Pressure intensifier device

Abstract

The invention relates to a pressure intensifier having a working portion and a pumping portion. The working portion comprises at least one assembly of a working cylinder and a working piston. The pumping portion comprises at least one assembly of a pumping cylinder and a pumping piston. The stroke of the working portion and the stroke of the pumping portion at least partially overlap each other. Additionally or alternatively, the displacement of the working cylinder is arranged at least partially more radially outward compared to the displacement of the pumping cylinder.

Description

[0001] This invention relates to a pressure enhancement device.

[0002] An example of a pressure boosting device is a pressure boosting pump. A more specific example of a pressure boosting device is a pressure boosting pump used for fuel.

[0003] Example fuels according to this disclosure may be liquid alcohols or liquid ammonia. For example, methanol or ethanol can be used as liquid alcohols as fuel in internal combustion engines. Fuels of interest herein generally include so-called Power-to-X fuels. “Power-to-X” is a collective term for various technologies used to store or otherwise utilize surplus electricity during (future) surpluses of variable renewable energy sources—such as solar, wind, and hydropower. In addition to the particularly preferred fuels mentioned—methanol, ethanol, or ammonia—hydrogen, methane, and syngas (a mixture of hydrogen and carbon monoxide) are also considered Power-to-X fuels herein, but this list is not exhaustive (collectively referred to as “fuels” below). The advantage of such fuels compared to diesel or gasoline, which are representative of conventional fuels, is that they are more environmentally friendly in both production and combustion. The disadvantage of fuels such as alcohols or ammonia is that they are difficult to pressurize to the high pressures required for combustion.

[0004] Fuels such as alcohols and ammonia are often used in combination with diesel fuel in so-called dual-fuel engines. These engines are typically relatively large internal combustion engines, used in things like ships or power plants.

[0005] Known pumps for alcohols (such as methanol or ethanol) or ammonia are industrial units. In other words, such pumps are electrically driven and typically have dimensions in the range of 2 × 1.5 × 1.5 meters, weigh about a ton or more, and are very expensive. These pumps operate at very low speeds (i.e., well below 1000 rpm).

[0006] In contrast, known pumps used to generate high-pressure diesel injection are small or compact and operate at significantly higher speeds. Due to differences in material properties (e.g., evaporation at low temperatures, high sensitivity to cavitation, poor lubrication, toxicity), it is not simply possible to repurpose diesel pumps to generate high pressure using fuels such as alcohols and ammonia.

[0007] Therefore, there is a need for high-pressure fuel pumps for fuels such as alcohols and ammonia (or Power-to-X fuels in general), which are small, compact, lightweight, cost-effective, and / or operate at high speeds. At the same time, the operational safety, reliability, and durability of the pumps should be maintained or improved.

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

[0009] According to the present invention, a pressure boosting device (e.g., a pressure boosting pump) for fuel—such as Power-to-X fuel—is proposed as a technical solution to the above-mentioned needs.

[0010] In traditional pressure boosting pumps, the force-generating piston and the high-pressure-generating piston are arranged in series, that is, sequentially. Figure 11 The structure of this pump is schematically shown. The conventional pressure enhancement device 1 includes a low-pressure section or working section 2 consisting of a low-pressure cylinder or working cylinder 3 and a low-pressure piston or working piston 4, and a high-pressure section or pumping section 5 consisting of a high-pressure cylinder or pumping cylinder 6 and a high-pressure piston or pumping piston 7.

[0011] For pulsed operation, the pumping section 5 can consist of an assembly of exactly one pumping cylinder 6 and one pumping piston 7. If continuous operation of the pressure enhancement device 1 is desired, the pumping section 5 can, for example, consist of an assembly of two pumping cylinders 6 and two pumping pistons 7, such as... Figure 11 As shown.

[0012] The working medium is supplied to the working section 2 via valve 8. The working medium is then discharged from the working section 2 via valve 8. Figure 11 In the middle, the valve 8 of the working part 2 is arranged on the surface of the housing of the working cylinder 3.

[0013] The medium to be pumped (the transport medium, such as fuel) is supplied to the pumping section 5 via valve 9. The transport medium is then discharged from the pumping section 5 at the desired high pressure via valve 9. Figure 11 In the middle, the valve 9 of the pumping section 5 is arranged on the end face of the pumping cylinder 6.

[0014] Figure 11The conventional pressure-enhancing device 1 shown operates as follows: two chambers on opposite sides of the working piston 4 are alternately filled with a pressurized working medium. The working medium is subjected to a pressure lower than the desired high pressure to be achieved by the delivery medium. The pressurized working medium then presses against the working piston 4 and displaces it toward the opposing pumping cylinder 6. The pumping piston 7 is ideally rigidly connected to the working piston 4, for example, via a rod. This means that substantially the same force acts on the pumping piston 7 as on the working piston 4. However, because the pumping piston 7 is smaller than the working piston 4, the consistent force applied to the smaller pumping piston generates a higher pressure on the delivery medium that has already flowed into the chamber of the pumping cylinder 6 via valve 9. The delivery medium is discharged from the chamber of the pumping cylinder 6 at the desired high pressure via valve 9. The pressure ratio corresponds to the inverse ratio of the piston areas of the working piston 4 and the pumping piston 7. If the delivery medium flows out of the pumping cylinder 6, the other chamber of the working cylinder 3 is filled with the working medium, and the process restarts in the opposite direction.

[0015] In this way, the transported medium can be targeted to achieve the desired pressure without pressurizing the entire system to the corresponding high pressure. This is advantageous in terms of cost and structure (e.g., size and weight, as well as the complexity of the device).

[0016] Figure 11 The drawback of the conventional design illustrated is that the working section 2 and the pumping section 5 are arranged side-by-side or sequentially, i.e., in series. This results in a relatively large structure.

[0017] The object of this invention is to provide an improved pressure enhancement device. For example, the invention aims to provide a compact and / or cost-effective and / or portable pressure enhancement device. Furthermore, the pressure enhancement device can ensure safer operation of systems equipped with it.

[0018] The pressure-enhancing device according to the invention is the subject of claim 1. Other advantageous improvements of the invention are the subject of the dependent claims.

[0019] By employing a "nested" arrangement of a force-generating working piston and a pressure-generating pumping piston, the present invention creates a significantly more compact structure than a series arrangement. This structure offers particular advantages for mobile applications.

[0020] The pressure-enhancing device of the present invention has a working part and a pumping part. The working part generates force. The pumping part generates pressure. The working part includes at least one assembly of a working cylinder and a working piston. The pumping part includes at least one assembly of a pumping cylinder and a pumping piston.

