Pressure intensifier device

Abstract

The invention relates to a pressure intensifier device comprising a working portion and a pump portion. The working portion comprises at least one combination of a working cylinder and a working piston, and the pump portion comprises at least one combination of a pump cylinder and a pump piston. A stroke of the working portion and a stroke of the pump portion at least partly overlap with each other. Additionally or alternatively, the stroke volume of the working cylinder is located at least partly radially further outward than the stroke volume of the pump cylinder.

Description

[0001] Pressure transducer device

[0002] The present invention relates to a pressure booster device.

[0003] An example of a pressure booster device is a pressure booster pump. An even more specific example of a pressure booster device is a pressure booster pump for fuels.

[0004] Exemplary fuels according to the present disclosure may be liquid alcohol or liquid ammonia. Examples of liquid alcohols used as fuel in internal combustion engines include methanol or ethanol. The fuels of interest here generally include so-called Power-to-X fuels. "Power-to-X" is a collective term for various technologies for storing or otherwise utilizing surplus electricity in times of a (future) oversupply of variable renewable energies such as solar energy, wind energy, and hydropower. In addition to the particularly preferred fuels methanol, ethanol, or ammonia mentioned above, Power-to-X fuels also include, but are not limited to, hydrogen, methane, and syngas (a mixture of hydrogen and carbon monoxide) (hereinafter generally referred to as "fuels").Compared to traditional fuels such as diesel or gasoline, such fuels have the advantage of being more environmentally friendly in production and combustion. A disadvantage of fuels such as alcohol or ammonia is that they are difficult to heat to the high pressure required for combustion.

[0005] Fuels such as alcohol and ammonia, for example, are often used alongside diesel in so-called dual-fuel engines. These engines are typically relatively large internal combustion engines, used, for example, in ships or power plants. Common pumps for alcohol (e.g., methanol or ethanol) or ammonia are industrial units. In other words, such pumps can be electrically driven and typically measure 2 x 1.5 x 1.5 meters, weigh approximately one ton or more, and are very expensive. These pumps run very slowly (i.e., well below 1000 rpm).

[0006] In contrast, known pumps for generating high pressure for diesel injection are small or compact and run significantly faster. A simple transfer of the function of a diesel pump to high-pressure generation with fuels such as alcohol and ammonia is not possible due to the different material properties (such as evaporation at low temperatures, high cavitation tendency, poor lubrication properties, and toxicity).

[0007] Therefore, there is a need for high-pressure fuel pumps for fuels such as alcohol and ammonia (or power-to-X fuels in general) that are small, compact, lightweight, cost-effective, and / or high-speed. While maintaining or improving the operational safety, reliability, and longevity of the pumps,

[0008] The desired pump concept should therefore offer a compact solution for mobile applications. The pump drive should not be rigidly coupled to the engine speed (e.g., via a gearbox), allowing the pump's flow rate to be adjusted independently of the engine speed.

[0009] According to the invention, a pressure booster device (for example a pressure booster pump) for fuels such as Power-to-X fuels is proposed as a technical solution to the above-mentioned need.

[0010] In conventional pressure intensifier pumps, the force-generating piston and the high-pressure-generating piston are arranged "in series," i.e., one behind the other. Fig. 11 shows a schematic diagram of the structure of such a pump. The conventional pressure intensifier device 1 has a low-pressure or working section 2 consisting of a low-pressure or working cylinder 3 and a low-pressure or working piston 4, as well as a high-pressure or pumping section 5 consisting of a high-pressure or pumping cylinder 6 and a high-pressure or pumping piston 7.

[0011] For pulsed operation, the pump section 5 can consist of a combination of exactly one pump cylinder 6 and one pump piston 7. If continuous operation of the pressure booster device 1 is desired, the pump section 5 can, for example, consist of a combination of two pump cylinders 6 and two pump pistons 7, as shown in Fig. 11.

[0012] A working medium is supplied to the working section 2 via valves 8. The working medium is discharged from the working section 2 via the valves 8. In Fig. 11, the valves 8 of the working section 2 are arranged on the outer surface of the working cylinder 3.

[0013] A medium to be pumped (conveying medium, for example, fuel) is supplied to the pumping section 5 via valves 9. The conveying medium is then discharged from the pumping section 5 via the valves 9 at the desired high pressure. In Fig. 11, the valves 9 of the pumping section 5 are arranged on the end face of the pump cylinder 6.

[0014] The operation of the conventional pressure booster device 1 shown in Fig. 11 is that the two chambers on opposite sides of the working piston 4 are alternately filled with a pressurized working medium. The pressure of the working medium is lower than the desired high pressure to which the pumped medium is to be brought. The pressurized working medium then presses on the working piston 4 and displaces it towards an opposite pump cylinder 6. The pump piston 7 is ideally rigidly connected to the working piston 4, for example via a rod. This means that essentially the same force acts on the pump piston 7 as on the working piston 4. However, since the pump piston 7 is smaller than the working piston 4, the constant force via the smaller pump piston generates a higher pressure on the pumped medium, which has flowed into the chamber of the pump cylinder 6 via a valve 9.The pumped medium is expelled from the chamber of the pump cylinder 6 at the desired high pressure via a valve 9. The pressure ratio corresponds to the reciprocal ratio of the two piston surfaces of the working piston 4 and the pump piston 7. Once the pumped medium has flowed out of the pump cylinder 6, the other chamber of the working cylinder 3 is filled with the working medium, and the process begins again in the opposite direction.

[0015] In this way, the pumped medium can be brought to the desired pressure without having to bring the entire system to the corresponding high pressure. This is advantageous in terms of cost and design (e.g., size and weight, but also the complexity of the device).

[0016] A disadvantage of the conventional design shown schematically in Fig. 11 is that the working section 2 and the pumping section 5 are arranged side by side or one behind the other, i.e., in series. This still results in a relatively large design.

[0017] The present invention is based on the object of providing an improved pressure booster device. For example, the present invention is intended to provide a compact and / or cost-effective and / or mobile pressure booster device. Furthermore, the pressure booster device can ensure safer operation of a system equipped with the pressure booster device.

[0018] A pressure booster device according to the invention is the subject of claim 1. Advantageous developments of the present invention are the subject of the dependent claims.

[0019] The inventive concept represents a significantly more compact design than a series arrangement by arranging the force-generating working piston and the pressure-generating pump piston "inside each other." This design offers advantages especially for mobile applications.

[0020] The pressure booster device according to the invention has a working section and a pumping section. The working section generates force. The pumping section generates pressure. The working section comprises at least one combination of a working cylinder and a working piston. The pumping section comprises at least one combination of a pumping cylinder and a pumping piston.

