressure channel).
  • the second end portion of the valve piston is cone-shaped and configured to engage in a form-fitting manner in the second position of the valve piston in a corresponding conical portion of the valve cylinder, so that that flow connection between the valve chamber and the valve cylinder or pressure channel is interrupted.
  • the control times by adapting the cam grinding or cam shape are readily adaptable. Therefore Complex functions such as those determined from measurements can be easily realized.
  • a gas flow is only possible if, according to the cam or the cam shape is also provided that the
  • Safety valve is open. In the event of damage to the device for increasing the pressure of a fluid, the safety valve moves to its safe rest position
  • the safety valve according to the invention represents a particularly favorable solution for isolating the device from downstream elements.
  • Bottle valve configured to open and close a flow connection between the inlet and the suction channel.
  • Carrying out device as part of a compressed gas cylinder valve wherein the housing of the pressure increase device and the cylinder valve form a unit.
  • the outlet channel of the bottle valve which is separated from the gas storage or the compressed gas cylinder by the cylinder valve, is connected to the suction channel in such a configuration.
  • the inlet of the device is configured to be brought into flow communication with the compressed gas cylinder, so that gas from the compressed gas cylinder via the inlet and the cylinder valve can be dispensed into the suction channel, and so in particular the device or the housing of the device together with cylinder valve is carried by the compressed gas cylinder and is portable.
  • the device has a fitting associated with said cylinder valve for closing and opening the
  • Compressed gas cylinder valve for connecting a container or a pipe
  • the housing of the device or of the compressed gas cylinder valve preferably has a maximum diameter of 150 mm and a maximum height of 150 mm.
  • Hydrogen gas from a compressed gas cylinder with an inlet pressure of 50 bar to an outlet pressure of 300 bar (single stage, in particular at most 350 bar), e.g. upon refueling the compressed gas storage of a hydrogen bicycle or vehicle using hydrogen as fuel (e.g., fuel cell).
  • a filling amount of the compression chamber is, for example, 29 g of hydrogen gas.
  • an energy of 87.76 kJ must be supplied.
  • a typical compressed gas storage of 1, 1 1 volume can be refueled in less than 5 minutes.
  • a heat exchanger thus preferably carries out a heat of about 75 kJ assuming an atmospheric pressure of 300 bar. Therefore, the heat exchanger is typically on a medium
  • Another aspect of the present invention relates to a method for
  • Device or an inventive compressed gas cylinder valve
  • a fluid preferably a gas, in particular of gaseous hydrogen
  • a device according to the invention for pressure increase the fluid through the
  • the fluid in the compression chamber is compressed and discharged through the pressure channel.
  • a gas particularly preferably gaseous hydrogen
  • a fluid, preferably gas, particularly preferably gaseous hydrogen from a
  • the device / compressed gas cylinder valve or the method according to the invention can advantageously be used for refueling a motor vehicle with a fluid, preferably with a gas, more preferably with hydrogen.
  • FIG. 1 shows a sectional view of a device according to the invention for increasing the pressure
  • FIG. 2 shows a sectional view of a compressed gas cylinder valve according to the invention
  • FIG. 3 shows a sectional view of a pressure-limiting valve according to the invention.
  • FIG. 1 shows a device 1 for pressure increase, with a compression chamber 3, a suction channel 4, which via an inlet 14 with a first fluid container (not shown) in fluid communication, and with a pressure channel 5, via an outlet 15 with a second fluid container (not shown) in FIG.
  • Flow connection can be brought.
  • a fluid or gas can pass from the first fluid container via the suction channel 4 into the device 1, be compressed there and output via the pressure channel 5 into a second fluid container.
  • the suction channel 4 and the pressure channel 5 each open into the compression chamber 3. In this case, a flow connection between the suction channel 4 and the
  • Compressor 3 interrupted by a suction valve 12 which is configured to open when a maximum pressure difference between the suction channel 4 and the compression chamber 3 is exceeded, so that to be compressed fluid during a Saugtakts on the suction channel 4 and the (open) suction valve 12 in the
  • Compression chamber 3 passes. During this, a pressure valve 13 is closed and interrupts a flow connection between the compression chamber 3 and the pressure channel 5.
  • the pressure valve 13 is configured to open when a maximum pressure difference between the compression chamber 3 and the pressure channel 5 is exceeded, during a pressure cycle following the suction cycle (the suction valve 12 is closed during the pressure cycle).
  • the two valves 12, 13 are each a spring-biased ball valve.
