EP2156049B1 - Pressure amplifier with integrated pressure reservoir - Google Patents

Description

State of the art

EP 0 711 914 A1 refers to a pressure-controlled fuel injection system in which fuel is compressed by means of a high-pressure pump to a first high fuel pressure of about 1200 and stored in a first pressure accumulator. Furthermore, the high-pressure fuel is also conveyed into a second pressure accumulator, in which by controlling its fuel supply by means of a 2/2-way valve, a second high fuel pressure of about 400 bar is maintained. Via a valve control unit, either the lower or the higher fuel pressure is conducted into the nozzle chamber of an injector. There, a spring-loaded valve body is lifted from its valve seat by the pressure, so that fuel can escape from the nozzle opening into the combustion chamber.

A disadvantage of this known fuel injection system is the fact that first of all the entire fuel must first be compressed to the higher pressure level in order then to relieve some of the fuel back to the lower pressure level. In addition, the high-pressure pump, since it is driven by the camshaft of the engine, permanently in operation, even if the desired pressure in the respective pressure accumulator is already established. This permanent high pressure generation and the subsequent relief to the low pressure level counteract a better efficiency.

The high-pressure fuel pumps used in the field of self-igniting internal combustion engines are currently able to build up pressures of up to about 2200 bar. Exceeding pressures are possible either with two-stage high-pressure pumps or with additional pressure amplifiers outside or inside the fuel injectors. Two-stage high pressure pumps require a much larger space and are therefore not compatible with the current systems. In addition, the mechanical stress on the part of the pump development is classified as critical. Internal and external pressure amplifiers are currently used only as local pressure intensifiers for individual injectors used, ie per injector is a pressure booster in use. This means from the effort initially a large number of additional components and beyond the function of a poor efficiency in pressure-boosted injection small amounts, since for each pressure boosting process, a minimum conversion to control amount in the pressure booster is necessary. Such a central pressure booster is for example off EP 1 125 046 B1 known.

From the DE 199 39 422 A1 In addition, an injection system is known in which fuel is compressed by a central, having only one piston element having pressure booster and fed to a high-pressure accumulator which supplies the injectors.

Disclosure of the invention

According to the invention, a pressure intensifier is proposed, which represents a single separate module, and corresponds approximately to the size of a commonly used pressure accumulator and also assumes its function. In this represents a common high-pressure pump is currently a common pressure level in the order of about 2000 bar, which is referred to below as the medium pressure. The pressure intensifier proposed according to the invention advantageously has at least two pistons for achieving the pressure boost, which are operated alternately and thus a continuous delivery at high pressure, i. at a pressure level of> 2500 bar. The delivered quantity can therefore be made available to the individual NEN fuel injectors even without large high-pressure accumulator, since a pressure drop can be compensated by injector-side removal largely by immediate Nachförderung.

This eliminates the costly separate pressure boost for each provided in the context of a fuel injection system fuel injector so that functionally the significant advantage is achieved that at injection pressures below the maximum pressure of the high-pressure pump, the required amount can be promoted without activation of the pressure booster in the individual fuel injectors. This means just for smaller injected into the combustion chamber of self-igniting internal combustion engines injection quantities a significant increase in hydraulic efficiency, due to the elimination of the previously required pressure intensifier control amount.

Likewise, alternatively, a simplified design of the pressure booster with only one switching valve and pressure booster piston is conceivable in the event that the reset time of the pressure booster piston is sufficiently short for the required engine speed and thus for the activation frequency of the booster. In this case, another gear ratio of the pressure booster may be necessary.

Brief description of the drawings

With reference to the drawing, the invention will be described below in more detail.

Figur 1

eine erste Ausführungsform des erfindungsgemäß vorgeschlagenen Hochdruckeinspritzsystems mit einer Druckverstärkereinheit,

Figur 2

zweite Ausführungsform des erfindungsgemäß vorgeschlagenen Hochdruckeinspritzsystems mit einer Druckverstärkereinheit, in der ein Zwischendruckspeicher und ein Hochdruckspeicher integriert sind,

Figur 3

eine Prinzipskizze der Druckverstärkungseinheit mit zwei Druckverstärkern,

Figur 4

eine weitere Ausführungsform der erfindungsgemäß vorgeschlagenen Druckverstärkereinheit (ohne Hochdruckspeicher),

Figur 5

eine Druckverstärkereinheit (mit integriertem Hochdruckspeicher),

Figur 6

der wechselweise Betrieb der Druckverstärkerkolben bei synchroner Einspritzung,

Figur 7

synchrone Einspritzungen bei synchronem Betrieb der Druckverstärkerkolben,

Figur 8

den wechselweisen Betrieb von Druckverstärkerkolben bei asynchroner Einspritzung,

Figuren 9.1 bis 9.5

Systembilder des erfindungsgemäß vorgeschlagenen Hochdruckspeichereinspritzsystem mit Verrohrungsvarianten.

It shows:

FIG. 1

A first embodiment of the present invention proposed high-pressure injection system with a pressure booster unit,

FIG. 2

second embodiment of the present invention proposed high-pressure injection system with a pressure booster unit in which an intermediate pressure accumulator and a high-pressure accumulator are integrated,

FIG. 3

a schematic diagram of the pressure amplification unit with two pressure amplifiers,

FIG. 4

a further embodiment of the pressure booster unit proposed according to the invention (without high-pressure accumulator),

FIG. 5

a pressure booster unit (with integrated high pressure accumulator),

FIG. 6

the alternating operation of the pressure intensifier pistons with synchronous injection,

FIG. 7

synchronous injections during synchronous operation of the pressure intensifier pistons,

FIG. 8

the alternating operation of pressure intensifier pistons in asynchronous injection,

FIGS. 9.1 to 9.5

System pictures of the inventively proposed high-pressure storage injection system with piping variants.