[0021] According to the invention, a stroke of the working section and a stroke of the pumping section overlap each other at least partially. Preferably, they can also overlap each other (almost) completely. In this case, "stroke" is understood to mean the complete travel of the respective pistons between their two dead centers in the associated cylinders. In this case, "overlap" is understood to mean a parallel arrangement of the strokes of the working section and the pumping section with respect to the longitudinal direction (stroke direction, which is the direction of the stroke) of the pressure intensifier device, unless explicit reference is made to the radial direction or a direction perpendicular to the longitudinal axis. In other words, "overlap" in this case means that the total length of the two sections (the working section and the pumping section) in the longitudinal direction of the pressure intensifier device is shorter than the sum of the lengths of the working section and the pumping section in the longitudinal direction of the pressure intensifier device.Therefore, the pressure booster device according to the invention can also be constructed more compactly, making it particularly advantageous for mobile applications. In this case, either the displacement of the working cylinder can be arranged at least partially radially further outward than the displacement of the pump cylinder, or the displacement of the pump cylinder can be arranged at least partially radially further outward than the displacement of the working cylinder. "Radial" is understood here to mean the radial direction of the pressure booster device, which is perpendicular to the longitudinal direction of the pressure booster device.

[0022] According to the invention - alternatively or in addition to the overlapping of the two sections - a displacement of the working cylinder is arranged at least partially radially further outwards than a displacement of the pump cylinder. In this case, displacement is understood to be the enclosed volume swept by the piston during one stroke. The displacement is therefore the space enclosed by the respective combination of cylinder and piston between the two dead centers of the piston (displacement volume). According to the invention, the displacement of the working cylinder can partially or completely overlap the displacement of the pump cylinder in the radial direction of the pressure intensifier device. However, the displacement of the working cylinder can also be arranged without overlap, completely further outwards in the radial direction than the displacement of the pump cylinder.

[0023] Preferably, the working section and the pumping section are parallel. This means that they extend at least partially adjacent to one another along the longitudinal direction of the pressure booster device, or that they are arranged such that one of the sections is located further outward in the radial direction of the pressure booster device than the other. Alternatively or additionally, (only) the working cylinder of the working section and the pumping cylinder of the pumping section are parallel.

[0024] Preferably, the working section and the pumping section are not arranged in series. This type of arrangement of the two sections can be chosen in addition to or as an alternative to a parallel arrangement of the sections. In other words, it is conceivable to arrange the working section and the pumping section not in series, although they do not necessarily have to extend parallel to each other. Alternatively or additionally, (only) the working cylinder of the working section and the pumping cylinder of the pumping section are not arranged in series.

[0025] Preferably, the working medium is air, hydraulic oil, fuel such as diesel, engine oil, water, etc.

[0026] Preferably, the pressure booster device is configured to pump fuel as the delivery medium. The fuel is preferably a Power-to-X fuel, as described above.

[0027] Preferably, the working section is configured to use the working medium at a working pressure of up to 60 MPa during operation of the pressure booster device.

[0028] In this context, working pressure is understood to be the pressure prevailing in the region of the working section during steady-state operation of the pressure booster device. The pumping section is preferably configured to pump the fuel (as the delivery medium) at a delivery pressure of up to 200 MPa during operation of the pressure booster device. The fuel is preferably liquid ammonia (during operation) or liquid alcohol (during operation). Even more preferably, the fuel is a methanol-based composition. Methanol is particularly preferred as a fuel.

[0029] In this case, delivery pressure is understood to be the pressure under which the delivery medium is ejected from the pump section during stationary operation of the pressure intensifier device.

[0030] In general, “operation” in this case means the intended use of the pressure intensifier device, in which the pressure intensifier device is used to pressurize a pumped medium with high pressure using a working medium.

[0031] The pressure booster device preferably has two working pistons and two pump pistons. In this way, continuous operation of the pressure booster device can be ensured on both the inlet and outlet sides, i.e., the working medium and the pumped medium. This can, for example, contribute to improved fuel injection, which achieves better (e.g., more efficient and / or less polluting) combustion. Furthermore, continuous operation can prevent pressure fluctuations, which, for example, has a positive effect on the service life of components of the pressure booster device and devices connected to it.

[0032] As described above, the total displacement of the working cylinder can be arranged radially further outwards than the displacement of the pump cylinder. Additionally or alternatively, the displacement of the working cylinder can be annular. An annular displacement of the working cylinder can preferably be arranged concentrically around the displacement of the pump cylinder. The displacement of the pump cylinder can preferably be cylindrical. However, it is also conceivable to arrange an (annular) displacement of the working cylinder radially further inwards than the displacement of the pump cylinder. These displacements or working and pump sections arranged in parallel with respect to the longitudinal direction of the pressure intensifier device result in a compact design of the pressure intensifier device.

[0033] Preferably, the working section comprises an annular working cylinder and an annular working piston. The working section is arranged concentrically around the pumping section. Alternatively, the working section comprises at least two working cylinders and associated working pistons. The working section is arranged concentrically around the pumping section. This design of the pressure booster device is also particularly compact.

[0034] The pump piston preferably comprises two opposing piston rods. The piston rods of the pump piston are each coupled to the piston rods of the working piston(s) via connecting elements. Connecting plates, for example, can be used as connecting elements. The connecting plates can, for example, have a triangular shape. This design is both compact and enables continuous operation of the pressure booster device.

[0035] Even more preferably, an annular working piston is provided with three piston rods on opposite sides relative to the longitudinal direction of the pressure intensifier device. With three piston rods on each side of the working piston, the connecting plates are preferably triangular. It is also preferred that the three piston rods are arranged offset by approximately 120 degrees in the circumferential direction of the piston or the pressure intensifier device. This design ensures the structural strength of the pressure intensifier device with the lowest possible complexity, size and mass of the pressure intensifier device. In particular, such a design counteracts torsional stress, for example on the piston rods. Even more preferably, the two arrangements of the three piston rods on the opposite axial sides of the working piston are offset by 60 degrees or 180 degrees in the circumferential direction of the piston orof the pressure intensifier device are offset or rotated with respect to one another. With such an arrangement, a particularly compact design can be ensured while still achieving the desired structural strength of the pressure intensifier device. Preferably, the working piston is pot-shaped and movable. The pump piston is tubular and rigid. The working piston and the pump piston are arranged such that an interior of the working piston forms the pump cylinder. In other words, the working piston and the pump cylinder are implemented or formed by the same component of the pressure intensifier device, which component can be pot-shaped, for example, and is movable within the working cylinder and relative to the immovable pump piston. Alternatively or additionally, the pump piston is at least partially inserted into the working piston.The working piston can be moved back and forth on the pump piston in the longitudinal direction of the pressure intensifier device. This design makes the pressure intensifier device even more compact. It eliminates one component—either the working piston or the pump cylinder, depending on the perspective.

