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
  • 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
  • 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
  • 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
  • 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

Definitions

• the invention relates to a device for increasing the pressure of a fluid with a safety valve.
• Compressed gas storage liquid gas storage and metal hydride storage.
• Prior art compressed gas storage devices have at least one valve which serves as a shut-off valve or throttling device.
• valves may be equipped with a safety device, rupture discs are mostly used.
• the valves are usually screwed in via threads and fixed and sealed with, for example, Teflon.
• a compressor is used in the removal from gas storage, which is not part of the gas storage. It must therefore be available as a connection between compressed gas cylinder and compressor corresponding high-pressure lines.
• prior art devices for the compression of gases e.g. Reciprocating compressor and rotary compressor known.
• Reciprocating compressor and rotary compressor known.
• the use of external gas compressors due to the high cost, space requirements and the
• High-pressure compressors for private users such as those required for home-refueling applications, must be distinguished above all by a high degree of safety.
• Automatically operated pressure valves of the prior art work with
• the invention is therefore based on the object to provide a device for increasing the pressure of fluids with an improved safety valve.
• the invention provides that the device has a safety valve, which can be brought into an open position in which the flow connection between the compression chamber and the pressure channel is open and compressed fluid passes the safety valve over from the compression chamber into the pressure channel, and in a closed position in which the
• Fluid communication through the safety valve is interrupted, so that no fluid passes through the safety valve in the pressure channel, wherein the device further comprises a valve connected to the drive shaft valve cam, which is adapted to move the safety valve in the open position upon rotation of the drive shaft.
• valve cam is preferably formed when rotating the
• the problem according to the invention is thus achieved in particular by a safety valve which can be controlled via a coupling to a rotating drive shaft of the device by means of a valve cam depending on the position of the drive shaft or the valve cam.
• the safety valve may e.g. the
• the type of control is adaptable by adapting the geometric shape of the valve cam for a variety of functions and desired timing.
• a safety valve according to the invention represents a particularly favorable solution for isolating a device for increasing the pressure.
• a pressure relief valve which reduces hazards to the user by increasing pressures in the hydraulic fluid chamber of the pressure increasing device.
• the device according to the invention can also have a
• the fluid comprises a gas, a gas mixture or a liquid / gas mixture, preferably a gas, more preferably hydrogen gas.
• the safety valve by a (first) biasing means against the valve cam in Direction is biased to the closed position, so that in particular 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 or held there.
• the safety valve has a valve piston, with a first end portion which is slidably disposed in a valve cylinder of the device.
• the valve cylinder extends through the pressure channel and into a
• Valve chamber opens, via which the compression chamber can be brought into fluid communication with the pressure channel when the safety valve is in its open position (in particular during the pressure cycle).
• valve cam is 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.
• valve piston has a second end portion, which projects into the valve chamber in this first position, so that compressed fluid can pass the second end portion over the valve cylinder into the pressure channel.
• valve piston is biased in the direction of a second position by means of the (in particular arranged in the valve chamber and in particular as a first compression spring) first biasing means which presses against the second end portion of the valve piston, which corresponds to the closed position of the safety valve.
• 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 the 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 device has a suction channel, wherein the compression chamber with the suction channel in
• Fluid connection can be brought, so that via the suction fluid in the
• the device preferably has a double membrane, comprising a first membrane and a second membrane adjacent to the first membrane.
• the double membrane preferably adjoins the compression chamber and the device is preferably designed to deform the double membrane by means of a hydraulic fluid so that the volume of the compression chamber of the device increases in a suction stroke, so that fluid via 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 located fluid is compressible and can be output via the pressure channel from the device.
• the hydraulic fluid is a hydraulic fluid, particularly preferably an incompressible
• 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
