TW201712226A - Device for increasing the pressure of a fluid, having a pressure-limiting valve - Google Patents

Abstract

The invention relates to a device and method for increasing the pressure of a fluid, having a pressure-limiting valve.

Description

Device for increasing fluid pressure with pressure limiting valve

The present invention relates to a device for increasing fluid pressure with a pressure limiting valve and a method for increasing fluid pressure by the device of the present invention.

Compressed gas reservoirs, liquefied gas reservoirs and metal hydride storage are among the most widely used hydrogen storage systems.

The compressed gas reservoir according to the prior art has at least one valve that acts as a shut-off valve or a throttling device. These valves can be further equipped with safety devices, most of which use a rupture disk. Of these, the valves are mostly screwed in and fastened and sealed, for example with Teflon.

When the gas is extracted from a pure gas phase compressed gas cylinder, the pressure of the remaining gas in the bottle is necessarily lowered. Therefore, there is always a pressure differential when transferring to other gas reservoirs.

The prior art uses a compressor to increase the pressure when extracting gas from the gas reservoir, which is not part of the gas reservoir. Therefore, a corresponding high pressure line must be provided to establish a connection between the compressed gas cylinder and the compressor. Devices for compressing gases, such as piston compressors and rotary compressors, are known from the prior art.

For private user fuel filling operations, the use of external gas compressors is disadvantageous due to high cost, space and safety risks.

High-pressure compressors required for private users to fill fuel at home must first provide a high level of safety. For example, a user poses a safety risk due to a fault that causes excessive pressure on the hydraulic fluid of the high pressure compressor.

The increased pressure of the hydraulic fluid can be prevented by the pressure limiting valve provided by the prior art, such as a hydraulic pressure limiting valve or a rupture disk.

When the valve seat is exposed to air cavitation due to cavitation and wear, and the overpressure occurs, the hydraulic pressure limiting valve will be damaged.

The rupture discs for maximum pressure protection can only be used once, as these rupture discs are mechanically damaged after overpressure.

In view of the above, it is an object of the present invention to provide an apparatus for increasing pressure and a corresponding method that at least partially alleviates the above problems. In particular, excessive pressure on the hydraulic fluid should be prevented to protect the user of the device.

The solution of the invention for achieving this object is a device having the features of claim 1. Advantageous technical solutions of the present invention are given by the subsidiary items, which will be described below.

According to claim 1, the invention proposes that the pressure limiting valve has a piston guided in the cylinder, wherein the cylinder opens into the hydraulic fluid chamber, and wherein the device has a first pretensioning member, the pretensioning member being used for Pre-tightening the piston in the direction of hydraulic fluid located in the hydraulic fluid chamber, and wherein the first pretensioning member is configured to pre-tension the piston toward the hydraulic fluid such that the piston is in the hydraulic fluid chamber Exercise to limit this pressure when a clear maximum pressure is exceeded.

In particular, the present invention specifically proposes that when the maximum pressure is exceeded, a portion of the hydraulic fluid flows from the hydraulic fluid chamber into the hydraulic fluid chamber of the cylinder and through the movement of the piston to establish a flow connection or a smooth passage with the hydraulic fluid chamber or Section.

By using the pressure limiting valve of the present invention, the system is not subject to mechanical damage when the hydraulic fluid is overpressured.

The simple construction of the pressure limiting valve provides a very low cost pressure protection solution.

Compared with the hydraulic pressure limiting valve and the rupture disk provided by the prior art, the pressure limiting valve of the present invention has the advantages of durability and reusability, respectively.

The various embodiments of the present invention employ a safety valve as an additional safety device that is configured to interrupt the flow connection between the compression chamber and the pressure passage through the intervention of a valve cam coupled to the drive shaft during the suction cycle. This prevents the user from being damaged by the high pressure gas that is discharged.

Further, the apparatus may include a heat exchanger for cooling the exhaust gas to prevent the user from being burnt by the discharged high temperature gas.

The apparatus for increasing pressure of the present invention is suitable for use in various gases and liquids. For example, by adjusting the drive power, the materials used, the volume, and the size of the heat exchanger, it is possible to adapt to a particular fluid.

According to a advantageous embodiment, the fluid is a gas, a gas mixture or a liquid-gas mixture, preferably a gas, particularly preferably hydrogen.

According to another advantageous embodiment, the hydraulic fluid is a hydraulic fluid, preferably an incompressible hydraulic fluid.

According to an advantageous embodiment of the invention, the cylinder of the pressure limiting valve is closed by a closure relative to the surrounding environment. The closure can extend into the cylinder.

Additionally, the pressure limiting valve may be sealed by a seal wherein the seal/seal separates the hydraulic fluid located in the hydraulic fluid chamber from the back side of the pressure limiting valve that is affected by atmospheric pressure. The seal can for example be looped onto the closure.

According to another advantageous embodiment of the invention, the first pretensioning member abuts against the closure. That is, the first pretensioning member is specifically disposed between the piston and the closure member, wherein the piston and the closure member are disposed opposite each other along a longitudinal axis or a cylinder axis of the cylinder. As the tension or compression of the first pretensioning member increases, the piston moves toward the closure and the degree of opening of the cylinder increases, so that hydraulic fluid can flow into the cylinder to achieve a pressure limit.