[0036] Even if the present invention is not limited thereto, in general two designs of the pressure booster device according to the invention are particularly preferred, a design with an annular working piston (which is even more preferably arranged radially outside the pump cylinder), and a design with a pot-shaped working piston (or pump cylinder).

[0037] In the pressure intensifier device described here, the pressure and quantity of the required delivery (e.g., fuel, especially power-to-X fuel) is controlled by controlling the working medium (e.g., air, hydraulic oil, diesel, engine oil, water, etc.). The achievable pressure of the delivery medium is directly related to the area ratio of the working medium to the delivery medium. An example area ratio could be 4:1. The delivered quantity of the delivery medium can be controlled by the speed or number of strokes of the pressure intensifier device (pressure intensifier pump) per unit of time.

[0038] For a fuel injection system equipped with the pressure booster device according to the invention (particularly for, but not limited to, Power-to-X fuels), no safety valve against overpressure is required, since in the event of an undesirably high pressure in the injection system, the piston simply stops. This increases the reliability of the operation of the fuel injection system. Furthermore, it reduces the complexity, costs, and size of the fuel injection system, since otherwise required safety valves are not needed.

[0039] In the pressure booster device according to the invention, the ratio of pump pressure (pressure of the pumped medium discharged) to working pressure (pressure of the working medium input) during operation of the pressure booster device is preferably in a range of greater than 1 to 8, preferably from 2 to 8, more preferably from 3 to 7 and particularly preferably from 4 to 6.

[0040] In the pressure booster device according to the invention, the working pressure during operation is preferably in a range from 10 MPa to 60 MPa, more preferably from 20 MPa to 50 MPa and particularly preferably from 20 MPa to 40 MPa.

[0041] In the pressure booster device according to the invention, the pump pressure during operation is preferably in a range from 30 MPa to 200 MPa, more preferably from 50 MPa to 100 MPa and particularly preferably from 60 MPa to 80 MPa.

[0042] The achievable pumping pressure is directly related to the area ratios of the working piston and pumping piston (e.g., 4:1). The delivered quantity of the pumped medium (e.g., the Power-to-X fuel) can be controlled by the speed or number of strokes of the device (e.g., pump) per unit of time.

[0043] Although the pressure booster device is primarily described here, the present disclosure is also directed to using the pressure booster device to transmit a lower pressure of a working medium to a conveying medium, the pressure of which is thus increased and is greater than the pressure of the working medium, and therefore to using the pressure booster device for pressure boosting. Likewise, the present disclosure is also directed to a pressure boosting method whose method steps correspond to an operation of the pressure booster device according to the invention. Furthermore, the present disclosure is also directed to systems that comprise the pressure booster device according to the invention, such as fuel injection systems. The features and embodiments of the pressure booster device described here can be combined with one another as desired, as long as the resulting combinations are technically expedient orat least one of the advantageous effects described herein can be achieved. In particular, individual features of the preferred embodiments described below can be taken from individual embodiments and used in other embodiments.

[0044] Embodiments of the present invention will be described in detail below.

[0045] Fig. 1 is a side sectional view along the longitudinal axis of an embodiment of the pressure intensifier device disclosed herein.

[0046] Fig. 2 is a perspective view of the pressure intensifier device of Fig. 1.

[0047] Fig. 3 is a perspective sectional view of a portion of the pressure booster device of Fig. 1 along the longitudinal axis of the pressure booster device.

[0048] Fig. 4 is a perspective sectional view of a portion of the pressure booster device of Fig. 1 perpendicular to the longitudinal axis of the pressure booster device.

[0049] Fig. 5 is a sectional view of a portion of the pressure booster device of Fig. 1 along the longitudinal axis of the pressure booster device.

[0050] Fig. 6 is a sectional view of a portion of the pressure booster device of Fig. 1 perpendicular to the longitudinal axis of the pressure booster device.

[0051] Fig. 7 is a side sectional view along the longitudinal axis of another embodiment of the pressure booster device disclosed herein.

[0052] Fig. 8 is a perspective view of the pressure booster device of Fig. 7. Fig. 9 is a perspective sectional view of the pressure booster device of Fig. 7 along the longitudinal axis of the pressure booster device.

[0053] Fig. 10 is a sectional view of a portion of the pressure booster device of Fig. 7 along the longitudinal axis of the pressure booster device.

[0054] Fig. 11 is a schematic diagram of a conventional pressure intensifier pump.

[0055] The following description focuses in particular on two designs of the pressure booster device according to the invention. The (first) embodiment or design shown in Figures 1 to 6 has an annular working piston arranged radially outside the pump cylinder. The (second) embodiment or design shown in Figures 7 to 10 has a cup-shaped working piston or pump cylinder.

[0056] First, the embodiment shown in Figures 1 to 6 will be described.

[0057] Figures 1 and 3 show a pressure booster pump 10 as an example of a pressure booster device. The pressure booster pump 10 comprises a working section 30 and a pumping section 50. Furthermore, the pressure booster pump 10 comprises a first connection plate 11 and a second connection plate 12, as well as two connecting plates 13.

[0058] The pressure booster pump 10 of the first embodiment is characterized in particular by a concentric and, with respect to the longitudinal axis of the pressure booster pump 10, parallel arrangement of the working section 30 and the pumping section 50.

[0059] In this case, the working section 30 is arranged completely outside the pumping section 50 in the radial direction of the pressure booster pump 10. In other words, in the direction perpendicular to the longitudinal axis of the pressure booster pump 10, the working section 30 and the pumping section 50 do not overlap. Relative to or along the longitudinal axis of the pressure booster pump 10, the working section 30 and the pumping section 50 overlap each other essentially completely.

[0060] The working section 30 completely encloses the radially inner pumping section 50 in the circumferential direction of the pressure booster pump 10.

[0061] The working section 30 comprises a combination of a working cylinder 31 and a working piston 32. In addition, the working section 30 here comprises a displacement (working displacement) 33 and at least one piston rod (working piston rod) 34.

[0062] The displacement 33 of the working section 30 is determined by the radial inner surface of the

[0063] Working cylinder 31, the working piston 32, the radial outer surface of the pump cylinder 51, and the axial inner surfaces of the first and second connecting plates 11, 12 are delimited or defined. In other words, the displacement 33 of the working section 30 is arranged in a ring around the pump cylinder 51 of the pump section 50 or around the pump section 50. In the present embodiment, the displacement 33 completely encloses the pump cylinder 51 in the circumferential direction of the pressure booster pump 10 or the working section 30 or the pump section 50.