[0021] According to the invention, the strokes of the working portion and the pumping portion at least partially overlap each other. Preferably, they may also (almost) completely overlap each other. In this context, "stroke" refers to the complete path of the corresponding piston between the two dead centers in its corresponding cylinder. In this context, "overlap" refers to the arrangement of the strokes of the working portion and the pumping portion parallel to the longitudinal direction of the pressure-enhancing device (stroke direction, i.e., the direction of the stroke), unless explicitly mentioned in the radial direction or a direction perpendicular to the longitudinal axis. In other words, "overlap" here means that the total length of the two portions (working portion and pumping portion) in the longitudinal direction of the pressure-enhancing device is shorter than the sum of the lengths of the working portion and the pumping portion in the longitudinal direction of the pressure-enhancing device. Therefore, the pressure-enhancing device according to the invention can also be constructed more compactly, and is therefore particularly advantageous for mobile applications. Here, the displacement portion of the working cylinder may be arranged at least partially radially outward compared to the displacement portion of the pumping cylinder, or the displacement portion of the pumping cylinder may be arranged at least partially radially outward compared to the displacement portion of the working cylinder. In this context, "radial" refers to the radial direction of the pressure enhancement device, which is perpendicular to the longitudinal direction of the pressure enhancement device.

[0022] According to the invention, as an alternative or supplement to the two partially overlapping components, the displacement portion of the working cylinder is arranged at least partially radially outward compared to the displacement portion of the pumping cylinder. In this context, "displacement portion" refers to the enclosed volume swept by the piston during one stroke. Therefore, the displacement portion is the space (stroke volume) enclosed by the assembly of the respective cylinder and piston between the two dead centers of the piston. According to the invention, the displacement portion of the working cylinder may partially or completely overlap with the displacement portion of the pumping cylinder in the radial direction of the pressure enhancing device. However, the displacement portion of the working cylinder may also be arranged so as not to overlap with the displacement portion of the pumping cylinder, and is arranged completely radially outward compared to the displacement portion of the pumping cylinder.

[0023] Preferably, the working section and the pumping section are parallel. This means that they extend at least partially side-by-side along the longitudinal direction of the pressure-enhancing device, or that they are arranged such that one section is positioned further outward than the other in the radial direction of the pressure-enhancing device. Alternatively or additionally, the working cylinder of the working section and the pumping cylinder of the pumping section are parallel only.

[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 as a supplement to or alternative to a parallel arrangement of the two sections. In other words, it is conceivable to arrange the working section and the pumping section in series, where they do not need to extend parallel to each other simultaneously. 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 boosting device is configured to pump fuel as the delivery medium. The fuel is preferably Power-to-X fuel as described above.

[0027] Preferably, the working part is configured to use a working medium with a working pressure of up to 60 MPa during operation of the pressure boosting device.

[0028] In this context, "working pressure" refers to the pressure present in the working section area during steady-state operation of the pressure enhancement device.

[0029] Preferably, the pumping section is configured to pump fuel (as a transport medium) at a supply pressure of up to 200 MPa during operation of the pressure boosting device. Here, the fuel is preferably liquid ammonia or liquid alcohol (during operation). More preferably, the fuel is a methanol-based composition. Methanol is particularly preferred as the fuel.

[0030] In this context, "supply pressure" refers to the pressure at which the delivery medium is discharged from the pumping section during steady-state operation of the pressure boosting device.

[0031] Generally speaking, the term "operation" as used in this article refers to the intended use of a pressure boosting device, which is used to pressurize a conveyed medium to a high pressure using a working medium.

[0032] Preferably, the pressure boosting device has two working pistons and two pumping pistons. This ensures continuous operation of the pressure boosting device on both the inlet and outlet sides, i.e., the inlet and outlet sides of the working medium and the delivery medium. This can, for example, help improve fuel injection, thereby achieving better (e.g., more efficient and / or lower emission) combustion. Furthermore, continuous operation prevents pressure fluctuations, which has a positive impact, for example, on the service life of the pressure boosting device and related components.

[0033] As described above, the entire displacement section of the working cylinder can be arranged radially outward compared to the displacement section of the pumping cylinder. Additionally or alternatively, the displacement section of the working cylinder can be formed as an annular shape. The annular displacement section of the working cylinder can preferably be arranged concentrically around the displacement section of the pumping cylinder. In this case, the displacement section of the pumping cylinder can preferably be cylindrical. However, it is also conceivable to arrange the (annular) displacement section of the working cylinder radially inward compared to the displacement section of the pumping cylinder. These displacement sections or working parts and pumping parts, arranged parallel to the longitudinal direction of the pressure enhancing device, create a compact structure for the pressure enhancing device.

[0034] Preferably, the working section includes an annular working cylinder and an annular working piston. Here, the working section is arranged concentrically around the pumping section. Alternatively, the working section includes at least two working cylinders and associated working pistons. Here, the working section is also arranged concentrically around the pumping section. This structure of the pressure enhancing device is also particularly compact.

[0035] Preferably, the pumping piston comprises two opposing piston rods. Each piston rod of the pumping piston is connected to the piston rod of one or more working pistons via a connecting element. For example, a connecting plate can be used as the connecting element. The connecting plate can, for example, have a triangular shape. This configuration is both compact and allows the pressure-enhancing device to operate continuously.

[0036] Even more preferably, the annular working piston has three piston rods on opposite sides relative to the longitudinal direction of the pressure-enhancing device. With three piston rods on each side of the working piston, the connecting plate is preferably triangular in shape. It is also preferred that the corresponding three piston rods are arranged offset by approximately 120 degrees in the circumferential direction of the piston or pressure-enhancing device. This structure ensures the structural strength of the pressure-enhancing device while minimizing its complexity, size, and mass. In particular, this structure counteracts, for example, torsional stresses in the piston rods. Even more preferably, two of the arrangements of the corresponding three piston rods on opposite axial sides of the working piston are offset or rotated relative to each other by 60 degrees or 180 degrees in the circumferential direction of the piston or pressure-enhancing device. This arrangement ensures a particularly compact structure while still achieving the desired structural strength of the pressure-enhancing device.

[0037] Preferably, the working piston is configured as a pot and is movable. The pumping piston is configured as a tube and is rigid. Here, the working piston and the pumping piston are arranged such that a pumping cylinder is formed inside the working piston. In other words, the working piston and the pumping cylinder are realized or formed by the same component of the pressure enhancing device, which may be, for example, pot-shaped, and movable relative to the fixed pumping piston within the working cylinder. Alternatively or additionally, the pumping piston is at least partially inserted into the working piston. Here, the working piston can move back and forth on the pumping piston in the longitudinal direction of the pressure enhancing device. This structure makes the pressure enhancing device more compact. Depending on whether the working piston or the pumping cylinder is considered, a component can be omitted.

[0038] Although the invention is not limited thereto, in general, these two structures of the pressure enhancement device according to the invention are particularly preferred: a structure having an annular working piston (more preferably arranged radially outside the pumping cylinder), and a structure having a pot-shaped working piston (or pumping cylinder).