According to a further advantageous embodiment of the invention, the device has a displacement piston which is arranged in the hydraulic fluid chamber, wherein the displacement piston is configured to displace the hydraulic fluid.

The displacement piston preferably has a circular cross section or a cylindrical shape. Wherein the cross section extends perpendicular to the direction of movement of the displacement piston.

According to another advantageous embodiment of the present invention, the pressure limiting valve is configured such that the volume of the hydraulic fluid displaced by the displacement piston of the device when the hydraulic pressure exceeds the maximum pressure only causes the piston of the pressure limiting valve to move, wherein That is, the first pretensioning member is compressed or tensioned. That is, when the maximum pressure of the hydraulic fluid is exceeded, the double diaphragm does not deform or move beyond its normal position, and the maximum allowable pressure is not exceeded in the compression chamber and the hydraulic fluid chamber. At the same time, this prevents the double diaphragm from being overloaded.

According to a further advantageous embodiment of the invention, the piston has a circular cross section or a cylindrical shape. Wherein the cross section extends perpendicular to the direction of movement of the piston.

According to another advantageous embodiment of the present invention, the first pretensioning member is configured as a first pressure spring, wherein the first pressure spring is specifically configured to press the piston against the hydraulic fluid chamber and/or the cylinder Hydraulic fluid in (see above).

The pressure limiting valve is preferably designed such that the smaller stroke of the piston in the pressure limiting valve compensates for the volume displaced by the displacement piston. In this way, the first pretensioning element (for example a spring, in particular a pressure spring) can be designed in a particularly precise manner in the pressure limiting valve, since the length change causes the (third) pretensioning element to be used in the case of a small stroke movement. There is a small deviation in the preload. Here, the ratio of the diameter between the displacement piston and the piston of the pressure limiting valve is set as a special value, the diameter ratio is less than or equal to 5 (for example, between 5 and 1), specifically less than or equal to 1, specifically less than Equal to 0.5.

Alternatively or additionally, the same effect can be obtained by selecting a spring (third pretensioning member) which is particularly long in spring stroke. Here, it is proposed for the third pretensioning member that the ratio of the length of the spring in the pretensioned state to the length of the spring in the compressed state is preferably in the range of 0.6 to 1, preferably in the range of 0.8 to 1.

In special application examples, the working pressure is limited to 300 bar. In this case, the stroke volume of the displacement piston is, for example, 1.6 ccm. The displacement piston diameter is here for example 20 Mm. The piston of the pressure limiting valve has, for example, a piston diameter of 12 mm.

According to a further advantageous embodiment of the device for increasing the pressure, the maximum pressure is from 100 bar to 300 bar, in particular from 150 bar to 300 bar, in particular from 200 bar to 300 bar, in particular from 250 bar to 300 bar, in particular It is 300 bar. In single-stage operation (device of the invention), the upper pressure limit can also be 350 bar.

According to another embodiment of the invention, an apparatus is proposed having several (e.g. two) devices of the invention, such as tandem. This can for example be compressed from 50 bar to 300 bar and then compressed from 300 bar to 750 bar.

According to another advantageous technical solution, the stroke volume of the displacement piston of the device for increasing the pressure is 1 cubic centimeter to 20 cubic centimeters, specifically 1.6 cubic centimeters.

According to another advantageous embodiment, the displacement piston of the device for increasing the pressure has a cross-sectional diameter of 10 mm to 50 mm, in particular 20 mm.

According to another advantageous embodiment, the piston of the pressure limiting valve of the device for increasing the pressure has a cross-sectional diameter of 10 mm to 80 mm, in particular 12 mm.

According to another advantageous embodiment of the present invention, the device includes a suction passage, a compression chamber having a volume, and a pressure passage, wherein the compression chamber can establish a flow connection with the suction passage, so that the fluid can be sucked into the compression through the suction passage. a cavity, wherein the compression chamber can establish a flow connection with the pressure channel, such that fluid can be output to the compression chamber through the pressure channel. Furthermore, the device preferably has a double diaphragm having a first diaphragm and a second diaphragm abutting the first diaphragm. Wherein the double diaphragm preferably abuts the compression chamber, and the displacement piston is preferably configured to press the hydraulic fluid against the double diaphragm to deform the double diaphragm such that the volume of the compression chamber of the device is The suction cycle becomes larger so that fluid can be drawn into the compression chamber of the device through the suction passage, and the volume of the compression chamber of the device becomes smaller during the compression cycle, so that the fluid located in the compression chamber can be compressed and transmitted. The pressure channel outputs the device.

According to another advantageous embodiment of the present invention, the double diaphragm of the device is sealed such that The working fluid to be compressed cannot be mixed with the hydraulic fluid. In addition, the dual diaphragm is preferably hermetically designed such that gas located in the compression chamber cannot pass through the dual diaphragm and exit the compression chamber.

According to another advantageous embodiment of the invention, the device has an eccentric which is configured to be pressed against the displacement piston such that the displacement piston presses the hydraulic fluid against the double diaphragm.