[0064] The displacement 33 is divided into two chambers by the working piston 32. The two chambers are located on opposite sides of the working piston 32 in the longitudinal direction of the pressure booster pump 10, the working section 30, and the pumping section 50, respectively.

[0065] As can be seen in Figures 1 and 3, the working piston 32 has a two-part construction, with three of the six piston rods 34 being inserted into one of the two parts of the working piston 32 from one side in the longitudinal direction of the pressure intensifier pump 10, and the other three piston rods 34 being inserted into the other of the two parts of the working piston 32 from the opposite side in the longitudinal direction of the pressure intensifier pump 10. This two-part construction of the working piston 32 simplifies the assembly of the working section 30, particularly in view of the large number of piston rods 34 to be inserted. Thus, three of the piston rods 34 can be inserted into the working cylinder 31 or the displacement chamber 33 from one axial end of the pressure intensifier pump 10, and the other three piston rods 34 can be inserted into the working cylinder 31 or the displacement chamber 33 from the opposite axial end of the pressure intensifier pump 10.

[0066] It is understood that the total number of piston rods 34 may be fewer or more than six. Likewise, the distribution of the piston rods 34 on both sides of the working piston 32 does not have to be the same. For example, two piston rods 34 may be arranged on one side and three piston rods 34 on the opposite side of the working piston 32.

[0067] It is also understood that the working piston 32 can also be constructed as a single piece. This may, for example, complicate the assembly of the working section 30, but may have advantages for the strength or service life of the working piston 32 or for the sealing between the two chambers of the displacement volume 33. A multi-part construction of the working piston 32, i.e., a construction with more than two parts, is also possible if this is advantageous, for example, with regard to assembly.

[0068] An exemplary assembly sequence for the working section 30 can be such that the corresponding piston rods 34 are inserted into through-openings 17 (see Figures 4 and 6) in the associated connecting plates 11, 12 and then into the associated openings in the working piston 32. Then, if the working piston 32 is designed as a two-part unit, the working piston 32 can be inserted into the working cylinder 31 or the displacement chamber 33. Subsequently or simultaneously, the associated connecting plate 11, 12 can be mounted onto the corresponding axial end of the pressure booster pump 10 or the working cylinder 31. The connecting plate 13 can be mounted before or after the piston rods 34 by inserting and securing the ends of the piston rods 34 that are longitudinally opposite to the working piston 32 into through-openings in the connecting plate 13.The piston rods 34 can also be permanently mounted on the connecting plate 13, for example by welding. In this case, no through openings need to be provided in the connecting plate 13. The assembly process is repeated accordingly on the opposite side in the longitudinal direction of the pressure intensifier pump 10. Unlike what is shown in Figures 1 and 3, it would also be conceivable to design the working section 30 such that it does not completely surround the pumping section 50 or only partially surrounds it in the circumferential direction of the pressure intensifier pump 10. It would also be conceivable to arrange the working section 30 and the pumping section 50 parallel to one another such that neither section surrounds the other, i.e., that the two sections overlap one another only in the longitudinal direction of the pressure intensifier pump 10, but not in the radial direction of the pressure intensifier pump 10.

[0069] The pump section 50 comprises a combination of a pump cylinder 51 and a pump piston 52. In addition, the pump section here comprises a displacement chamber (pump displacement chamber) 53 and at least one piston rod (pump piston rod) 54.

[0070] The displacement 53 of the pump section 50 is limited or defined by the radial inner surface of the pump cylinder 51, the pump piston 52, and the axial inner surfaces of the first and second connecting plates 11, 12. In other words, the displacement 53 of the pump section 50 is cylindrical within the pump cylinder 51. In the present embodiment, the pump cylinder 51 is completely enclosed by the displacement 33 of the working section 30 in the circumferential direction of the pressure booster pump 10 or the working section 30 or the pump section 50.

[0071] The displacement 53 is divided into two chambers by the pump piston 52. The two chambers are located on opposite sides of the pump piston 52 in the longitudinal direction of the pressure booster pump 10, the working section 30, and the pump section 50, respectively.

[0072] As can be seen in Figures 1 and 3, the pump piston 52 is constructed in one piece, with one of the two piston rods 54 being inserted into one of the two parts of the pump piston 52 from one side in the longitudinal direction of the pressure booster pump 10, and the other piston rod 54 being inserted into the pump piston 52 from the opposite side in the longitudinal direction of the pressure booster pump 10. Since the pump section 50 in this case comprises only two piston rods 54, assembly is relatively simple even with a one-piece pump piston 52. The one-piece construction of the pump piston 52 has advantages for the strength and service life of the pump piston 52 and also for the sealing between the two chambers of the displacement chamber 53.

[0073] It is understood that the total number of piston rods 54 may be fewer or more than two. Likewise, the distribution of the piston rods 54 on both sides of the pump piston 52 does not need to be the same. For example, two piston rods 54 may be arranged on one side and one piston rod 54 on the opposite side of the pump piston 52.

[0074] It is also understood that the pump piston 52 can also be constructed in two or more parts. This can, for example, facilitate the assembly of the pump section 50, as described above in connection with the assembly of the working section 30.

[0075] An exemplary assembly sequence of the pump section 50 can be such that the corresponding piston rod 54 is inserted into a through-opening 18 (see Figures 4 and 6) in the associated connecting plate 11, 12 and then into the associated opening in the pump piston 52. The pump piston 52 can then be inserted into the pump cylinder 51 or the displacement chamber 53. Subsequently or simultaneously, the associated connecting plate 11, 12 can be mounted on the corresponding axial end of the pressure booster pump 10 or the pump cylinder 51. The connecting plate 13 can be mounted before or after the piston rod 54 by inserting and fixing the end of the piston rod 54 that is longitudinally opposite to the pump piston 52 into a through-opening in the connecting plate 13. The piston rod 54 can also be permanently mounted to the connecting plate 13, for example by welding.In this case, no through-openings need to be provided in the connecting plate 13. The assembly process is repeated accordingly on the opposite side in the longitudinal direction of the pressure intensifier pump 10, whereby the other piston rod 54 is only inserted into the pump piston 52 within the pump cylinder 51 or displacement chamber 53. A similar procedure can be followed when assembling the working section 30 if the working piston 32 is of one-piece design. In the example shown in Figures 1 and 3, the piston rods 34, 54 are detachably mounted to the connecting plates 13 by means of a screw connection. Other detachable connections are conceivable, for example by means of a tongue and groove. Likewise, other (permanent) connections than welding are conceivable, such as by shrinking. The monolithic production of the connecting plates 13 with the piston rods 34, 54 using additive processes is also conceivable.