[0039] In the pressure boosting device described herein, the pressure and flow rate of the delivery medium (e.g., fuel, particularly Power-to-X fuel) are 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 exemplary area ratio could be 4:1. The supply rate of the delivery medium can be controlled via the speed or number of strokes of the pressure boosting device (pressure boosting pump) per unit time.

[0040] Fuel injection systems equipped with the pressure enhancement device according to the invention (particularly for, but not limited to, Power-to-X fuels) do not require safety valves to prevent overpressure because the piston simply stops when unwanted high pressure occurs in the injection system. This improves the operational safety of the fuel injection system. Furthermore, since safety valves, which would be necessary in other situations, are no longer required, the complexity, cost, and size of the fuel injection system are reduced.

[0041] In the pressure enhancing device according to the invention, the ratio of pumping pressure (pressure of the discharged pumping medium) to working pressure (pressure of the input working medium) during operation of the pressure enhancing device is preferably in the range of greater than 1 to 8, preferably 2 to 8, even more preferably 3 to 7, and particularly preferably 4 to 6.

[0042] In the pressure enhancement device according to the invention, the operating pressure during operation is preferably in the range of 10 MPa to 60 MPa, more preferably 20 MPa to 50 MPa, and particularly preferably 20 MPa to 40 MPa.

[0043] In the pressure enhancement device according to the invention, the pumping pressure during operation is preferably in the range of 30 MPa to 200 MPa, more preferably 50 MPa to 100 MPa, and particularly preferably 60 MPa to 80 MPa.

[0044] The achievable pumping pressure is directly related to the area ratio of the working piston to the pumping piston (e.g., 4:1). The supply of the pumping medium (e.g., Power-to-X fuel) can be controlled by the speed or number of strokes of the device (e.g., the pump) per unit time.

[0045] Although this disclosure primarily describes a pressure-enhancing device, it also relates to using a pressure-enhancing device to transfer a lower pressure of a working medium to a delivery medium, thereby increasing the pressure of the delivery medium to be greater than that of the working medium; that is, it relates to using a pressure-enhancing device for pressure enhancement. Similarly, this disclosure also relates to a pressure-enhancing method, the steps of which correspond to the operation of the pressure-enhancing device according to the invention. Furthermore, this disclosure also relates to systems including the pressure-enhancing device according to the invention, such as fuel injection systems.

[0046] The features and embodiments of the pressure enhancement device described herein can be combined with each other in any way, provided that the resulting combination is technically feasible or produces at least one of the advantageous effects described herein. In particular, features of the preferred embodiments described below can be extracted from various embodiments and incorporated into other embodiments.

[0047] Embodiments of the present invention are described in detail below.

[0048] Figure 1 This is a side cross-sectional view along the longitudinal axis of an embodiment of the pressure enhancement device disclosed herein.

[0049] Figure 2 yes Figure 1 A perspective view of the pressure enhancement device shown.

[0050] Figure 3 It is along the longitudinal axis of the pressure enhancement device. Figure 1 A perspective cross-sectional view of a portion of the pressure-enhancing device shown.

[0051] Figure 4 It is perpendicular to the longitudinal axis of the pressure enhancement device. Figure 1 A perspective cross-sectional view of a portion of the pressure-enhancing device shown.

[0052] Figure 5 It is along the longitudinal axis of the pressure enhancement device. Figure 1 A cross-sectional view of a portion of the pressure enhancement device shown.

[0053] Figure 6 It is perpendicular to the longitudinal axis of the pressure enhancement device. Figure 1 A cross-sectional view of a portion of the pressure enhancement device shown.

[0054] Figure 7 This is a side cross-sectional view along the longitudinal axis of another embodiment of the pressure enhancement device disclosed herein.

[0055] Figure 8 yes Figure 7 A perspective view of the pressure-enhancing device shown.

[0056] Figure 9 It is along the longitudinal axis of the pressure enhancement device. Figure 7 The pressure enhancement device shown is a perspective cross-sectional view.

[0057] Figure 10 It is along the longitudinal axis of the pressure enhancement device. Figure 7 A cross-sectional view of a portion of the pressure enhancement device shown.

[0058] Figure 11 This is a schematic diagram of a traditional pressure boosting pump.

[0059] The following description is specifically for two structural configurations of the pressure enhancement device according to the present invention. Figures 1 to 6 The (first) embodiment or structural configuration shown has an annular working piston arranged radially outward of the pumping cylinder. Figures 7 to 10 The (second) embodiment or structural configuration shown has a pot-shaped working piston or pumping cylinder.

[0060] First, the description Figures 1 to 6 The example shown.

[0061] Figure 1 and Figure 3 A pressure boosting pump 10 is shown as an example of a pressure boosting device. The pressure boosting pump 10 includes a working section 30 and a pumping section 50. In addition, the pressure boosting pump 10 includes a first end plate 11 and a second end plate 12, as well as two connecting plates 13.

[0062] The pressure boosting pump 10 of the first embodiment is particularly characterized in that the working part 30 and the pumping part 50 are arranged concentrically and are parallel to the longitudinal axis of the pressure boosting pump 10.

[0063] Here, the working part 30 is arranged completely outside the pumping part 50 in the radial direction of the pressure boosting pump 10. In other words, the working part 30 and the pumping part 50 do not overlap each other in the direction perpendicular to the longitudinal axis of the pressure boosting pump 10.

[0064] The working part 30 and the pumping part 50 substantially overlap each other relative to or along the longitudinal axis of the pressure boosting pump 10.

[0065] The working part 30 completely surrounds the pumping part 50 located radially inside the pressure boosting pump 10 in the circumferential direction.

[0066] The working part 30 includes an assembly of a working cylinder 31 and a working piston 32. Furthermore, the working part 30 includes a displacement section (displacement volume) 33 and at least one piston rod (working piston rod) 34.

[0067] The displacement portion 33 of the working section 30 is defined or limited by the radial inner surface of the working cylinder 31, the working piston 32, the radial outer surface of the pumping cylinder 51, and the axial inner surfaces of the first end plate 11 and the second end plate 12. In other words, the displacement portion 33 of the working section 30 is arranged annularly around the pumping cylinder 51 of the pumping section 50 or around the pumping section 50. In this embodiment, the displacement portion 33 completely surrounds the pumping cylinder 51 in the circumferential directions of the pressure-enhancing pump 10, the working section 30, and the pumping section 50, respectively.

[0068] The displacement section 33 is divided into two chambers by the working piston 32. These two chambers are located on opposite sides of the working piston 32 in the longitudinal direction of the pressure boosting pump 10, the working section 30, and the pumping section 50.