Further preferably, the apparatus has a drive shaft coupled to the eccentric for rotating the eccentric, the drive shaft being configured to rotate the eccentric by rotation of the drive shaft.

In its simplest embodiment, the eccentric has a circular cross section or alternatively a cam shape or is embodied as a cam disk, which can have a non-circular circumference.

According to another advantageous embodiment of the present invention, the eccentric is integrally formed with the drive shaft, that is, integrally formed, or connected to the drive shaft through other connecting members.

According to another advantageous embodiment of the invention, the drive shaft is configured to be mechanically coupled to a means for generating torque or, preferably, to a means for generating torque.

The drive shaft of the device is preferably configured to be coupled to or otherwise drivable by a particularly movable external drive such that the drive shaft rotates normally, wherein the drive can be, for example, a drill or a rechargeable screwdriver.

According to another preferred embodiment of the present invention, the device has an inlet for introducing a fluid into the suction passage or for connecting a first fluid container (for example, a compressed gas cylinder, see below), so that the suction passage can be coupled with the first The fluid container establishes a flow connection.

According to another advantageous embodiment of the present invention, the device has an outlet for outputting the compressed fluid or for connecting the second fluid container (or pipeline) such that the pressure passage can establish a connection with the second fluid container or the pipeline Stream connection.

According to another advantageous embodiment, the first fluid container is a gas container, preferably a compressed gas container, particularly preferably a compressed gas cylinder.

According to another advantageous embodiment, the device has a suction valve configured to close or interrupt the flow connection between the compression chamber and the suction passage during a compression cycle and to keep the flow connection unobstructed during the suction cycle .

According to another advantageous embodiment, the suction valve has a first body, which is in the form of a ball, and a (second) pretensioning element, which is preferably a (second) pressure spring. Wherein the second pretensioning member can be tensioned such that the first body can be held in a position by the tensioned second pretensioning member, wherein the first body closes the position A through-flow connection between the compression chamber and the suction passage. This type of valve is also known as a spring preloaded ball valve.

In particular, the suction valve can also be a reed valve, in particular a fiber-reinforced (for example carbon fiber) plastic, which also forms a (second) pretension at the same time. Such a reed valve is configured to open and automatically close again based on the pressure difference between the two valve sides without a separate drive. Wherein, the reed valve or the corresponding body has elasticity capable of closing the reed valve.

According to a further advantageous embodiment of the invention, the device has a pressure valve which is configured to close or interrupt the flow connection between the compression chamber and the pressure channel during the suction cycle and during compression, in particular during compression The flow connection is opened at the end of the cycle so that the compressed fluid can be output to the compression chamber or the device through the pressure channel.

According to a preferred embodiment of the present invention, the pressure valve has a second body, the body of which is specifically a sphere, and a (third) pretensioning member. The pretensioning member is preferably a (third) Pressure spring. Wherein the third pretensioning member can be tensioned such that the second body can be held in a position by the tensioned third pretensioning member, in which position the second body closes the A through-flow connection between the compression chamber and the pressure passage.

According to an embodiment of the invention, the pressure valve can of course also be a reed valve (see above).

According to another advantageous embodiment of the invention, the device has a safety valve and a valve cam. Wherein the safety valve can enter an open position in which the device is compressed a flow connection between the chamber and the pressure passage of the device is opened (the pressure valve is open), and the compressed fluid enters the pressure passage from the compression chamber via the safety valve, and can enter a closed position in which the closed position The flow connection between the compression chamber of the device and the pressure passage of the device is interrupted by the safety valve such that no fluid enters the pressure passage via the safety valve. Wherein the drive shaft of the device is preferably coupled to the valve cam such as a mechanical connection such that the valve cam moves the safety valve to the open position periodically, in particular during the compression cycle, as the drive shaft rotates .

According to another advantageous embodiment of the invention, the valve cam and the eccentric of the device are configured to be rotatable together.

According to a further advantageous embodiment of the invention, the valve cam has a circular cross section. The valve cam is preferably formed as a cam disc, for example in the form of a cam disc. The cam disc may in particular have a non-circular perimeter.

According to another advantageous embodiment, the valve cam is integrally formed with the eccentric (ie, integrally), wherein the eccentric and the valve cam are preferably fixed to the drive shaft by a fixing member or integrally or integrally formed with the drive shaft. .

According to another alternative embodiment of the present invention, the valve cam is formed separately from the eccentric, wherein the valve cam and the eccentric are connectable to each other and/or can be separately connected to the drive shaft through a connecting member or can be integrally formed On the drive shaft.

According to a further advantageous embodiment, the safety valve is pretensioned in the direction of the valve cam, preferably in the direction of the closed position, by the (fourth) pretensioning element of the (fourth) pressure spring, so that When the safety valve is moved to the open position against the elastic force under the action of the valve cam, the safety valve is moved to the closed position by the elastic force. Thus in this embodiment the safety valve closes during the suction cycle and opens during the compression cycle. Thereby a seal is formed between the pressure channel and the compression chamber. This seal prevents fluid flow, for example, in the event of damage.

The relationship between the state of the safety valve and the suction and compression cycles of the device depends on The shape of the valve cam and the shape of the eccentric wheel are specifically fixedly coupled to the drive shaft.