[0076] In Fig. 2, the pressure booster pump 10 according to the invention is shown in perspective, with the connecting plates 11, 12 only indicated. In addition, a connecting piece 14 is shown as an example on the connecting plate 11 on the left in Fig. 2.

[0077] The connecting plates 11, 12 are preferably monolithic components and contain flow channels formed by machining processes, such as drilling. The connecting plates 11, 12, including the flow channels formed therein, can also be manufactured monolithically using additive processes. It is also conceivable that the connecting plates 11, 12 are not monolithic components, but merely housings with flexible or rigid lines located therein.

[0078] In the present embodiment, the connecting plates 11, 12 each contain a working medium inlet / outlet (working medium connection) 15, as well as a pumping medium inlet 16 and a pumping medium outlet 16 (pumping medium connections 16). The pumping medium inlet 16 and the pumping medium outlet 16 can be interchangeable, depending on how they are connected to downstream or upstream devices. Although the working medium connection 15 is a combined inlet and outlet for the working medium, it can also be implemented via two connections, for example, if corresponding one-way valves are provided in the connecting plates 11, 12.

[0079] The working medium flows through the respective connection plate 11, 12 into the displacement chamber 33 and out of it again via the working medium connection 15. The pump medium flows through the respective connection plate 11, 12 into the displacement chamber 53 and out of it again via the pump medium connections 16.

[0080] The respective ports 15, 16 are connected to downstream and upstream devices, respectively, by means of connectors 14. Accordingly, in the case of the first embodiment, six connectors 14 are provided, one of which is shown as an example in Fig. 2.

[0081] Figures 4 and 6 show the connection plate 11 in a section perpendicular to the longitudinal axis of the pressure booster pump 10. The two connection pieces 14 mounted on the pump medium connections 16 are visible. Furthermore, the channels are visible that fluidically connect the connection pieces 14 or pump medium connections 16 to the displacement chamber 53 and through which the pump medium flows into and out of the displacement chamber 53.

[0082] Furthermore, Figures 4 and 6 show the working medium connection 15 without an associated connecting piece. Furthermore, the channels that fluidically connect the working medium connection 15 or the associated connecting piece to the displacement chamber 33 and through which the working medium flows into and out of the displacement chamber 33 are visible.

[0083] Figures 4 and 6 further show that the through-hole 18 for the piston rod 54 is arranged centrally, and the through-holes 17 for the piston rods 34 are arranged radially outward, surrounding the through-hole 18. The through-holes 17 are offset from one another by 120 degrees in the circumferential direction of the pressure booster pump 10 or the connecting plate 11. The distance between the through-holes 17 and the through-hole 18 is the same in each case. This results in a symmetrical arrangement. However, an asymmetrical arrangement of the through-holes 17, 18 is also conceivable.

[0084] The connection plate 12 can, for example, be structurally identical to the connection plate 11, but this does not have to be the case. The connection plate 12 can be arranged in the pressure intensifier pump 10 offset by 180 degrees or rotated (around the longitudinal axis of the pressure intensifier pump 10) with respect to the connection plate 11. This arrangement would correspond to an upside-down view of Fig. 6. However, the connection plate 12 can also be arranged offset by 60 degrees or rotated (around the longitudinal axis of the pressure intensifier pump 10) with respect to the connection plate 11. For this purpose, the pump medium connections 16 shown in Figs. 4 and 6, including the connection pieces 14, as well as the working medium connection 15, might have to be slightly offset under certain circumstances.

[0085] The identical design of the connection plates 11 and 12 enables cost savings in the manufacture, assembly, maintenance and logistics of the pressure intensifier pump 10.

[0086] The connection piece 14 shown on the left in Figures 4 and 6 serves as an inlet connection piece 14 for the pumping medium in the present embodiment, and the connection piece 14 shown on the right serves as an outlet connection piece 14 for the pumping medium in the present embodiment.

[0087] Fig. 5 shows a sectional view of a portion of the pressure booster pump 10 along the longitudinal axis of the pressure booster pump 10. The sealing system of the pressure booster pump 10 can be particularly clearly illustrated in Fig. 5. Fig. 5 only shows the grooves into which corresponding, for example, elastic sealing elements, such as sealing rings, can be inserted.

[0088] In this case, the three seals 21, 22 and 23 are provided in particular for sealing the working medium.

[0089] The seal 21 is intended to prevent the working medium from escaping from the pressure booster pump 10 or from the displacement chamber 33 by sealing between the piston rod 34 and the connection plate 11. The seal 22 is intended to prevent the working medium from escaping from one chamber of the displacement chamber 33 to the other chamber of the displacement chamber 33 on the opposite side of the working piston 32 by sealing between the working piston 32 and the working cylinder 31. The seal 23 is intended to prevent the working medium from escaping from the pressure booster pump 10 or from the displacement chamber 33 by sealing between the connection plate 11 (or 12) and the working cylinder 31. The seal 23 is arranged on the radial outer side of the connection plate 11. Alternatively or additionally, a (further) seal could be arranged on the axial end face of the connection plate for the same purpose, similar to the seal 26.

[0090] In this case, the three seals 24, 25 and 26 are provided in particular for sealing the pumped medium.

[0091] The seal 24 is intended to prevent the pumped medium from escaping from the pressure booster pump 10 or from the displacement chamber 53 to the outside by sealing between the piston rod 54 and the connecting plate 11. The seal 25 is intended to prevent the pumped medium from escaping from one chamber of the displacement chamber 53 to the other chamber of the displacement chamber 53 on the opposite side of the pump piston 52 by sealing between the pump piston 52 and the pump cylinder 51. The seal 26 is intended to prevent the pumped medium from escaping from the pressure booster pump 10 or from the displacement chamber 53 to the outside or into the displacement chamber 33 by sealing between the connecting plate 11 and the pump cylinder 51. In the present case, the seal 26 is arranged on the axial end face of the pump cylinder 51. Alternatively or additionally, a (further) direction could be arranged on the radial outside of the pump cylinder 51 for the same purpose, similar to what is the case with the seal 23.

[0092] All seals 21 to 26 described here can comprise several sealing elements, as is the case with seals 21, 22, 24 and 25 here, or can each comprise one sealing element, as is the case with seals 23 and 26 here.

[0093] The seals 21 to 26 shown are purely exemplary and can also be arranged differently. For example, seal 21 can be mounted on piston rods 34 instead of being inserted into connection plate 11. The same applies to seal 24. Likewise, seal 23 can be inserted into working cylinder 31 instead of connecting plate 11. Seal 26 can also be inserted into connection plate 11 instead of pump cylinder 51. Any combination of the arrangement options for seals 21 to 26 described here, as well as any additional seals, is conceivable.