[0069] like Figure 1 and Figure 3 As can be seen, the working piston 32 has a two-part structure, in which three of the six piston rods 34 are inserted into one of the two parts of the working piston 32 from one side in the longitudinal direction of the pressure boosting pump 10, while the other three piston rods 34 are inserted into the other part of the two parts of the working piston 32 from the opposite side in the longitudinal direction of the pressure boosting pump 10. This two-part structure of the working piston 32 simplifies the assembly of the working part 30, especially considering the large number of piston rods 34 to be inserted. Therefore, three piston rods 34 can be inserted into the working cylinder 31 or the displacement section 33 from one axial end of the pressure boosting pump 10, while the other three piston rods 34 can be inserted into the working cylinder 31 or the displacement section 33 from the opposite axial end of the pressure boosting pump 10.

[0070] It should be understood that the total number of piston rods 34 may be less than or more than six. Similarly, the distribution of piston rods 34 on both sides of the working piston 32 does not need to be equal. For example, two piston rods 34 may be arranged on one side of the working piston 32, and three piston rods 34 may be arranged on the opposite side of the working piston 32.

[0071] It should also be understood that the working piston 32 can be formed as a single piece. This may, for example, make the assembly of the working part 30 more difficult, but may provide advantages in terms of the strength or service life of the working piston 32, or in terms of the seal between the two chambers of the displacement part 33. A multi-part structure of the working piston 32, i.e., a structure consisting of more than two parts, may also be considered if, for example, it is advantageous in terms of assembly.

[0072] An exemplary process for assembling the working part 30 may involve: inserting the corresponding piston rod 34 into the through hole 17 in the associated end plates 11, 12 (see...). Figure 4 and Figure 6 Then, it is inserted into the corresponding opening in the working piston 32. Then, with the two parts of the working piston 32 configured, the working piston 32 can be inserted into the working cylinder 31 or the displacement section 33. Subsequently or simultaneously, the corresponding end plates 11, 12 can be installed onto the corresponding axial ends of the pressure boosting pump 10 or the working cylinder 31. Before or after this step, the connecting plate 13 can be installed on the piston rod 34 by inserting and fixing the end of the piston rod 34, which is opposite to the working piston 32 in the longitudinal direction, into the through hole of the connecting plate 13. The piston rod 34 can also be permanently installed on the connecting plate 13, for example, by welding. In this case, it is not necessary to provide a through hole in the connecting plate 13. The assembly process is repeated accordingly on the opposite side in the longitudinal direction of the pressure boosting pump 10.

[0073] and Figure 1 and Figure 3 Unlike the previous arrangement, it is also conceivable that the working part 30 is formed such that it does not completely surround the pumping part 50 in the circumferential direction of the pressure boosting pump 10, or only partially surrounds the pumping part. Similarly, it is conceivable that the working part 30 and the pumping part 50 are arranged parallel to each other, such that neither part surrounds the other, that is, the two parts overlap each other only in the longitudinal direction of the pressure boosting pump 10, but do not overlap each other in the radial direction of the pressure boosting pump 10.

[0074] The pumping section 50 includes an assembly of a pumping cylinder 51 and a pumping piston 52. Furthermore, the pumping section here includes a displacement section (pumping displacement section) 53 and at least one piston rod (pumping piston rod) 54.

[0075] The displacement portion 53 of the pumping section 50 is defined or limited by the radial inner surface of the pumping cylinder 51, the pumping piston 52, and the axial inner surfaces of the first end plate 11 and the second end plate 12. In other words, the displacement portion 53 of the pumping section 50 is formed in a cylindrical shape within the pumping cylinder 51. Here, the pumping cylinder 51 is completely surrounded by the displacement portion 33 of the working section 30 in the circumferential directions of the pressure-enhancing pump 10, the working section 30, and the pumping section 50, respectively.

[0076] The displacement section 53 is divided into two chambers by the pumping piston 52. These two chambers are located on opposite sides of the pumping piston 52 in the longitudinal direction of the pressure boosting pump 10, the working section 30, and the pumping section 50, respectively.

[0077] like Figure 1 and Figure 3 As can be seen, the pumping piston 52 is constructed as a single piece, wherein one of the two piston rods 54 is inserted into one of the two parts of the pumping piston 52 from one side in the longitudinal direction of the pressure-enhancing pump 10, while the other piston rod 54 is inserted into the pumping piston 52 from the opposite side in the longitudinal direction of the pressure-enhancing pump 10. Since the pumping section 50 in this case only includes two piston rods 54, assembly is relatively simple even though the pumping piston 52 is constructed as a single piece. The single-piece structure of the pumping piston 52 provides advantages in terms of the strength and service life of the pumping piston 52, as well as in terms of sealing between the two chambers of the displacement section 53.

[0078] It goes without saying that the total number of piston rods 54 can be less than or more than two. Similarly, the distribution of piston rods 54 on both sides of the pumping piston 52 does not have to be equal. For example, two piston rods 54 can be arranged on one side of the pumping piston 52, and one piston rod 54 can be arranged on the opposite side of the pumping piston 52.

[0079] It should also be understood that the pumping piston 52 can also be formed as two or more parts. This can, for example, facilitate the assembly of the pumping section 50, as described above in conjunction with the assembly of the working section 30.

[0080] An exemplary process for assembling the pumping section 50 may involve inserting the corresponding piston rod 54 into the through hole 18 in the associated end plates 11, 12 (see...). Figure 4 and Figure 6 Then, it is inserted into the corresponding opening in the pumping piston 52. The pumping piston 52 can then be inserted into the pumping cylinder 51 or the displacement section 53. Subsequently or simultaneously, the corresponding end plates 11, 12 can be installed on the corresponding axial ends of the pressure boosting pump 10 or the pumping cylinder 51. The connecting plate 13 can be installed on the piston rod 54 before or after this step by inserting and fixing the end of the piston rod 54 into the through hole of the connecting plate 13, the aforementioned end of the piston rod being opposite to the pumping piston 52 in the longitudinal direction. The piston rod 54 can also be permanently installed on the connecting plate 13, for example by welding. In this case, it is not necessary to provide a through hole in the connecting plate 13. The assembly process is repeated accordingly on the opposite side in the longitudinal direction of the pressure boosting pump 10, wherein another piston rod 54 is first inserted into the pumping piston 52 in the pumping cylinder 51 or the displacement section 53. For the single-piece design of the working piston 32, the assembly of the working part 30 is performed similarly.

[0081] exist Figure 1 and Figure 3 In the example shown, piston rods 34 and 54 are detachably mounted to connecting plate 13 via a threaded connection. Other detachable connections are also conceivable, such as those via mortise and tenon joints. Similarly, other (permanent) connections besides welding are conceivable, such as those via shrink fitting. It is also conceivable to use additive manufacturing processes to integrally manufacture connecting plate 13 with piston rods 34 and 54.