• the device has a hydraulic fluid chamber for receiving the hydraulic fluid, a displacer, an eccentric, and connected to the eccentric drive shaft, which is preferably designed to enable the eccentric by rotation of the drive shaft in rotation.
• the displacer is preferably in the
• Hydraulic fluid chamber arranged slidably and adapted to push the hydraulic fluid to deform the double membrane against the double membrane.
• the eccentric is designed to press against the displacer during rotation, so that the displacer presses the hydraulic fluid against the double diaphragm.
• the hydraulic fluid chamber and the displacer piston may have a circular cross-sectional area.
• the respective cross-section extends in each case perpendicular to the direction of movement of the displacer.
• the eccentric in its simplest embodiment, a circular cross-sectional area or alternatively a cam shape or is formed as a cam, which may have a circumference which deviates from a circular shape.
• the eccentric with the drive shaft in one piece, that is, integrally, executed or connected thereto via another connecting means.
• valve cam and the eccentric of the device are designed to perform a common rotation.
• valve cam has a circular cross-sectional area.
• valve cam as
• valve cam can be ground as a cam.
• the cam may have a circumference that deviates from a circular shape.
• valve cam is in one piece, 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 integrally formed therewith or integrally therewith.
• valve cam and the eccentric are formed separately, wherein the valve cam and the eccentric with each other and / or separately via a connecting means may be connected to the drive shaft or integrally formed thereon.
• the coupling of the state of the safety valve to the suction cycle or pressure cycle of the device results from the shape of the valve cam and the shape of the eccentric, each of which is in particular firmly connected to the drive shaft.
• the drive shaft is adapted to, with a device for generating a torque
• the drive shaft of the device is adapted to be releasably coupled with a drill or a cordless screwdriver, so that the drive shaft of the drill or the cordless screwdriver is set in rotary motion.
• the drive shaft can have a corresponding recess into which that device for generating a torque (for example a drill or a cordless screwdriver) can engage positively and / or non-positively.
• the device has a first fluid container (e.g., pressurized gas bottle, see below) such that the suction passage is connectable to the first fluid container.
• a first fluid container e.g., pressurized gas bottle, see below
• 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 (second) biasing means, preferably a (second) compression spring, on.
• the second biasing means is tensioned so that the first body by means of the tensioned second 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 (third) biasing means, preferably in the form of a (third) compression spring on.
• the third biasing means is so tensioned, that the second body by means of the tensioned third biasing means is stable in a position in which the second body closes the flow connection between the compression chamber and the pressure channel.
• the pressure valve can also be a flutter valve (see above).
• the device has a heat exchanger, which is designed 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 embodiment of the inventors said heat exchanger is configured to use ambient air as a coolant. Furthermore, the
• Heat exchanger use a liquid coolant and can be configured in particular for evaporative cooling.
• Heat exchanger preferably designed so that the temperature of the out of the
• Pressure channel escaping 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 can be lowered by at least 175 ° C.
• 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 in the hydraulic fluid chamber the device opens.
• the pressure relief valve further comprises (fourth) biasing means for biasing the piston against hydraulic fluid in the hydraulic fluid chamber.
• the fourth biasing means is adapted to bias the piston against the hydraulic fluid such that the piston is defined when exceeding a bias by the piston
• Pressure limiting valve closed by a closure means relative to the surrounding atmosphere, wherein the closure means projects in particular into the cylinder, and wherein the closure means is preferably sealed by means of a sealing means.
• the fourth 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. With increasing tension or deflection of the fourth biasing means, the piston moves in the direction of the closure means, so that the pressure in the hydraulic fluid is limited.
• said piston has a circular cross-sectional area.
• the cross section in question extends perpendicular to the direction of movement of the piston.
• the ratio between the diameter of the cross section of the displacer and the diameter of the cross section of the piston of the pressure relief valve is less than or equal to 5, in particular less than or equal to 1, in particular less than or equal to 0.5.
• the fourth biasing means is configured as a fourth compression spring, wherein the fourth compression spring is adapted to the piston against befindlichem in the hydraulic fluid chamber or in the cylinder