[0094] Exemplary technical data of the pressure booster pump 10 of the present embodiment include the following values:

[0095] Total length of the pressure intensifier pump 10 including stroke: approximately 1050 mm Weight of the pressure intensifier pump 10: 75 kg

[0096] Stroke: 250 mm

[0097] Working medium consumption / stroke: about 2.4 l at 10 MPa (ie 12 l / min working medium consumption)

[0098] Pumped medium volume / stroke: about 0.4 l at 60 MPa (ie 20 1 / min flow rate)

[0099] - Piston speed: about 0.5 m / s.

[0100] The above values ​​are purely exemplary. However, they illustrate the size and weight advantages compared to the conventional pumps described above. The pressure booster pump 10 according to the invention is in no way limited to this combination of values ​​or to individual values. Individual values ​​or any combination of these values ​​can be implemented in the embodiments disclosed herein.

[0101] The principle of the first embodiment shown in Figures 1 to 6 essentially consists in the fact that an annular working piston 32 or displacement chamber 33 surrounds a cylindrical pump piston 52 or displacement chamber 53. When a chamber of the displacement chamber 33 is filled with the pressurized working medium via the working medium connection 15 and the channels in the connection plate 11 or 12, the (larger) annular working piston 32 moves, taking the (triangular) connecting plate 13 with it via the (three) piston rods 34. The pump piston 52 is actuated via the connecting plate 13 and the piston rod 54 and thus moves in the same direction as the working piston 32.The pumped medium, which has entered a chamber of the displacement 53 via a pumped medium connection 16 and the channels in the connecting plate 11 or 12, is pressurized by the (smaller) pump piston 52 and expelled from the pressure booster pump 10 under high pressure via the other pumped medium connection 16 and the channels in the connecting plate 11 or 12. This high pressure is essentially achieved by the fact that the area of ​​the annular working piston 32 is larger than the area of ​​the cylindrical pump piston 52.

[0102] When the pressure intensifier pump 10 is in operation, the working medium is controlled via external valves, which are not shown.

[0103] In this way, with a compact design of the pressure intensifier pump 10, the pumped medium can be subjected to a pressure and expelled from the pressure intensifier pump 10 that is (significantly) higher than the pressure of the working medium flowing into the pressure intensifier pump 10 (pressure intensification).

[0104] Figures 7 to 10 show a further (second) embodiment of the pressure booster pump 10 according to the invention. The same components in the second embodiment are represented by the same reference numerals as in the first embodiment.

[0105] Figures 7, 8, and 9 show a pressure booster pump 10 as an example of a pressure booster device. The pressure booster pump 10 comprises a working section 30 and a pumping section 50. Furthermore, the pressure booster pump 10 comprises a first connection plate 61 and a second connection plate 62, as well as a coupling plate 63.

[0106] The pressure booster pump 10 of the second embodiment is particularly characterized by a nested arrangement of the working section 30 and the pumping section 50. In this arrangement, the working piston of the working section 30 and the pumping cylinder of the pumping section 50 are formed by the same component with the reference numeral 70, a combined working piston-pump cylinder (hereinafter referred to as the pot) 70.

[0107] In this case, the working section 30 is arranged partially outside the pumping section 50 in the radial direction of the pressure booster pump 10. In other words, in the direction perpendicular to the longitudinal axis of the pressure booster pump 10, the working section 30 and the pumping section 50 partially overlap each other.

[0108] Relative to or along the longitudinal axis of the pressure intensifier pump 10, the working section 30 and the pumping section 50 partially overlap each other.

[0109] In the present embodiment, the pressure booster pump 10 comprises a substantially symmetrical arrangement around the coupling plate 63, comprising two (partial) working sections 30 and two (partial) pumping sections 50. For non-continuous operation, however, the provision of only one (partial) working section 30 and one (partial) pumping section 50 would be sufficient. In such a case, the structure of the pressure booster pump 10 would be similar to the part of the pressure booster pump 10 depicted in Fig. 10.

[0110] The working section 30 completely encloses the radially inner pumping section 50 in the circumferential direction of the pressure booster pump 10.

[0111] The working section 30 comprises a combination of the working cylinder 31 and a working piston formed by the peripheral walls and the end faces (in particular the bottom) of the pot 70. Furthermore, the working section 30 in this case comprises a displacement (working displacement) 33.

[0112] In the present embodiment, the two pots 70 are essentially rigidly connected to each other via at least one rod 71 (see Fig. 9), preferably via three rods 71. This is intended to ensure a constant distance in the longitudinal direction of the pressure booster pump 10 between the two pots 70, or a coupling of the two pots 70.

[0113] The displacement 33 of the working section 30 is limited or defined by the radial inner surface of the working cylinder 31, the outer surfaces of the pot 70 (in particular, the outer part of the bottom of the pot 70), and the axial inner surfaces of the first and second connecting plates 61, 62. In other words, the displacement 33 of the working section 30 is cylindrical and arranged in the longitudinal direction of the pressure booster pump 10 between the pot 70 and the first and second connecting plates 61, 62.

[0114] In the present embodiment, the displacement 33 is divided into two chambers by the two pots 70 connected by the rod 71. The two chambers are located on opposite sides of the interconnected pots 70 in the longitudinal direction of the pressure booster pump 10, the working sections 30, and the pumping sections 50, respectively.

[0115] As already described, in the present embodiment, the axially and radially outer part of the pot 70 corresponds to the working piston. The pot 70 slides along the radially inner surface of the working cylinder 31 and thus, in combination with the working cylinder 31, forms part of the working section 30. On the other hand, in the present embodiment, the radially inner part and the inner part of the pot bottom of the pot 70 correspond to the pump cylinder. The pot 70 slides along the radially outer surface of the stationary pump piston 52 and thus, in combination with the pump piston 52, forms part of the pump section 50.

[0116] Due to the nested structure of the working cylinder 31, the pot 70 and the pump piston 52, a compact design of the pressure intensifier pump 10 can be achieved.

[0117] As also already described, continuous pumping operation is achieved by means of two pots 70, which are rigidly connected to one another by at least one rod 71. Preferably, three rods 71 ​​are used to couple the two pots, as in the present embodiment. It is understood that two or more than three rods 71 ​​may also be used.

[0118] The pump section 50 comprises a combination of the movable pump cylinder, which is formed by the inside of the pot 70, and a rigid, immovable pump piston 52. Furthermore, the pump section 50 in this case comprises a displacement (pump displacement) 53. The displacement 53 of the pump section 50 is limited or defined by the radial inner surface of the pot 70 and by the inside of the pot base of the pot 70 (i.e., by the pot interior of the pot 70) as well as by the pump piston 52 (more precisely, by an axial end face of the pump piston 52). In other words, the displacement 53 of the pump section 50 is cylindrical within the pot 70.