The safety valve preferably has a valve piston including a first end that is slidably disposed in the valve cylinder. The valve cylinder preferably extends through the pressure passage and opens into a valve chamber through which the compression chamber is in flow communication with the pressure passage when the safety valve (specifically during the compression cycle) is in its open position.

Additionally, the valve piston is preferably configured to cooperate with a valve cam that is coupled to the drive shaft, the valve cam preferably being configured to press against the first end of the valve piston and to cause the valve piston therebetween when the drive shaft rotates Move to the first position, which corresponds to the open position of the safety valve.

Additionally, the valve piston preferably has a second end that extends into the valve chamber in the first position such that compressed fluid can enter the pressure passage from the second end side through the valve cylinder.

The valve piston is further preferably pre-tensioned in the direction of the second position by the fourth pretensioning member, the position corresponding to the closed position of the safety valve, and the fourth pretensioning member is preferably constructed as a fourth pressure spring, the pressure spring Specifically, it is disposed in the valve chamber and is pressed against the second end of the valve piston. The pretensioning causes the valve piston to return from its first position to its second position during the suction cycle based on the shape of the valve cam, in which the second end interrupts the flow connection between the valve chamber and the valve cylinder (and In turn, the flow connection between the valve chamber and the pressure passage is also interrupted.

To this end, the second end of the valve piston is preferably tapered and configured to be insertably fitted into a correspondingly tapered section of one of the valve cylinders in a second position of the valve piston, thereby interrupting the valve chamber and Flow connection between valve cylinder or pressure channel.

The safety valve of the present invention can directly adjust the control time by changing the cam grinding or cam shape. Thus, for example, the complex functions obtained in the measurement are also easy to implement. The air flow can be formed only when the safety valve is opened correspondingly according to the cam grinding or the cam shape. When the device for increasing fluid pressure is damaged, the safety valve moves to its safe, inoperative position (the closed position of the safety valve). Due to the low friction loss, only low power is required Drive the safety valve. The safety valve of the present invention is an extremely low cost solution for isolating the device from downstream components as compared to an electrically or pneumatically isolated valve.

According to a particularly advantageous embodiment of the invention, the inlet of the device is configured to be connectable to a compressed gas cylinder, wherein the device further has a cylinder valve, the cylinder valve being configured to open and close the inlet and the suction passage The flow connection between the two.

In other words, the technical solution of the present invention proposes to implement the device as an integral part of a compressed gas cylinder valve, wherein the housing of the device for increasing pressure forms a unit with the cylinder valve. The discharge passage of the cylinder valve is separated from the gas reservoir or the compressed gas cylinder by the cylinder valve. In the present embodiment, the discharge passage is connected to the suction passage.

The inlet of the device is preferably configured to establish a flow connection with the compressed gas cylinder so that gas can be output from the compressed gas cylinder to the suction passage through the inlet and the cylinder valve, and the device or the housing of the device is combined with the gas The bottle valves are either carried together or can be carried by a compressed gas cylinder.

According to an advantageous embodiment, the device has a fitting attached to the cylinder valve for closing and opening a through-flow connection between the inlet and the suction passage.

Additionally, the device or the outlet of the compressed gas cylinder valve is preferably configured to connect to a vessel or line for receiving the fluid.

According to another advantageous embodiment, the housing of the device or the compressed gas cylinder valve preferably has a maximum diameter of 150 mm and a maximum height of 150 mm.

For example, when filling a fuel for a hydrogen powered bicycle or a hydrogen powered vehicle's compressed gas storage device using hydrogen as a fuel (for example, a fuel cell), the input pressure from the compressed gas cylinder can be made by the apparatus of the present invention. 50 bar of hydrogen reaches an output pressure of 300 bar (up to 350 bar for a single stage). The filling amount of the compression chamber is, for example, 29 g of hydrogen. When based on the adiabatic compression process, an energy of 87.76 kJ must be provided. Thereby, a typical compressed gas reservoir having a volume of 1.1 liters can be filled in less than 5 minutes with a typical drive power of the drive shaft of 250 W.

Among them, if it is assumed to be an isentropic process, the input temperature reaches 20 ° C and reaches 215 ° C. Out of temperature. Thus, if the atmospheric pressure is assumed to be 300 bar, the heat exchanger preferably discharges about 75 kJ of heat. Therefore, the heat exchanger typically employs about 238 W of equal power.

Another aspect of the invention is directed to a method of increasing fluid pressure which preferably utilizes the apparatus of the present invention (or the compressed gas cylinder valve of the present invention).

When the method of the present invention for increasing the pressure of a fluid, preferably a gas, in particular a gaseous hydrogen, is carried out using the apparatus for increasing pressure of the present invention, the fluid is drawn into the compression through the suction passage during an inhalation cycle. Cavity. The fluid located in the compression chamber is compressed during the next compression cycle and the fluid is output through the pressure passage. Preferably, the method transfers a fluid, further preferably a gas, particularly a gaseous hydrogen, from a first gas reservoir having a first pressure to a second gas reservoir having a second pressure, wherein the second pressure is Greater than the first pressure. Alternatively, the fluid may be extracted from a gas reservoir, preferably a gas, particularly preferably gaseous hydrogen.