• 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 fourth 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 fourth 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 eg 1, 6ccm.
• the displacer diameter is here eg 20mm.
• the piston of the pressure relief valve has, for example, a piston diameter of 12mm.
• 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).
• a device comprising several devices according to the invention (for example two), e.g. are connected in series.
• the possibility exists e.g. from 50 bar to 300 bar and then from 300 bar to 750 bar.
• the stroke volume of the displacer of the pressure increase device is 1 cubic centimeter to 20 cubic centimeters, in particular 1.6 cubic centimeters.
• the diameter of the cross section of the displacer of the pressure increase device is 10 millimeters to 50 millimeters, in particular 20 millimeters. According to a further advantageous embodiment, the diameter of the cross section of the piston of the pressure limiting valve of the device for
• Pressure increase 10 mm to 80 mm, in particular 12 mm.
• the inlet of the device is adapted to a
• 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 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
• a fluid preferably a gas, in particular gaseous hydrogen
• the fluid is sucked through the suction channel into the compression chamber in a suction cycle.
• the fluid in the compression chamber is compressed and discharged through the pressure channel.
• a fluid, more preferably a gas, particularly preferably gaseous hydrogen are transferred from a first gas reservoir with a first pressure into a second gas reservoir with a second pressure, wherein the second pressure may be greater than the first pressure
• 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.
• 1 shows a sectional view of a device according to the invention for pressure increase with a safety valve
• 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) is in fluid communication, and with a pressure channel 5, which via an outlet 15 with a second fluid container (not shown) in
• 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 device 1 for pressure increase or compression has according to the invention a safety valve 19, which is configured to interrupt the flow connection between the compression chamber 3 and the pressure channel 5 and to close the pressure channel 5.
• the safety valve 19 has for this purpose a valve piston 31, with a first end portion 32 which is slidably disposed in a valve cylinder 32a and in particular sealed by means of two circumferential to the end portion 32 seals 32b, so that the compressed fluid does not over the
• Valve cylinder 32a can escape.
• the valve cylinder 32a extends with a portion through the pressure passage 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 one
• Valve chamber 33 via which the compression chamber 3 is in flow communication with the pressure channel 5 when the safety valve 19 is in its open position (in particular during the pressure cycle).
• the valve piston 31 cooperates with a connected to a 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.
• the drive shaft 1 1 serves to drive the device 1, such that it can compress the fluid in the compression chamber 3, which will be described in detail below.
• valve piston 31 In the first position of the valve piston 31, a second end section 30 of the valve piston 31 protrudes into the valve chamber 33, so that compressed fluid can pass the second end section 30 past the valve cylinder 32a into the pressure channel 5.
• the valve piston 31 is further arranged by means of a (first) biasing means 29, preferably in the form of a (first) compression spring 29, which is arranged in the valve chamber 33 is pressed against the second end portion of the valve piston 31, biased toward a second position, the closed position of the
• Valve piston 31 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 a
• valve piston Fluid communication between the valve chamber 33 and the valve cylinder 32a (and thus also with the pressure channel 5) interrupts.
• 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 ,
• valve cam 20 may be integrally formed with an eccentric 10 used to compress the fluid and also connected to the drive shaft 11 so as to rotate together with the drive shaft 11.
• 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 first compression spring 29, so that the flow connection between the compression chamber 3 and the pressure channel 5 is opened.
• the suction channel 4 and the pressure channel 5 each open into the compression chamber 3 a. In this case, a flow connection between the suction channel 4 and the
• Compression chamber 3 further characterized by a suction valve 12 which is configured to open when exceeding a maximum pressure difference between the suction channel 4 and compression chamber 3, so that to be compressed fluid during a Saugtakts on the suction port 4 and the (open) suction valve 12 in the compression chamber 3 passes.
• a pressure valve 13 which is provided in particular upstream of the safety valve 19, closed and interrupts a flow connection between the compression chamber 3 and the pressure channel fifth
• 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 which follows the suction cycle (During the pressure stroke, the suction valve 12 is closed).