[0119] In the present embodiment, the displacement 53 is divided into two chambers, each of which is formed within one of the two pots 70.

[0120] As already described, in the present embodiment, two (partial) working sections 30 and two (partial) pumping sections 50 are arranged substantially symmetrically around a substantially centrally arranged coupling plate 63 and are detachably mounted to the coupling plate 63 by means of flanges 64. In the present case, the detachable connection is achieved with screw bolts, as can be seen in Fig. 8, in which the coupling plate 63 is omitted and merely indicated in order to clarify the internal structure of the pressure intensifier pump 10. It is understood that other detachable connections, such as clamps, can also be used. Permanent connections, such as welding, are also possible for coupling the components of the pressure intensifier pump 10.

[0121] An exemplary assembly sequence for the pressure booster pump 10 of the second embodiment could be to first connect the rigid pump pistons 52 to the coupling plate 63. This can be done, for example, by means of a screw connection, wherein the pump pistons 52 are screwed into the coupling plate 63. Subsequently, the movable pots 70 can be mounted on the pump pistons 52 or slid over the pump pistons 52. After that, the working cylinders 31 can be mounted on the pots 70 or slid over the pots 70. The flanges 64 can, for example, be firmly connected to the working cylinders 31. The connection can be made, for example, by welding or shrinking. A detachable connection using a screw connection or a tongue and groove connection would also be conceivable. Alternatively, the working cylinders 31 can, for example, have radially outwardly projecting projections or flanges on their axial ends facing the coupling plate 63.The annular flanges 64 can then be pushed from the axial ends of the working cylinders 31 facing away from the coupling plate 63 toward the coupling plate 63 or the projections or flanges, and then connected to the coupling plate 63. By connecting the flanges 64 to the coupling plate 63 or to one another via the coupling plate 63, the two (partial) working sections 30 and two (partial) pumping sections 50 are connected to one another. Before or, if necessary, after this, the connection plates 61, 62 are mounted on the axial outer ends of the working cylinders 31. Here, too, detachable or permanent connections are possible, such as screw connections, the use of tongue and groove joints, welded joints, or shrink-fitting, etc. It is understood that the working cylinders 31 with the flanges 64 and / or the connection plates 61, 62 can be manufactured monolithically using additive processes.

[0122] In addition, connecting pieces 14 are mounted on the working medium connections 15 in the connecting plates 61, 62 and on the pumping medium connections 16 (see Fig. 10) in the coupling plate 63. In Figures 7 to 10, only the connecting pieces 14 mounted on the coupling plate 63 are visible, while the connecting pieces 14 mountable on the connecting plates 61, 62 are not shown.

[0123] In Fig. 8, the pressure booster pump 10 according to the invention is shown in perspective, with the coupling plate 63 only indicated. Two connecting pieces 14 are shown as examples on the indicated coupling plate 63.

[0124] The connecting plates 61, 62 are preferably monolithic components and contain at least one (continuous) flow channel formed by machining processes, such as drilling. The connecting plates 61, 62, including the at least one flow channel formed therein, can also be manufactured by additive processes. It is also conceivable that the connecting plates 61, 62 are not monolithic components, but merely housings with flexible or fixed lines located therein.

[0125] In the present embodiment, the connection plates 61, 62 each contain a working medium inlet / outlet (working medium connection) 15. Although the working medium connection 15 is a combined inlet and outlet for the working medium, it can also be realized via two connections if, for example, corresponding one-way valves are provided in the connection plates 61, 62.

[0126] The coupling plate 63 contains a pumping medium inlet 16 and a pumping medium outlet 16 (pumping medium connections 16). The pumping medium inlet 16 and the pumping medium outlet 16 (see Fig. 10) can be interchangeable, depending on how they are connected to downstream and upstream devices, respectively.

[0127] Via the working medium connection 15, the working medium flows through the respective connection plates 61, 62 into the displacement chamber 33 and out of it again. Via the pump medium connections 16, the pump medium flows through the coupling plate 63 into the displacement chamber 53 and out of it again.

[0128] The respective ports 15, 16 are connected to downstream and upstream devices, respectively, by means of connectors 14. Accordingly, in the case of the second embodiment, four connectors 14 are provided, two of which are shown as examples in Figures 7 to 10.

[0129] Figures 7, 9, and 10 show the connection plates 61, 62 and the coupling plate 63 in a section along the longitudinal axis of the pressure booster pump 10. The two connection pieces 14 are visible, which are mounted on the pump medium connections 16 on the coupling plate 63. Furthermore, the channels are visible that fluidically connect the connection pieces 14 or pump medium connections 16 with the displacement chamber 53 and through which the pump medium flows into and out of the displacement chamber 53.

[0130] Furthermore, in Figures 7 to 10, the working medium connection 15 is shown without an associated connecting piece. Furthermore, Figures 7, 9, and 10 show the channels that fluidically connect the working medium connection 15 or the associated connecting piece to the displacement chamber 33 and through which the working medium flows into and out of the displacement chamber 33. The connection plate 62 can, for example, be constructed identically to the connection plate 61. The identical design of the connection plates 61 and 62 enables cost savings in the manufacture, assembly, maintenance, and logistics of the pressure booster pump 10.

[0131] The connection piece 14 shown at the top in Figures 7, 9 and 10 serves as an inlet connection piece 14 for the pumping medium in the present embodiment, and the connection piece 14 shown at the bottom serves as an outlet connection piece 14 for the pumping medium in the present embodiment.

[0132] Fig. 10 shows a sectional view of a portion of the pressure booster pump 10 along the longitudinal axis of the pressure booster pump 10. The sealing system of the pressure booster pump 10 can be particularly clearly illustrated in Fig. 10. Fig. 10 shows only the grooves into which corresponding, for example, elastic sealing elements, such as sealing rings, can be inserted.

[0133] In this case, the two seals 81 and 82 are provided in particular for sealing the working medium.

[0134] The seal 81 is intended to prevent the working medium from escaping from the pressure booster pump 10 or from the displacement chamber 33 by sealing between the working cylinder 31 and the connection plate 61 or 62. The seal 81 is presently arranged in the base of the pot-shaped connection plate 61 or 62, but can also be arranged on the axial end face of the working cylinder 31. Alternatively or additionally, a (further) seal could be arranged on the radial outer side of the working cylinder 31 or on the radial inner side of the connection plate 61 or 62 for the same purpose. The seal 82 is intended to prevent the working medium from escaping from the displacement chamber 33 to the coupling plate 63 on the axially opposite side of the pot 70 or into the displacement chamber 53 by sealing between the pot 70 and the working cylinder 31. In this case, the three seals 83, 84 and 85 are provided in particular for sealing the pumped medium.