Accordingly, the apparatus/compressed gas cylinder valve of the present invention or the method of the present invention can be advantageously used to fill a car with a fluid, preferably a gas, particularly preferably hydrogen.

1‧‧‧Devices for increasing pressure or compressed cylinder valves

2‧‧‧Compressed gas cylinders

3‧‧‧Compression chamber

4‧‧‧Inhalation channel

5‧‧‧pressure channel

6‧‧‧First diaphragm

7‧‧‧Second diaphragm

8‧‧‧Hydraulic fluid chamber

9‧‧‧Squeezing the piston

10‧‧‧Eccentric wheel

11‧‧‧Drive shaft

12‧‧‧Inhalation valve

12a‧‧‧First body or sphere

13‧‧‧pressure valve

13a‧‧‧Second body or sphere

14‧‧‧ Entrance

15‧‧‧Export

16‧‧‧Leakage indicator

17‧‧‧ heat exchanger

18‧‧‧Limited pressure valve

19‧‧‧Safety valve

20‧‧‧Valve Cam

21‧‧‧ cylinder

22‧‧‧Piston

23‧‧‧Second preloader

24‧‧‧Shell

25‧‧‧ entrance

25a‧‧‧ gas cylinder valve

26‧‧‧Seal

26a‧‧‧Closed

27‧‧‧Couplings

28‧‧‧ dent

29‧‧‧4th preloading piece

30‧‧‧second end

31‧‧‧ valve piston

32‧‧‧First end

32a‧‧‧Valve cylinder

32b‧‧‧Seal

32c‧‧‧Cone section

33‧‧‧Valve room

34‧‧‧Export

35‧‧‧First pretension

Further features and advantages of the invention will be set forth in the description of the embodiments. 1 is a cross-sectional view of a device for increasing pressure of a pressure limiting valve of the present invention; FIG. 2 is a cross-sectional view of a valve for a compressed gas cylinder of the present invention; and FIG. 3 is a cross-sectional view of the pressure limiting valve of the present invention.

Figure 1 shows a device 1 for increasing the pressure, the device having a compression chamber 3, a suction passage 4 permeable to the first fluid container (not shown) through the inlet 14 and a permeable opening 15 and a second fluid A container (not shown) establishes a pressure channel 5 for the flow connection. Correspondingly, fluid or gas from the first fluid container can enter the device 1 through the suction channel 4 where it is compressed and output by the pressure channel 5 to the second fluid container.

In order to compress or inhale the fluid, the device 1 has a hydraulic fluid chamber 8 filled with a hydraulic fluid or a hydraulic fluid, for example in the form of a cylindrical gap adjoining the compression chamber 3. The cylindrical displacement piston 9 is slidably disposed in the hydraulic fluid chamber 8, whereby the displacement piston 9 fills a cross section of the hydraulic fluid chamber 8 extending transversely to the direction of movement of the displacement piston 9 and can be along the hydraulic fluid chamber 8 The direction of motion reciprocates.

Therein, the hydraulic fluid chamber 8 is closed or restricted on the first side by the end face of the displacement piston 9. On the second side opposite the first side, the compression chamber 3 abuts the hydraulic fluid chamber 8, wherein between the compression chamber 3 and the hydraulic fluid chamber 8, a double diaphragm 6, 7 is provided, the double diaphragm comprising the first The diaphragm 6 and the second diaphragm 7 of the first diaphragm 6 are attached.

The double diaphragms 6, 7 thereby separate the hydraulic fluid chamber 8 from the compression chamber 3 and seal the hydraulic fluid chamber 8 on the second side against hydraulic fluid flow. As shown in Fig. 1, the double diaphragms 6, 7 extend along an extension plane which is parallel to the above-mentioned cross section of the chamber 8 or the end face of the displacement piston 9. Therefore, the direction of movement of the piston 9 is perpendicular to the plane of extension of the double diaphragms 6, 7. When the displacement piston 9 is moved in the direction of movement of the opposing double diaphragms 6, 7, the double diaphragms 6, 7 are applied with hydraulic fluid and deflected towards the compression chamber 3, which is the compression cycle. During the suction cycle, the displacement piston 9 moves in a direction away from the movement of the double diaphragms 6, 7, during which a negative pressure is generated, and the double diaphragms 6, 7 are correspondingly moved in the direction of the hydraulic fluid chamber 8, so that the volume of the compression chamber 3 becomes larger. And the compression chamber draws in fluid through the suction passage 4 and the correspondingly opened suction valve 12.

According to the present invention, as shown in FIGS. 1 and 3, the apparatus 1 for increasing the pressure further has a pressure limiting valve 18 including a piston 22, a cylinder 21 and a (first) pretensioning member 35 in the form of Good pressure spring 35.

The piston 22 of the pressure limiting valve 18 is slidably disposed in the cylinder 21 and abuts against the closing member 26a through the pretensioning member 35. The closing member closes the cylinder 21 outwardly on the first end of the cylinder 21, wherein the cylinder 21 The hydraulic fluid chamber 8 of the device 1 is further introduced at the opposite second end.