[0082] Figure 2 A perspective view of the pressure boosting pump 10 according to the present invention is shown, wherein end plates 11, 12 are only schematically illustrated. Furthermore, in Figure 2 In the middle, end piece 14 is shown exemplarily on the left end plate 11.

[0083] End plates 11 and 12 are preferably single-piece components and include flow channels formed by machining processes such as drilling. End plates 11 and 12, including the flow channels formed therein, can also be integrally manufactured using additive manufacturing processes. It is also conceivable that end plates 11 and 12 are not single-piece components, but merely housings in which flexible or fixed conduits are incorporated.

[0084] In this embodiment, end plates 11 and 12 each include a working medium inlet / outlet (working medium port) 15, and a pumping medium inlet 16 and a pumping medium outlet 16 (pumping medium port 16). The pumping medium inlet 16 and the pumping medium outlet 16 can be interchanged depending on whether they are connected to a downstream or upstream device. Although the working medium port 15 is a combined inlet and outlet for the working medium, it can also be implemented via two ports if, for example, a corresponding check valve is provided in the end plates 11 and 12.

[0085] The working medium flows through the working medium port 15, passes through the corresponding end plates 11 and 12, enters the displacement section 33, and then flows out again. The pumping medium flows through the pumping medium port 16, passes through the corresponding end plates 11 and 12, enters the displacement section 53, and then flows out again.

[0086] Each port 15, 16 is connected to the downstream device and the upstream device respectively via a terminal 14. In the first embodiment, six terminal 14s are provided accordingly, one of which is in Figure 2 As exemplarily shown in the figure.

[0087] Figure 4 and Figure 6 The end plate 11 is shown in a cross-section perpendicular to the longitudinal axis of the pressure boosting pump 10. Two end pieces 14 mounted on the pumping medium port 16 are visible. Furthermore, channels are visible that fluidly connect the end pieces 14 and the pumping medium port 16 to the displacement section 53, through which the pumping medium enters and exits the displacement section 53.

[0088] also, Figure 4 and Figure 6 The working medium port 15 without associated end fittings is shown. Channels connecting the working medium port 15 and associated end fittings to the displacement section 33 are also visible, through which the working medium enters and exits the displacement section 33.

[0089] Figure 4 and Figure 6 Further shown, the through-hole 18 for piston rod 54 is centrally located, while the through-hole 17 for piston rod 34 is radially arranged outwards, surrounding the through-hole 18. The through-holes 17 are respectively offset from each other by 120 degrees in the circumferential direction of the pressure-enhancing pump 10 or the end plate 11. The distance between the through-holes 17 and 18 is the same in each case. This results in a symmetrical arrangement. However, an asymmetrical arrangement of the through-holes 17 and 18 is also conceivable.

[0090] End plate 12 can be constructed in the same manner as end plate 11, for example, but this is not necessary. End plate 12 can be arranged in the pressure boosting pump 10 to be offset relative to end plate 11 or rotated 180 degrees (about the longitudinal axis of the pressure boosting pump 10). This arrangement will correspond to... Figure 6 The pump is shown in an inverted view. However, the end plate 12 can also be arranged, for example, to be offset relative to the end plate 11 or rotated by 60 degrees (about the longitudinal axis of the pressure-enhancing pump 10). Figure 4 and Figure 6 The pumping medium port 16, together with the end piece 14 and the working medium port 15 shown may need to be slightly offset.

[0091] The identical configuration of end plates 11 and 12 enables cost savings in the manufacture, assembly, maintenance, and logistics of the pressure boosting pump 10.

[0092] exist Figure 4 and Figure 6 The end piece 14 shown on the left is used as the inlet end piece 14 of the pumping medium in this embodiment, while the end piece 14 shown on the right is used as the outlet end piece 14 of the pumping medium in this embodiment.

[0093] Figure 5 A cross-sectional view of a portion of the pressure boosting pump 10 along its longitudinal axis is shown. Figure 5 The sealing system of the pressure boosting pump 10 is shown in particular detail. Figure 5 Only the grooves are shown; corresponding, for example, resilient sealing elements—such as sealing rings—can be inserted into these grooves.

[0094] In this case, three seals 21, 22 and 23 are specifically provided to seal the working medium.

[0095] Seal 21 shall prevent the working medium from leaking from the pressure boosting pump 10 or from the displacement section 33 to the outside by sealing between the piston rod 34 and the end plate 11. Seal 22 shall prevent the working medium from leaking from one chamber of the displacement section 33 to another chamber of the displacement section 33 opposite to the working piston 32 by sealing between the working piston 32 and the working cylinder 31. Seal 23 shall prevent the working medium from leaking from the pressure boosting pump 10 or from the displacement section 33 to the outside by sealing between the end plate 11 (or 12) and the working cylinder 31. In this embodiment, seal 23 is arranged on the radially outer side of the end plate 11. Alternatively or additionally, (another) seal may be arranged on the axial end side of the end plate for the same purpose, similar to the case of seal 26.

[0096] In this embodiment, three seals 24, 25 and 26 are specifically provided to seal the pumped medium.

[0097] Seal 24 shall prevent the pumping medium from reaching the outside from the pressure boosting pump 10 or from the displacement section 53 by sealing between the piston rod 54 and the end plate 11. Seal 25 shall prevent the pumping medium from reaching the other chamber of the displacement section 53 opposite to the pumping piston 52 by sealing between the pumping piston 52 and the pumping cylinder 51. Seal 26 shall prevent the pumping medium from reaching the outside or entering the displacement section 33 from the pressure boosting pump 10 or from the displacement section 53 by sealing between the end plate 11 and the pumping cylinder 51. In this embodiment, seal 26 is arranged on the axial end side of the pumping cylinder 51. Alternatively or additionally, (another) seal may be arranged on the radially outer side of the pumping cylinder 51 for the same purpose, similar to the arrangement of seal 23.

[0098] All seals 21 to 26 described herein may include multiple sealing elements, as in the case of seals 21, 22, 24 and 25, or may each include a single sealing element, as in the case of seals 23 and 26.

[0099] The seals 21 to 26 shown are merely exemplary and can be arranged differently. For example, instead of being inserted into end plate 11, seal 21 can also be mounted on piston rod 34. The same applies to seal 24. Similarly, seal 23 can be inserted into working cylinder 31 instead of end plate 11. Seal 26 can also be inserted into end plate 11 instead of pumping cylinder 51. Any combination of the arrangement options for seals 21 to 26 described herein, as well as any additional seals, is contemplated.

[0100] Exemplary technical data for the pressure boosting pump 10 in this embodiment include the following values: - The total length of the pressure boosting pump 10, including the stroke length, is approximately 1050 mm. - Weight of the pressure booster pump 10: 75 kg - Travel length: 250 mm - Working medium consumption per stroke: approximately 2.4 l at 10 MPa (i.e., 12 l / min working medium consumption). - Quantity of medium delivered per stroke: approximately 0.4 l at 60 MPa (i.e., a supply rate of 20 l / min). - Piston speed: approximately 0.5 m / s.