• the two valves 12, 13 are each a spring-biased ball valve.
• the two valves 12, 13 may each also be flutter valves (see also above).
• 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 piston 9 is slidably disposed, so that the displacer 9 is a cross section of the hydraulic fluid chamber 8.
• Hydrauiikfluidhunt 3 which extends transversely to a direction of movement of the displacer 9, fills and in the direction of movement in the Hydrauiikfluidhunt 8 back and forth is movable.
• the hydraulic fluid chamber 8 is in this case closed or bounded on a first side by an end face of the displacement piston 9. On a second side opposite the first side, the compression chamber 3 adjoins the
• Hydrauiikfluidhunt 8 wherein between the compression chamber 3 and the Hydrauiikfluidhunt 8 a double membrane 6.7, comprising a first diaphragm 6 and a voltage applied to the first diaphragm 6 second diaphragm 7, is arranged.
• the double membrane 6, 7 thus separates the Hydrauiikfluidhunt 8 of the
• Compression chamber 3 seals the Hydrauiikfluidhunt 8 on the second side against leakage of hydraulic fluid.
• the double diaphragm 6, 7 extends along an extension plane which runs parallel to the said cross section of the chamber 8 or the end face of the displacement piston 9. The direction of movement of the piston 9 thus extends perpendicular to
• 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 16 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 is applied to the
• Double membrane 6, 7 is detectable.
• the leakage-indicating means 16 can have a receptacle for receiving the leakage fluid, which can then be visually detected in the receptacle. As already indicated, is shown in FIG. 1 for driving the device 1 the
• Drive shaft 1 1 is provided, which extends along a longitudinal or cylindrical axis, in particular parallel to the plane of extension of the double diaphragm 6, 7 and in particular perpendicular to the direction of movement of the displacer 9.
• the drive shaft 1 1 is on a side remote from the double diaphragm 6, 7 side the displacement piston 9 is provided and is connected for driving the displacement piston 9 with said eccentric 10.
• the drive shaft 1 1 has in particular a circular cross section and has at a free end (on an outside of the device 1) via a coupling means 27, e.g. in form of a
• the said torque generating means may, for example, positively and / or non-positively engage in said recess (eg, electric 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 store lubricant and thus the friction of that contact surface between the eccentric 10 and the
• the printing device according to the invention according to FIG. 1 has a
• Heat exchanger 17 the e.g. is disposed downstream of the pressure channel 5 and upstream of the outlet 15.
• the heat exchanger 17 is used for cooling the output from the pressure channel 5, compressed fluid.
• the pressure increasing device 1 of FIGS. 1 and 3 may further include a pressure relief valve 18 having a piston 22, a cylinder 21, and a (fourth) biasing means 35, preferably in the form of a (fourth) compression spring 35.
• the piston 22 of the pressure limiting valve 18 is slidably mounted in the cylinder 21 and is supported via the biasing means 35 on a closure means 26 a, which closes the cylinder 21 outwardly at a first end of the cylinder 21, wherein further the cylinder 21 at a opposite second end opens into the hydraulic fluid chamber 8 of the device 1.
• 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 away from the chamber 8 upon reaching a maximum pressure in the hydraulic fluid chamber 8 against the spring force of the (fourth) biasing means 35 in the cylinder 21, whereby the volume of the chamber 8 is effectively increased and limited according to the prevailing pressure on the said maximum pressure becomes.
• 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 integrated into it, ie, a housing 24 of the device 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 integrated into it, ie, a housing 24 of the device 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 2, 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 for 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 communication via the valve 25 a, the e.g. manually operable (e.g., via a corresponding fitting).
• Compressed gas cylinder valve 1 connected compressed gas cylinder 2 through the inlet 25 and the suction channel 4 in the device 1 and the compressed gas cylinder valve 1 sucked, by means of the device 1 compressible and can be output by the pressure channel 5 and outlet 34 at elevated pressure.
• a coupling means 27 is further provided, which with the
• Drive shaft 1 1 of the device 1 is connected, and is accessible via a recess of the housing 24, for example. 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.

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

Applications Claiming Priority (2)

Publications (1)

Family

ID=56413613

Family Applications (1)

Country Status (3)

Citations (4)

• 2015
  • 2015-07-30 DE DE102015009846.2A patent/DE102015009846A1/de not_active Withdrawn
• 2016
  • 2016-07-12 WO PCT/EP2016/001198 patent/WO2017016643A1/de active Application Filing
  • 2016-07-29 TW TW105124228A patent/TW201712260A/zh unknown

Patent Citations (4)

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