  • the two valves 12,13 each have a ball 12a, 13a, which are each biased by a spring means or biasing means 23 (not visible at ball 12 in Fig. 1) against the position at which the respective
  • the device 1 For compressing the fluid, the device 1 comprises a hydraulic fluid chamber 8 filled with a hydraulic fluid or a hydraulic fluid, e.g. in the form of a cylindrical recess which adjoins the compression chamber 3.
  • a cylindrical displacer 9 is slidably disposed so that the displacer 9 is a cross section of
  • Hydraulic fluid chamber 3 which extends transversely to a direction of movement of the displacer piston 9, fills and in the direction of movement in the hydraulic fluid chamber 8 back and forth is movable.
  • the hydraulic fluid chamber 8 is completed or limited here on a first side by an end face of the displacement piston 9.
  • the compression chamber 3 adjoins the
  • Hydraulic fluid chamber 8 wherein between the compression chamber 3 and the hydraulic fluid chamber 8, a double diaphragm 6.7, comprising a first diaphragm 6 and a voltage applied to the first diaphragm 6 second diaphragm 7, is arranged.
  • the double diaphragm 6, 7 thus separates the hydraulic fluid chamber 8 from the
  • Compression chamber 3 from and seals the hydraulic fluid chamber 8 on the second side against leakage of hydraulic fluid.
  • the double membrane 6, 7 extends along an extension plane parallel to the said cross-section of the chamber 8 and the end face of the displacement piston 9 extends. The direction of movement of the piston 9 thus extends perpendicular to
  • Double diaphragm 6, 7 moves away, wherein a negative pressure arises, according to which the double diaphragm 6, 7 is moved in the direction of the hydraulic fluid chamber 8, so that the compression chamber 3 increases its volume and sucks in fluid through the suction channel 4 and the correspondingly open suction valve 12.
  • the diameter of the particular circular double diaphragm 6,7 is greater than the inner diameter of said cross section of the hydraulic fluid chamber 8, so that the opening of the hydraulic fluid chamber 8 on the second side through the
  • Double membrane 6,7 is closable.
  • the double membrane 6, 7 with a peripheral edge region on a front side of the chamber 8, which bounds that opening, sealingly.
  • the double membrane 6, 7 is depicted in a position which corresponds to the end of the printing cycle of the device 1.
  • the double diaphragm 6,7 is curved in the position shown in the direction of the compression chamber 3.
  • a leak indicating means 16 for indicating leakage of hydraulic fluid from the hydraulic fluid chamber 8 is shown.
  • the leakage indicating means 6 is arranged on a side of the double diaphragm 6, 7 facing away from the hydraulic fluid chamber 8 and is in fluid communication with that end face of the chamber 8 at an outer edge of the double diaphragm 6, 7, so that hydraulic fluid which passes by the double diaphragm 6, 7 is detectable by means of the leakage indicator means 16.
  • the leakage-indicating means 16 can have a receptacle for receiving the leakage fluid, which can then be visually detected in the receptacle.
  • the device 1 further comprises a drive shaft 1 1, which extends along a longitudinal or cylindrical axis, in particular parallel to the plane of extension of the double membrane 6, 7 and in particular perpendicular to Movement direction of the displacer 9.
  • the drive shaft 1 1 is on a side facing away from the double diaphragm 6, 7 side of the displacer 9th
  • the drive shaft 1 1 has in particular a circular
  • a coupling means 27 e.g. in the form of a recess which is designed and provided for coupling the drive shaft 1 1 with a (in particular external) device for generating a torque.
  • Torque generating agent may be e.g. positively and / or non-positively engage in said recess (for example, cordless screwdriver, etc.).
  • the eccentric 10 is in particular provided on the drive shaft 1 1, that he moves in the pressure cycle of the device 1 when rotating the drive shaft 1 1 about the longitudinal axis of the drive shaft 1 1 to the displacer 9 and this against the hydraulic fluid in the chamber. 8 presses, so that the double membrane 6, 7 the previously sucked in the suction cycle in the compression chamber 3 compressed fluid in the pressure cycle and outputs via the pressure channel 5 with the pressure valve 13 open.
  • the displacer 9 may further comprise a recess 28 at a contact surface to the eccentric 10 to that contact surface between the eccentric 10 and the displacer 9 to reduce the friction
  • the device 1 for pressure increase or compression can furthermore according to FIG. 1 have a safety valve 19, which is configured to
  • the safety valve 9 has for this purpose a valve piston 31, with a first end portion 32 which is slidably disposed in a valve cylinder 32 a and in particular by means of two on
  • valve cylinder 32a extends with a portion through the pressure channel 5, wherein that portion has a smaller inner diameter than that portion of the valve cylinder 32a, which receives the first end portion 32 of the valve piston 31, and opens into a valve chamber 33, via which the compression chamber.