[0101] The values ​​above are provided as examples only. However, they illustrate advantages in size and weight compared to the conventional pumps described at the beginning. The pressure-enhancing pump 10 according to the invention is by no means limited to this combination of values ​​or any single value of these values. Single values ​​or any combination of these values ​​can be implemented in the embodiments disclosed herein.

[0102] Figures 1 to 6 The principle of the first embodiment shown is essentially as follows: an annular working piston 32 or displacement section 33 surrounds a cylindrical pumping piston 52 or displacement section 53. When the chamber of the displacement section 33 is filled with pressurized working medium through the channels in the working medium port 15 and end plate 11 or 12, the (larger) annular working piston 32 moves, thereby driving the (triangular) connecting plate 13 via the (three) piston rods 34. The pumping piston 52 is actuated via the connecting plate 13 and piston rods 54, causing it to move in the same direction as the working piston 32. The pumping medium that has reached the chamber of the displacement section 53 through the channels in the pumping medium port 16 and end plate 11 or 12 is pressurized by the (smaller) pumping piston 52 and discharged from the pressure-enhancing pump 10 under high pressure through the channels in another pumping medium port 16 and end plate 11 or 12. This high pressure is essentially achieved because the area of ​​the annular working piston 32 is larger than the area of ​​the cylindrical pumping piston 52.

[0103] During operation of the pressure boosting pump 10, the working medium is controlled via an external valve (not shown).

[0104] In this way, the compact structure of the pressure boosting pump 10 can pressurize the pumping medium and discharge it from the pressure boosting pump 10 at a pressure (significantly) higher than the pressure of the working medium flowing into the pressure boosting pump 10 (pressure boosting).

[0105] Figures 7 to 10 Another (second) embodiment of the pressure boosting pump 10 according to the present invention is shown. The same components in the second embodiment are indicated by the same reference numerals as in the first embodiment.

[0106] Figure 7 , Figure 8 and Figure 9 A pressure boosting pump 10 is shown as an example of a pressure boosting device. The pressure boosting pump 10 includes a working section 30 and a pumping section 50. In addition, the pressure boosting pump 10 includes a first end plate 61 and a second end plate 62, as well as a connecting plate 63.

[0107] The pressure boosting pump 10 of the second embodiment is particularly characterized by the nested arrangement of the working part 30 and the pumping part 50. In this arrangement, the working piston of the working part 30 and the pumping cylinder of the pumping part 50 are formed by the same component, which is indicated by reference numeral 70, namely the combined working piston-pumping cylinder (hereinafter referred to as the "pot-shaped component") 70.

[0108] Here, the working part 30 is partially arranged outside the pumping part 50 in the radial direction of the pressure boosting pump 10. In other words, the working part 30 and the pumping part 50 partially overlap each other in the direction perpendicular to the longitudinal axis of the pressure boosting pump 10.

[0109] The working portion 30 and the pumping portion 50 partially overlap each other relative to or along the longitudinal axis of the pressure boosting pump 10.

[0110] In this embodiment, the pressure boosting pump 10 includes an arrangement consisting of two (partial) working sections 30 and two (partial) pumping sections 50, which is substantially symmetrical about the connecting plate 63. However, for discontinuous operation, providing only one (partial) working section 30 and one (partial) pumping section 50 is also sufficient. In this case, the structure of the pressure boosting pump 10 will be similar to Figure 10 Part of the pressure boosting pump 10 shown.

[0111] The working part 30 completely surrounds the pumping part 50 located radially inside the pressure boosting pump 10 in the circumferential direction.

[0112] The working part 30 includes an assembly of a working cylinder 31 and a working piston, which is formed by the peripheral wall and end face (particularly the bottom) of the pot-shaped part 70. In addition, the working part 30 includes a displacement section (working displacement section) 33.

[0113] In this embodiment, the two pot-shaped components 70 are connected via at least one rod 71 (see...) Figure 9 Preferably, the two pot-shaped parts 70 are connected to each other in a substantially rigid manner via three rods 71. This ensures a consistent distance between the two pot-shaped parts 70 or at the joint of the two pot-shaped parts 70 in the longitudinal direction of the pressure boosting pump 10.

[0114] The displacement section 33 of the working part 30 is defined or limited by the radial inner surface of the working cylinder 31, the outer surface of the pot-shaped part 70 (especially the outer part of the bottom of the pot-shaped part 70), and the axial inner surfaces of the first end plate 61 and the second end plate 62, respectively. In other words, the displacement section 33 of the working part 30 is cylindrical and is arranged in the longitudinal direction of the pressure-enhancing pump 10 between the pot-shaped part 70 and the first end plate 61, and between the pot-shaped part 70 and the second end plate 62, respectively.

[0115] In this embodiment, the displacement section 33 is divided into two chambers by two pot-shaped members 70 connected by a rod 71. These two chambers are located on opposite sides of the interconnected pot-shaped members 70, either in the longitudinal direction of the pressure-enhancing pump 10 or in the longitudinal direction of the working section 30 or the pumping section 50.

[0116] As previously described, in this embodiment, the axial and radially outer portions of the pot-shaped member 70 correspond to the working piston. The pot-shaped member 70 slides along the radially inner surface of the working cylinder 31, thus forming part of the working section 30 when combined with the working cylinder 31. On the other hand, in this embodiment, the radially inner portion and the inner portion of the bottom of the pot-shaped member 70 correspond to the pumping cylinder. The pot-shaped member 70 slides along the radially outer surface of the fixed pumping piston 52, thus forming part of the pumping section 50 when combined with the pumping piston 52.

[0117] The compact structure of the pressure-enhancing pump 10 can be achieved through the nested structure of the working cylinder 31, the pot-shaped part 70, and the pumping piston 52.

[0118] As previously described, continuous pumping operation is achieved by two pot-shaped components 70 rigidly connected to each other by at least one rod 71. Preferably, as in this embodiment, three rods 71 ​​are used to connect the two pot-shaped components. It should be understood that two or more rods 71 ​​may also be used.

[0119] The pumping section 50 includes an assembly of a movable pumping cylinder formed on the inner side of the pot-shaped member 70 and a rigid, fixed pumping piston 52. Furthermore, the pumping section 50 includes a displacement section (pumping displacement section) 53.

[0120] The displacement portion 53 of the pumping section 50 is defined or limited by the radial inner surface of the pot-shaped member 70 and the inner side of the bottom of the pot-shaped member 70 (i.e., by the pot-shaped interior of the pot-shaped member 70), and by the pumping piston 52 (more precisely, by the axial end face of the pumping piston 52). In other words, the displacement portion 53 of the pumping section 50 is formed into a cylindrical shape within the pot-shaped member 70.