[0135] The seal 83 is intended to prevent pump medium from the displacement chamber 53 from passing past the pump piston 52 into the coupling plate 63 by sealing between the pump piston 52 and the coupling plate 63. The seal 83 can be arranged on the axial end face and / or on the radial outside of the pump piston 52. The seal 83 can also be arranged on the axial end face and / or on the radial inside of the coupling plate 63. Combinations of these variants are possible. The seal 84 is intended to prevent the pump medium from escaping from the pressure booster pump 10 to the outside by sealing between the working cylinder 31 and the coupling plate 63. The seal 84 can be arranged on the axial end face and / or on the radial inside of the working cylinder 31. The seal 84 can be arranged on the axial end face and / or on the radial outside of the coupling plate 63. Combinations of these variants are possible.The seal 85 is intended to prevent pumped medium from the displacement chamber 53 from passing past the pump piston 52 into the coupling plate 63 or into the displacement chamber 33 by sealing between the pump piston 52 and the cup 70. The seal 85 can be implemented by selecting an appropriate clearance between the cup 70 and the pump piston 52 or, for example, by means of a sealing ring (O-ring). In the latter case, the seal 85 can be arranged on the radial inside of the cup 70 and / or on the radial outside of the pump piston 52.

[0136] All seals 81 to 85 described here can comprise several sealing elements, as is the case with seal 82 here, or can each comprise one sealing element, as is the case with seals 81 and 83 to 85 here.

[0137] Exemplary technical data of the pressure booster pump 10 of the present embodiment include the following values:

[0138] Total length of the pressure intensifier pump 10: about 850 mm Weight of the pressure intensifier pump 10: 75 kg Stroke distance: 130 mm

[0139] Working medium consumption / stroke: about 1 l at 15 MPa (ie 120 1 / min working medium consumption)

[0140] Pumped medium volume / stroke: about 0.25 l at 60 MPa (ie 30 1 / min delivery rate)

[0141] - Piston speed: about 0.5 m / s.

[0142] The above values ​​are purely exemplary. However, they illustrate the size and weight advantages compared to the conventional pumps described above. The pressure booster pump 10 according to the invention is in no way limited to this combination of values ​​or to individual values. Individual values ​​or any combination of these values ​​can be implemented in the embodiments disclosed herein.

[0143] The principle of the second embodiment shown in Figures 7 to 10 essentially consists in the fact that a pot-shaped combination (pot 70) consisting of the working piston and the movable pump cylinder is arranged between the working cylinder 31 and the rigid pump piston 52. When a chamber of the displacement 33 is filled with the pressurized working medium via the working medium connection 15 and the channels in the connection plate 61 or 62, the working piston formed by the pot 70 moves and, via the rods 71, takes with it the movable pump cylinder formed by the further pot 70. The movable pump cylinder slides on the immovable, rigid pump piston 52.The pumped medium, which has entered a chamber of the displacement chamber 53 via a pumped medium connection 16 and the channels in the coupling plate 63, is pressurized by the pump cylinder, which slides over the rigid pump piston 52, and expelled from the pressure booster pump 10 under high pressure via the other pumped medium connection 16 and the channels in the coupling plate 63. This high pressure is essentially achieved by the fact that the area of ​​the interior of the pot base of the pot 70 is smaller than the area of ​​the exterior of the pot base of the pot 70.

[0144] The movement of the pot 70 (the working cylinder) is controlled by the flow of the working medium. During operation of the pressure intensifier pump 10, the working medium is controlled via external valves, which are not shown. In this way, with a compact design of the pressure intensifier pump 10, the pumped medium can be subjected to a pressure and expelled from the pressure intensifier pump 10 that is (significantly) higher than the pressure of the working medium flowing into the pressure intensifier pump 10 (pressure intensification).

Claims

Claims 1. Pressure booster device with a working section with at least one combination of a working cylinder and a working piston; and a pumping section with at least one combination of a pumping cylinder and a pumping piston; wherein a stroke of the working section and a stroke of the pumping section at least partially overlap each other, and / or a displacement of the working cylinder is arranged at least partially radially further outward than a displacement of the pumping cylinder.

2. Pressure booster device according to claim 1, wherein the stroke of the working section and the stroke of the pumping section substantially completely overlap each other.

3. Pressure booster device according to claim 1 or 2, wherein the working section and the pumping section are parallel; and / or the working cylinder and the pumping cylinder are parallel.

4. Pressure booster device according to one of the preceding claims, wherein the working section and the pumping section are not arranged in series; and / or the working cylinder and the pumping cylinder are not arranged in series.

5. Pressure booster device according to one of the preceding claims, wherein the pressure booster device is configured for pumping fuel; the working section is configured to use a working medium, preferably air, hydraulic oil, fuel, such as diesel, engine oil or water, at a working pressure of up to 60 MPa during operation; and the pumping section is arranged, in operation, to pump the fuel, preferably liquid ammonia or liquid alcohol, more preferably a methanol-based composition and even more preferably methanol, at a delivery pressure of up to 200 MPa.

6. Pressure booster device according to one of the preceding claims, wherein the pressure booster device has two working pistons and two pump pistons.

7. Pressure booster device according to one of the preceding claims, wherein the total displacement of the working cylinder is arranged radially further outward than the displacement of the pump cylinder; and / or the displacement of the working cylinder is annular and arranged concentrically around the displacement of the pump cylinder, wherein the displacement of the pump cylinder is preferably cylindrical.

8. Pressure booster device according to one of the preceding claims, wherein the working section comprises an annular working cylinder and an annular working piston and is arranged concentrically around the pumping section; or the working section comprises at least two working cylinders and associated working pistons and is arranged concentrically around the pumping section.

9. Pressure booster device according to one of the preceding claims, wherein the pump piston comprises two opposite piston rods, each of which is coupled to piston rods of the working piston or pistons via connecting elements, preferably connecting plates.

10. Pressure booster device according to claim 9, wherein the annular working piston is provided with one, two, four or five, but preferably three piston rods on opposite axial sides and the connecting plates are round or polygonal, preferably triangular; and More preferably, the three piston rods are arranged offset by approximately 120 degrees in the circumferential direction of the piston and are coupled to the triangular connecting plates; and more preferably, the two arrangements of the three piston rods on the opposite axial sides of the working piston are offset by 60 degrees or 180 degrees in the circumferential direction relative to each other.

11. Pressure booster device according to one of claims 1 to 6, wherein the working piston is pot-shaped and movable; the pump piston is tubular and rigid; and the working piston and the pump piston are arranged such that an interior of the working piston forms the pump cylinder; and / or the pump piston is at least partially inserted into the working piston and the working piston is movable back and forth on the pump piston.

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