  • 3 in Fluid communication with the pressure channel 5 is when the safety valve 19 is in its open position (in particular during the pressure cycle).
  • valve piston 31 cooperates with a connected to the drive shaft 1 1 valve cam 20 which is adapted to press upon rotation of the drive shaft 1 1 against the first end portion 32 of the valve piston 31 and thereby to move the valve piston 31 in a first position, the the open position of the safety valve 19 corresponds. In this first position of the valve piston 31, a second protrudes
  • valve piston 31 is further biased by means of a (fourth) biasing means 29, preferably in the form of a (fourth) compression spring 29, which is arranged in the valve chamber 33 and presses against the second end portion 30 of the valve piston 31, toward a second position, the the closed position of the safety valve 19 corresponds. Due to this bias, the valve piston 31 moves due to the valve cam shape in the suction cycle from its first position back to its second position in which the second end portion 30 interrupts a flow connection between the valve chamber 33 and the valve cylinder 32a (and thus also with the pressure channel 5).
  • the second end portion 30 of the valve piston is preferably formed cone-shaped and engages in the second position of the valve piston 31 positively in a corresponding conical portion 32c of the valve cylinder 32a, so that those flow connection between the valve chamber 33 and the valve cylinder 32a and pressure channel 5 is interrupted ,
  • the valve cam 20 may in particular be formed integrally with the eccentric 10. In the figure 1, the valve cam 20 is in a maximum raised position with respect to the valve piston 31, ie, this has been advanced by the valve cam 20 straight into its first position, against the bias of the fourth compression spring 29, so that the flow connection between the compression chamber 3 and the pressure channel 5 is opened.
  • the printing device according to the invention according to FIG. 1 has a
  • Heat exchanger 17 for example, downstream of the pressure channel 5 and the pressure channel 5 and upstream of the outlet 15 is arranged.
  • the heat exchanger 17 serves to cool the compressed fluid discharged via the pressure channel 5.
  • the device 1 for pressure increase according to Figures 1 and 3, a pressure relief valve 18 with a piston 22, a cylinder 21, and a (third) biasing means 35, preferably in the form of a compression spring 35 on.
  • the piston 22 of the pressure relief valve 18 is slidably disposed in the cylinder 21 and is supported via the third biasing means 35 at a
  • Closing means 26 a which closes the cylinder 21 outwardly at a first end of the cylinder 21, wherein further the cylinder 21 at a
  • a sealing means 26 is preferably provided, which rotates on the closure means 26a and seals the cylinder 21 against the environment of the device 1.
  • the piston 22 is moved on reaching a maximum pressure in the hydraulic fluid chamber against the spring force of the third biasing means 35 in the cylinder 21 from the chamber 8, whereby the volume of the chamber 8 effectively increases and
  • FIG. 2 shows an embodiment of a further aspect of the invention, in which a device 1 according to the invention is designed as a compressed gas cylinder valve or is integrated in such a device, ie a housing 24 of the device 1 is provided which is provided with a cylinder valve 25a for shutting off the Suction channel 4 forms a unit.
  • a device 1 according to the invention is designed as a compressed gas cylinder valve or is integrated in such a device, ie a housing 24 of the device 1 is provided which is provided with a cylinder valve 25a for shutting off the Suction channel 4 forms a unit.
  • this embodiment of the device 1 according to FIG. 2 furthermore has an inlet 25, which is configured to connect a compressed gas cylinder, so that the device 1 is carried, in particular, by the compressed gas cylinder 2, and an outlet 34, which is provided on the housing 24 Connecting a container to be filled (eg gas tank) or a corresponding line is formed.
  • the inlet 25 is connected to the suction channel 4 of the compressed gas cylinder valve 2 in FIG.
  • Fluid connection can be brought, via the valve 25 a, which is eg manually operable (eg via a corresponding valve). With the cylinder valve 25a open, fluid from a compressed gas cylinder connected to the compressed gas cylinder valve 1 can be sucked through the inlet 25 and the suction channel 4 into the device 1 or the compressed gas cylinder valve 1, can be compressed by the device 1 and through the pressure channel 5 and outlet 34 at elevated pressure dispensable.
  • the valve 25 a which is eg manually operable (eg via a corresponding valve).
  • a coupling means 27 is further provided, which is connected to the drive shaft 1 1 of the device 1, and is accessible for example via a recess of the housing 24. Via the coupling means 27, for example, in the manner described above, a torque can be transmitted to the drive shaft 11, which drives the compressed gas cylinder valve 1 for the compression of the fluid.