In addition, a sealing member 26 is preferably provided, the sealing member is annularly disposed on the closing member 26a and opposite The cylinder 21 is sealed in the surrounding environment of the device 1.

When the maximum pressure is reached in the hydraulic fluid chamber, the piston 22 moves away from the chamber 8 in the cylinder 21 against the spring force of the first pretensioning member 35, thereby effectively increasing the volume of the chamber 8 and correspondingly present in the chamber. The pressure is limited to the above maximum pressure.

The suction passage 4 and the pressure passage 5 open into the compression chamber 3, respectively. Wherein, the flow connection between the suction passage 4 and the compression chamber 3 can be interrupted by the suction valve 12, which is configured to open when the maximum pressure difference is exceeded between the suction passage 4 and the compression chamber 3 to allow the fluid to be compressed The compression chamber 3 is introduced through the suction passage 4 and the (open) suction valve 12 during the suction cycle. In the meantime, the pressure valve 13 closes and interrupts the flow connection between the compression chamber 3 and the pressure passage 5.

Therein, the pressure valve 13 is configured to be openable when a maximum pressure difference is exceeded between the compression chamber 3 and the pressure passage 5, that is, during a compression cycle after the suction cycle (the suction valve 12 is closed during the compression cycle). The two valves 12, 13 are preferably spring preloaded ball valves, respectively. The two valves 12, 13 can also be reed valves (see also above). The two valves 12, 13 each have a ball 12a, 13a, respectively, which are respectively actuated by the spring element or the pretensioning element 23 (the pretensioning element is not visible at the ball 12 in Fig. 1). The direction in which the connection is interrupted is pre-tensioned.

In particular, the diameter of the circular double diaphragms 6, 7 is larger than the inner diameter of the aforementioned cross section of the hydraulic fluid chamber 8, so that the opening of the hydraulic fluid chamber 8 on the second side can be closed by the double diaphragms 6, 7. In this case, the double diaphragms 6 , 7 are sealed in a circumferential edge region against the end face of the chamber 8 which delimits the opening.

The double diaphragms 6, 7 shown in Figure 1 are in a position corresponding to the end of the compression cycle of the device 1. Therefore, the double diaphragms 6, 7 are bent toward the compression chamber 3 at the positions shown.

Furthermore, FIG. 1 shows a leak indicator 16 for indicating the flow of hydraulic fluid in the hydraulic fluid chamber 8. The leakage indicator 16 is disposed on the side of the double diaphragm 6, 7 facing away from the hydraulic fluid chamber 8 and is in flow connection with the end surface of the chamber 8 on the outer edge of the double diaphragm 6, 7 so that the leakage indicator 16 can detect The hydraulic fluid passing by the double diaphragms 6, 7 was measured. To this end, the leak indicator 16 can have a receiving member for accommodating the leaking fluid, and can be visually detected in the receiving member. To leak fluid.

According to FIG. 1 , the device 1 further has a drive shaft 11 which extends along a longitudinal axis or a cylindrical axis, in particular parallel to the plane of extension of the double diaphragms 6 , 7 , that is to say in particular perpendicular to the displacement piston 9 . The direction of motion extends. The drive shaft 11 is disposed on a side of the displacement piston 9 facing away from the double diaphragms 6, 7 and connects the eccentric 10 to drive the displacement piston 9. The drive shaft 11 has a circular cross section in particular and has a coupling 27 on the free end (on the outside of the device 1), for example in the form of a slot, which is configured and arranged for the drive shaft 11 to A (external) torque generating device is coupled. The torque generating member can be inserted into the slot (for example, a chargeable screwdriver or the like), for example, in a form fit and/or a press fit.

The eccentric 10 is in particular arranged on the drive shaft 11 such that the eccentric moves towards the displacement piston 9 during the compression cycle of the device 1 as the drive shaft 11 rotates about the longitudinal axis of the drive shaft 11 and will The hydraulic fluid displaced into the chamber 8 is displaced by the piston so that the double diaphragms 6, 7 compress the fluid that was previously drawn into the compression chamber 3 during the suction cycle during the compression cycle and through the pressure passage 5 with the pressure valve 13 open. The fluid is discharged.

According to FIG. 1, the displacement piston 9 can further have a recess 28 on the contact surface with respect to the eccentric 10 for feeding the lubricating medium and thereby reducing the friction of the contact surface between the eccentric 10 and the displacement piston 9.

According to FIG. 1, the device 1 for increasing the pressure or for compression can further have a safety valve 19 which is configured to interrupt the flow connection between the compression chamber 3 and the pressure channel 5 or to close the pressure channel 5. For this purpose, the safety valve 19 has a valve piston 31 comprising a first end 32 which is slidably arranged in the valve cylinder 32a and, in particular, is sealed by two seals 32b provided on the end 32. This prevents the compressed fluid from escaping through the valve cylinder 32a. A section of the valve cylinder 32a extends through the pressure passage 5, wherein the inner diameter of the section is smaller than the section of the valve cylinder 32a for receiving the first end 32 of the valve piston 31, and the section opens into the valve chamber 33. When the safety valve 19 (specifically during the compression cycle) is in its open position, the compression chamber 3 is in flow communication with the pressure channel 5 through the valve chamber.