[0121] In this embodiment, the displacement section 53 is divided into two chambers, which are respectively formed in one of the two pot-shaped parts 70.

[0122] As previously described, in this embodiment, the two (partial) working portions 30 and the two (partial) pumping portions 50 are arranged substantially symmetrically about a connecting plate 63 that is substantially centrally located, and are detachably mounted to the connecting plate 63 via flanges 64. Here, threaded bolts are used to achieve the detachable connection, such as... Figure 8 As shown, the connecting plate 63 is omitted and is only illustrated to illustrate the internal structure of the pressure boosting pump 10. It should be understood that other detachable connections, such as clamps, may also be used. Permanent connections, such as welding, may also be used to connect the various components of the pressure boosting pump 10.

[0123] An exemplary assembly sequence for the pressure-enhancing pump 10 of the second embodiment may be to first connect a rigid pumping piston 52 to a connecting plate 63. This may be done, for example, by a threaded connection, wherein the pumping piston 52 is screwed into the connecting plate 63. Next, a movable pot-shaped member 70 may be mounted on or slide over the pumping piston 52. Subsequently, a working cylinder 31 may be mounted on or slide over the pot-shaped member 70. A flange 64 may be permanently connected to the working cylinder 31, for example. This connection may be made, for example, by welding or cold shrink fitting. A detachable connection using threaded connections or tongue and groove joints is also conceivable. Alternatively, the working cylinder 31 may, for example, have a radially outwardly projecting protrusion or flange at its axial end facing the connecting plate 63. The annular flange 64 may then be pushed from the axial end of the working cylinder 31 away from the connecting plate 63 toward the connecting plate 63 or the protrusion or flange, and subsequently connected to the connecting plate 63. The two (partial) working parts 30 and the two (partial) pumping parts 50 are connected to each other by connecting flange 64 to connecting plate 63 or by connecting flanges across connecting plate 63. Before this, or if necessary, after this, end plates 61, 62 are mounted on the axial outer ends of the working cylinder 31. Here, detachable or permanent connections are also possible, such as threaded connections, tongue and groove joints, welded connections, or cold shrink fits. It should be understood that the working cylinder 31 can be integrally manufactured with flange 64 and / or end plates 61, 62 using additive manufacturing processes.

[0124] In addition, end piece 14 is installed at the working medium port 15 in end plates 61 and 62, and at the pumping medium port 16 in connecting plate 63 (see...). Figure 10 (location) Figures 7 to 10 In the diagram, only the end piece 14 mounted on the connecting plate 63 is visible, while the end pieces 14 that can be mounted on the end plates 61 and 62 are not shown.

[0125] Figure 8 A perspective view of the pressure boosting pump 10 according to the invention is shown, wherein the connecting plate 63 is shown only schematically. Two end pieces 14 are exemplary shown on the schematic connecting plate 63.

[0126] End plates 61 and 62 are preferably single-piece components and include at least one (through) flow channel formed by a machining process—such as drilling. End plates 61 and 62, including the at least one flow channel formed therein, may also be manufactured using additive manufacturing processes. It is also conceivable that end plates 61 and 62 are not single-piece components, but merely housings with flexible or fixed conduits present therein.

[0127] In this embodiment, end plates 61 and 62 each include a working medium inlet / outlet (working medium port) 15. Although the working medium port 15 is a combined inlet and outlet for the working medium, it can also be implemented via two ports if, for example, a corresponding check valve is provided in end plates 61 and 62.

[0128] The connecting plate 63 includes a pumping medium inlet 16 and a pumping medium outlet 16 (pumping medium port 16). The pumping medium inlet 16 and pumping medium outlet 16 (see...) Figure 10 They can be interchanged depending on whether they are connected to a downstream or upstream device.

[0129] The working medium flows through the corresponding end plates 61 and 62 into the displacement section 33 via the working medium port 15 and then flows out again. The pumping medium flows through the connecting plate 63 into the displacement section 53 via the pumping medium port 16 and then flows out again.

[0130] Each port 15, 16 is connected to the downstream device and the upstream device respectively via terminal 14. In the second embodiment, four terminal 14s are correspondingly provided, two of which are in… Figures 7 to 10 As exemplarily shown in the figure.

[0131] Figure 7 , Figure 9 and Figure 10 End plates 61, 62 and connecting plate 63 are shown in a cross-section along the longitudinal axis of the pressure boosting pump 10. In each figure, two end pieces 14 mounted on the pumping medium port 16 at the connecting plate 63 are visible. Furthermore, channels are visible that fluidly connect the end pieces 14 and the pumping medium port 16 to the displacement section 53 through which the pumping medium enters and exits the displacement section 53.

[0132] also, Figures 7 to 10 The working medium port 15 without associated terminals is shown. Furthermore, in Figure 7 , Figure 9 and Figure 10 As can be seen, the working medium port 15 or the corresponding end piece is fluidly connected to the displacement section 33 through the channels through which the working medium enters and leaves the displacement section 33.

[0133] End plate 62 can be configured, for example, to have the same construction as end plate 61. This configuration of identical construction of end plates 61 and 62 enables cost savings in the manufacture, assembly, maintenance, and logistics of the pressure boosting pump 10.

[0134] exist Figure 7 , Figure 9 and Figure 10In each figure, the end piece 14 shown at the top is used as the inlet end piece 14 of the pumping medium in this embodiment, while the end piece 14 shown at the bottom of each figure is used as the outlet end piece 14 of the pumping medium in this embodiment.

[0135] Figure 10 A cross-sectional view along the longitudinal axis of the pressure boosting pump 10 is shown, depicting a portion of the pressure boosting pump 10. Figure 10 The sealing system of the pressure boosting pump 10 is shown in particular detail. Figure 10 Only the grooves are shown; corresponding, for example, resilient sealing elements—such as sealing rings—can be inserted into these grooves.

[0136] In this case, two seals, 81 and 82, are specifically provided to seal the working medium.

[0137] Seal 81 shall prevent the working medium from reaching the outside from the pressure boosting pump 10 or from the displacement section 33 by sealing between the working cylinder 31 and the end plate 61 or 62. Seal 81 is disposed in the bottom of the pot-shaped end plate 61 or 62, but may also be disposed on the axial end side of the working cylinder 31. Alternatively or additionally, (another) seal may be disposed on the radially outer side of the working cylinder 31 or the radially inner side of the end plate 61 or 62 for the same purpose. Seal 82 shall prevent the working medium from reaching the connecting plate 63 on the axially opposite side of the pot-shaped part 70 or entering the displacement section 53 from the displacement section 33 by sealing between the pot-shaped part 70 and the working cylinder 31.