Landscapes

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

Abstract

La présente invention concerne un dispositif (1) servant à augmenter la pression d'un fluide, se présentant notamment sous la forme d'une soupape de bouteille de gaz (1), ainsi qu'un procédé pour augmenter la pression d'un fluide. Ce dispositif (1) comprend une chambre à fluide hydraulique (8) dans laquelle est disposé un piston de refoulement (9). Le refoulement du fluide hydraulique par le piston de refoulement (9) provoque l'actionnement d'une double membrane (6,7) dans une chambre de compression (3), ce qui a pour effet de transporter un fluide à comprimer d'un canal d'aspiration (4) à un canal de refoulement (5) et de comprimer ledit fluide. Le piston de refoulement (9) est entraîné par un excentrique (10) par l'intermédiaire d'un arbre d'entraînement (11). Ce dispositif (1) présente également une soupape de limitation de pression (18) disposée dans la zone de la chambre à fluide hydraulique (8). Ledit dispositif présente en outre une soupape de sécurité (19) pouvant être régulée par une came de soupape (20). L'arbre d'entraînement dispose de moyens d'accouplement (27) destinés par exemple à être accouplés à une perceuse. Ce dispositif trouve des applications de préférence dans la purge de bouteilles de gaz comprimé à usage domestique.
PCT/EP2016/001149 2015-07-30 2016-07-05 Dispositif pour augmenter la pression d'un fluide, se présentant en particulier sous la forme d'une soupape de bouteille de gaz comprimé WO2017016635A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015009850.0 2015-07-30
DE102015009850.0A DE102015009850A1 (de) 2015-07-30 2015-07-30 Vorrichtung zur Druckerhöhung eines Fluids, insbesondere in Form eines Druckgasflaschenventils

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Publication Number Publication Date
WO2017016635A1 true WO2017016635A1 (fr) 2017-02-02

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PCT/EP2016/001149 WO2017016635A1 (fr) 2015-07-30 2016-07-05 Dispositif pour augmenter la pression d'un fluide, se présentant en particulier sous la forme d'une soupape de bouteille de gaz comprimé

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DE (1) DE102015009850A1 (fr)
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Publication number Priority date Publication date Assignee Title
TWI778877B (zh) * 2021-11-25 2022-09-21 吳尚樺 用於泡沫式消防滅火系統的流體輸送增壓裝置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0148691A2 (fr) * 1984-01-11 1985-07-17 DOSAPRO MILTON ROY, SociÀ©té dite: Perfectionnement aux pompes à membrane à débit variable
EP0460386A1 (fr) * 1990-06-08 1991-12-11 LEWA Herbert Ott GmbH + Co. Membrane pour une pompe À  membrane entraînée hydrauliquement
DE4122538A1 (de) * 1991-07-08 1993-01-14 Friedhelm Schneider Membranpumpe mit hydraulischer betaetigung
DE4327969A1 (de) * 1993-08-19 1995-03-02 Ott Kg Lewa Hydraulisch angetriebene Membranpumpe

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8437701U1 (de) * 1984-12-21 1986-01-09 Lewa Herbert Ott Gmbh + Co, 7250 Leonberg Membranpumpe
DE202012100995U1 (de) * 2012-03-20 2013-07-01 Pressure Wave Systems Gmbh Kompressorvorrichtung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0148691A2 (fr) * 1984-01-11 1985-07-17 DOSAPRO MILTON ROY, SociÀ©té dite: Perfectionnement aux pompes à membrane à débit variable
EP0460386A1 (fr) * 1990-06-08 1991-12-11 LEWA Herbert Ott GmbH + Co. Membrane pour une pompe À  membrane entraînée hydrauliquement
DE4122538A1 (de) * 1991-07-08 1993-01-14 Friedhelm Schneider Membranpumpe mit hydraulischer betaetigung
DE4327969A1 (de) * 1993-08-19 1995-03-02 Ott Kg Lewa Hydraulisch angetriebene Membranpumpe

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DE102015009850A1 (de) 2017-02-02

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