The valve piston 31 cooperates with a valve cam 20 that is coupled to the drive shaft 11 that is configured to be pressed against the first end 32 of the valve piston 31 and to move the valve piston 31 therebetween during rotation of the drive shaft 11 Position, which corresponds to the open position of the safety valve 19. When the valve piston 31 is in this first position, the second end 30 of the valve piston 31 extends into the valve chamber 33 so that compressed fluid enters the pressure passage 5 from the side of the second end 30 via the valve cylinder 32a. The valve piston 31 is further pre-tensioned in the second position by the action of the (fourth) pretensioning member 29, which corresponds to the closed position of the safety valve 19, which is preferably in the form of a (fourth) pressure. A spring 29 is provided in the valve chamber 33 and is pressed against the second end 30 of the valve piston 31. This pretensioning causes the valve piston 31 to return from its first position to its second position during the suction cycle based on the valve cam shape, in which the second end 30 interrupts the passage between the valve chamber 33 and the valve cylinder 32a. The flow connection (and thus also the flow connection of the valve chamber to the pressure channel 5). To this end, the second end of the valve piston is preferably tapered and is inserted into a correspondingly conical section 32c of the valve cylinder 32a in a form-fit manner in the second position of the valve piston 31, thereby interrupting the valve chamber 33 and A through-flow connection between the valve cylinder 32a or the pressure passage 5.

The valve cam 20 can be integrally formed with the eccentric 10 in particular. In Fig. 1, the valve cam 20 is in a maximum extended position relative to the valve piston 31, that is, the valve piston is forwarded to its first by the valve cam 20 against the preload of the fourth pressure spring 29. The position is such that a through-flow connection between the compression chamber 3 and the pressure channel 5 is opened.

According to FIG. 1, the pressure device according to the invention further has a heat exchanger 17, which is arranged downstream of the pressure channel 5 and upstream of the outlet 15, for example. The heat exchanger is used to cool the compressed fluid that is output to the pressure channel 5.

2 shows an embodiment of the invention in which the device 1 of the invention is constructed as a compressed gas cylinder valve or integrated in a compressed gas cylinder valve, that is to say that the device 1 has a housing 24 which is used The cylinder valve 25a, which closes the suction passage 4, collectively forms a unit.

In particular, the embodiment of the device 1 as shown in Fig. 2 further has an inlet 25 which is configured to be connectable to a compressed gas cylinder, so that the device 1 is specifically compressed by the gas cylinder 2 Carrying, and an outlet 34 provided on the housing 24, the outlet being configured to connect a container to be filled (e.g., a gas cylinder) or a corresponding line. The inlet 25 can be in flow connection with the suction passage 4 of the compressed gas cylinder valve 1, in particular through the valve 25a, which can be manually manipulated, for example by means of a corresponding fitting.

Thereby, when the cylinder valve 25a is opened, the fluid can be self-contained from the compressed cylinder suction device 1 or the compressed cylinder valve 1 connected to the compressed cylinder valve 1 through the inlet 25 and the suction passage 4, and the device 1 compresses the The fluid is output through the pressure passage 5 and the outlet 34 while the pressure has been increased.

Further coupled to the housing 24 is a coupling member 27 that connects the drive shaft 11 of the device 1 and is accessible, for example, through a notch in the housing 24. Torque can be transmitted to the drive shaft 11 via the coupling member 27, for example in the manner previously described, which drives the compressed cylinder valve 1 to compress the fluid.

1‧‧‧Devices for increasing pressure or compressed cylinder valves

3‧‧‧Compression chamber

4‧‧‧Inhalation channel

5‧‧‧pressure channel

6‧‧‧First diaphragm

7‧‧‧Second diaphragm

8‧‧‧Hydraulic fluid chamber

9‧‧‧Squeezing the piston

10‧‧‧Eccentric wheel

11‧‧‧Drive shaft

12‧‧‧Inhalation valve

12a‧‧‧First body or sphere

13‧‧‧pressure valve

13a‧‧‧Second body or sphere

14‧‧‧ Entrance

15‧‧‧Export

16‧‧‧Leakage indicator

17‧‧‧ heat exchanger

18‧‧‧Limited pressure valve

19‧‧‧Safety valve

20‧‧‧Valve Cam

23‧‧‧Second preloader

24‧‧‧Shell

27‧‧‧Couplings

28‧‧‧ dent

29‧‧‧4th preloading piece

30‧‧‧second end

31‧‧‧ valve piston

32‧‧‧First end

32a‧‧‧Valve cylinder

32b‧‧‧Seal

33‧‧‧Valve room

Claims (14)