[0138] Specifically, three seals, 83, 84 and 85, are provided to seal the pumped medium.

[0139] Seal 83 shall prevent pumping medium from entering the connecting plate 63 from the displacement section 53 through the pumping piston 52 by sealing between the pumping piston 52 and the connecting plate 63. Seal 83 may be arranged on the axial end side and / or radially outer side of the pumping piston 52. Seal 83 may also be arranged on the axial end side and / or radially inner side of the connecting plate 63. Combinations of these variations are possible. Seal 84 shall prevent pumping medium from reaching the outside of the pressure-enhancing pump 10 by sealing between the working cylinder 31 and the connecting plate 63. Seal 84 may be arranged on the axial end side and / or radially inner side of the working cylinder 31. Seal 84 may be arranged on the axial end side and / or radially outer side of the connecting plate 63. Combinations of these arrangements are possible. Seal 85 shall prevent pumping medium from entering the connecting plate 63 or the displacement section 33 from the pumping piston 52 through the pumping piston 52 by sealing between the pumping piston 52 and the pot-shaped part 70. The seal 85 can be achieved by selecting an appropriate clearance between the pot-shaped part 70 and the pumping piston 52, or, for example, by a sealing ring (O-ring). In the latter case, the seal 85 can be arranged on the radially inner side of the pot-shaped part 70 and / or the radially outer side of the pumping piston 52.

[0140] All seals 81 to 85 described herein may include multiple sealing elements, as in the case of seal 82, or may each include a single sealing element, as in the cases of seals 81 and 83 to 85.

[0141] Exemplary technical data for the pressure boosting pump 10 in this embodiment include the following values: - Overall length of pressure booster pump 10: approximately 850 mm - Weight of the pressure booster pump 10: 75 kg - Travel length: 130 mm - Working medium consumption per stroke: approximately 1 l at 15 MPa (i.e., 120 l / min working medium consumption). - Quantity of medium conveyed per stroke: approximately 0.25 l at 60 MPa (i.e., a supply rate of 30 l / min). - Piston speed: approximately 0.5 m / s.

[0142] The values ​​described above are merely exemplary. However, they illustrate the size and weight advantages compared to the conventional pumps described at the beginning. The pressure-enhancing pump 10 according to the invention is by no means limited to this combination of values ​​or any single value thereof. Individual values ​​or any combination of these values ​​may be implemented in the embodiments disclosed herein.

[0143] Figures 7 to 10The principle of the second embodiment shown is essentially based on a pot-shaped assembly (pot-shaped component 70) comprising a working piston and a movable pumping cylinder, arranged between the working cylinder 31 and the rigid pumping piston 52. When the chamber of the displacement section 33 is filled with pressurized working medium via the working medium port 15 and the passage in the end plate 61 or 62, the working piston, implemented by the pot-shaped component 70, moves, thereby driving the movable pumping cylinder, implemented by another pot-shaped component 70, via the rod 71. During this process, the movable pumping cylinder slides on the fixed rigid pumping piston 52. The pumping medium that has entered the chamber of the displacement section 53 via the passage in the pumping medium port 16 and the connecting plate 63 is pressurized by the pumping cylinder sliding on the rigid pumping piston 52 and discharged from the pressure-enhancing pump 10 under high pressure via the passage in the other pumping medium port 16 and the connecting plate 63. This high pressure is essentially achieved because the internal area of ​​the bottom of the pot-shaped component 70 is smaller than the external area of ​​the bottom of the pot-shaped component 70.

[0144] The movement of the pot-shaped component 70 (working cylinder) is controlled by the flow of the working medium. During operation of the pressure boosting pump 10, the control of the working medium is performed via an external valve (not shown).

[0145] In this way, the compact structure of the pressure boosting pump 10 can pressurize the pumping medium and discharge it from the pressure boosting pump 10 at a pressure (significantly) higher than the pressure of the working medium flowing into the pressure boosting pump 10 (pressure boosting).

Claims

1. A pressure enhancing device, comprising: The working part includes at least one assembly of a working cylinder and a working piston; and The pumping section includes at least one assembly of a pumping cylinder and a pumping piston; wherein The stroke of the working section and the stroke of the pumping section overlap at least partially with each other, and / or The displacement section of the working cylinder is at least partially arranged further outward in the radial direction compared to the displacement section of the pumping cylinder.

2. The pressure enhancing device according to claim 1, wherein, The stroke of the working section and the stroke of the pumping section substantially overlap with each other.

3. The pressure enhancing 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. The pressure enhancing device according to any 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. The pressure enhancing device according to any one of the preceding claims, wherein, The pressure boosting device is configured to pump fuel; The working section is configured to use a working medium with a maximum working pressure of 60 MPa during operation, preferably air, hydraulic oil, fuel such as diesel, engine oil, or water; and The pumping section is configured to pump the fuel at a supply pressure of up to 200 MPa during operation. The fuel is preferably liquid ammonia or liquid alcohol, more preferably a methanol-based composition, and even more preferably methanol.

6. The pressure enhancing device according to any one of the preceding claims, wherein, The pressure enhancement device has two working pistons and two pumping pistons.

7. The pressure enhancing device according to any one of the preceding claims, wherein, The entire displacement section of the working cylinder is arranged radially outward compared to the displacement section of the pumping cylinder; and / or The displacement section of the working cylinder is formed in an annular shape and is arranged concentrically around the displacement section of the pumping cylinder, wherein the displacement section of the pumping cylinder is preferably cylindrical.

8. The pressure enhancing device according to any one of the preceding claims, wherein, The working part includes an annular working cylinder and an annular working piston, and are arranged concentrically around the pumping part; or The working section includes at least two working cylinders and associated working pistons, arranged concentrically around the pumping section.

9. The pressure enhancing device according to any one of the preceding claims, wherein, The pumping piston includes two opposing piston rods, which are respectively connected to the piston rods of one or more of the working pistons via connecting elements, preferably via connecting plates.

10. The pressure enhancing device according to claim 9, wherein, The annular working piston has one, two, four, or five, but preferably three, piston rods on opposite axial sides, and the connecting plate is circular or polygonal, preferably triangular; and More preferably, the three piston rods are respectively offset by approximately 120 degrees in the circumferential direction of the piston and connected to the triangular connecting plate; and More preferably, two of the piston rods on the opposite axial sides of the working piston, each comprising three corresponding piston rods, are offset from each other by 60 degrees or 180 degrees in the circumferential direction.

11. The pressure enhancing device according to any one of claims 1 to 6, wherein, The working piston is pot-shaped and movable; The pumping piston is tubular and rigid; and The working piston and the pumping piston are arranged such that the interior of the working piston forms the pumping cylinder; and / or The pumping piston is at least partially inserted into the working piston, and the working piston is capable of reciprocating on the pumping piston.

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