A device for increasing fluid pressure, comprising: a hydraulic fluid chamber (8) for accommodating hydraulic fluid, and a pressure limiting valve (18) for restricting pressure in the hydraulic fluid chamber (8), wherein The pressure limiting valve (18) has a piston (22) guided in a cylinder (21), wherein the cylinder (21) opens into the hydraulic fluid chamber (8), and wherein the device (1) has a first pre- a tightening member (35) for pretensioning the piston (22) in the direction of hydraulic fluid located in the hydraulic fluid chamber (8), and wherein the first pretensioning member (35) is configured to be The piston (22) is pre-tensioned in the direction of the hydraulic fluid such that the piston (22) moves during the hydraulic fluid chamber (8) beyond a defined maximum pressure to limit the pressure. A device according to claim 1, characterized in that the cylinder (21) of the pressure limiting valve (18) is closed by a closure (26a) relative to the surrounding environment. A device according to claim 2, characterized in that the first pretensioning member (35) abuts against the closure member (26a). A device according to any one of claims 1 to 3, characterized in that the device (1) has a displacement piston (9) for compressing the fluid, the displacement piston being arranged in the hydraulic fluid chamber (8), wherein the displacement The piston (9) is configured to displace the hydraulic fluid, and wherein the displacement piston (9) in particular has a circular cross section. The apparatus of claim 4, wherein the pressure limiting valve (18) is configured such that the volume of the hydraulic fluid displaced by the displacement piston (9) of the apparatus (1) when the hydraulic pressure exceeds the maximum pressure is only made The piston (22) of the pressure limiting valve (18) moves. A device according to any of the preceding claims, characterized in that the piston (22) has a circular cross section. A device according to any one of the preceding claims, characterized in that the ratio of the cross-sectional diameter of the displacement piston (9) to the piston (22) of the pressure limiting valve (18) is less than or equal to 5, in particular less than or equal to 1, Specifically, it is less than or equal to 0.5. A device according to any of the preceding claims, characterized in that the first pretensioning member (35) is constructed as a first pressure spring, wherein the first pressure spring (35) is configured to be capable of the piston (22) Pressing hydraulic fluid in the hydraulic fluid chamber (8) and/or the cylinder (21). A device according to any one of the preceding claims, wherein the first pretensioning member has a preloaded state of a first spring length and a compressed state of a second spring length, wherein the first spring length and the second spring The ratio of lengths is in the range of 0.6 to 1, preferably in the range of 0.8 to 1. The apparatus of claim 4 or the claim of claim 4, wherein the apparatus (1) comprises a suction passage (4) and a compression chamber having a volume (3). And a pressure channel (5), wherein the compression chamber (3) is capable of establishing a flow connection with the suction passage (4), thereby allowing fluid to be drawn into the compression chamber (3) through the suction passage (4), and wherein The compression chamber (3) can establish a flow connection with the pressure channel (5), through which the fluid can be output to the compression chamber (3), and wherein the device (1) has a double diaphragm (6) , 7), the double diaphragm has a first diaphragm (6) and a second diaphragm (7) abutting the first diaphragm (6), wherein the double diaphragm (6, 7) abuts the compression a chamber (3), and the displacement piston (9) is configured to press the hydraulic fluid against the double diaphragm (6, 7) to deform the double diaphragm (6, 7) such that the device (1) The volume of the compression chamber (3) becomes larger during the suction period so that fluid can be drawn into the compression chamber (3) of the device (1) through the suction passage (4), and the compression chamber of the device (1) (3) The volume becomes smaller during the compression cycle so that it can be located in the compression In the (3) and outputs the fluid compression means (1) through the pressure channel (5). The device of claim 10, characterized in that The device (1) has an eccentric (10) configured to be pressed against the displacement piston (9) such that the displacement piston (9) presses the hydraulic fluid against the double diaphragm (6, 7) And the device (1) has a drive shaft (11) coupled to the eccentric (10) for rotating the eccentric (10), the drive shaft being configured to be rotatable by the drive shaft (11) The eccentric (10) is rotated. The device of claim 10 or 11, characterized in that the device has a suction valve (12) configured to allow communication between the compression chamber (3) and the suction passage (4) during an inhalation cycle The flow connection remains unobstructed and the flow connection is interrupted during the compression cycle, and/or the device (1) has a pressure valve (13) configured to interrupt the compression chamber (3) during the suction cycle a flow connection between the pressure channels (5) and opening the flow connection during a compression cycle, so that the compressed fluid in the compression chamber (3) can be output to the compression chamber through the pressure channel (5) 3). The device of claim 11 or the scope of the request item 11 as recited in claim 12, characterized in that the device (1) has a safety valve (19) and a valve cam (20), wherein the safety valve (19) can enter An open position in which the flow connection between the compression chamber (3) of the device (1) and the pressure channel (5) of the device (1) is opened and can be closed to a closed position Positionally, the flow connection between the compression chamber (3) of the device (1) and the pressure channel (5) of the device (1) is interrupted by the safety valve (19), and wherein the drive shaft of the device (1) (11) The valve cam (20) is coupled such that the valve cam (20) moves the safety valve (19) to the open position during the compression cycle as the drive shaft (11) rotates. A method of increasing fluid pressure in the case of using the device (1) according to any one of claims 1 to 13, comprising the steps of: (1) drawing the fluid through the suction passage (4) during the inhalation cycle Compression chamber (3), (2) compressing the fluid located in the compression chamber (3) during the compression cycle, and (3) outputting the fluid through the pressure passage (5) during the compression cycle.