embodiments

The representation according to FIG. 1 a first embodiment of the high-pressure injection system can be seen. The high-pressure injection system 10 as shown in FIG FIG. 1 In addition to a tank 12, a high-pressure pump 14 is provided. The high-pressure pump acts on a pressure booster unit 16 which, according to this first embodiment, comprises an intermediate rail 18 and an optionally activatable pressure booster 24. The pressure intensifier unit 16 in turn acts on an externally arranged high pressure accumulator 20, which in turn has a number of high pressure ports 26. About the high pressure ports 26, which are provided on the high-pressure accumulator 20 in a number corresponding to the number to be supplied with fuel fuel injectors 22, the in FIG. 1 supplied internal combustion engine, not shown. Via the dashed lines from the fuel injector 22 and from the pressure intensifier unit 16, control or leakage amount is conveyed back to the tank 12 of the high-pressure accumulator injection system 10.

FIG. 2 shows a second embodiment of the present invention proposed high-pressure injection system, in which, in contrast to the representation according to FIG. 1 the pressure booster unit 16 comprises the intermediate rail 18, the optionally activatable pressure booster 24 and the high-pressure accumulator 20 as an integrated component. In this case, the high pressure ports 26 are provided on the pressure booster unit 16 in a number corresponding to the number of fuel injectors 22 to be supplied with fuel. As shown in the illustration FIG. 2 As can be seen, the leakage or control quantity is returned via the lines indicated by dashed lines both from the pressure intensifier unit 16 and from the at least one fuel injector 22 to the tank 12 of the high-pressure accumulator injection system 10.

FIG. 3 shows the schematic structure of the booster, of which two in the in FIGS. 1 and 2 illustrated pressure booster units are installed.

As shown in the illustration FIG. 3 a pressure amplifier 24, of which at least one is installed in a pressure amplification unit 16, comprises a base body 30. In the base body 30 are pressure booster piston 32, 33. The in the Figures 1 and 2 Pressure booster units 16 shown each comprise two pressure boosters 24.

In the main body 30 of the pressure booster piston 32 is arranged, which has a first piston part 34 in a larger diameter and a second piston part 36 in a smaller diameter. On the first pressure piston part 34 is an annular collar 38, on which a return spring 40 is supported. The return spring 40 is further supported on an annular surface of a piston guide body 42.

In the main body 30 of the in FIG. 3 illustrated pressure booster 24 is a high pressure valve 44 and a filling valve 46. These two valves 44, 46 are preferred designed as check valves. The high-pressure valve 44 is located in a storage supply line 54 which communicates with a high-pressure chamber 60. The high-pressure chamber 60 is limited on the one hand by the piston guide body 42 and on the other hand by a high-pressure surface 64.

The filling valve 46 is located in a hydraulic line, which, as shown in FIG FIG. 3 connects a control chamber 62 via a switching valve 50 and a bypass with a storage volume 58. Furthermore, in the main body 30 of the in FIG. 3 illustrated pressure intensifier 24, the switching valve 50 is integrated, which may be formed, for example, operated as a solenoid valve switching valve, as a 3/2-way valve.

From the main body 30 of the pressure booster 24 as shown in FIG FIG. 3 extends on the one hand, a pressure booster 56, which is located downstream of the switching valve 50, the storage supply line 54 with integrated high-pressure valve 44, which is the high-pressure accumulator 20 according to the system overviews in FIGS. 1 and 2 extends as well as a pressure booster inlet 52, via the in the Figures 1 and 2 shown high-pressure pump 14 is acted upon. From the illustration according to FIG. 3 also results that the storage volume 58, which is also referred to as a medium-pressure accumulator, communicates via a bypass 68 with the control chamber 62.

At injection pressures below the maximum delivery pressure of the high-pressure pump 14, a medium pressure designated here by the high pressure pump 14 via the pressure booster inlet 52 in the one or more parts trained storage volume 58 and further promoted via the filling valve 46 and the high pressure valve 44 directly to the storage feed 54. From there it enters either an external high-pressure accumulator 20 - as in FIG. 1 represented - or via the internal high-pressure accumulator - to the fuel injectors 22, as in FIG. 2 shown.

In this case, the pressure booster 24 is operated according to the schematic representation in Figure 3 in the bypass mode in which no pressure boosting is necessary and therefore no appreciable efficiency losses occur. In bypass operation is simultaneously by all available pressure booster 24 a pressure booster unit 16 - as in the Figures 1 and 2 presented - promoted.

When pressure amplification is required, the pressure amplifiers 24 of the pressure booster unit 16 can be used alternately or simultaneously. In each of these cases, the corresponding switching valve 50, which is preferably a 3/2-way valve, is switched. The control space 62 of the pressure intensifier piston 32 becomes due to the activation the switching valve 50 is connected to the pressure booster return 56 and therefore depressurized. Due to this, the pressure in the high-pressure chamber 60 of the pressure intensifier 24 increases until an equilibrium of forces has been established between the high pressure on the high-pressure surface 64 of the high-pressure piston 32 and the force generated by the return spring 40 and the mean pressure at the medium-pressure surface 66 of the pressure intensifier pistons 32, 33 ,

The transmission ratio i defined by the two pressure surfaces 64 and 66 preferably corresponds to the quotient of the desired maximum pressure required at the storage supply line 54 and the high-pressure pump delivery pressure. Thus, the high pressure amount is fed back through the high pressure valve 44 when at the high pressure port, i. in the storage supply line 54, the pressure drops due to quantity removal. About the filling valve 46, the connection to the storage volume 58 is closed.

When deactivating the switching valve 50, the control chamber 62 of the high pressure piston 32 is connected to the storage volume 58, whereby the pressure in the control chamber 62 increases and the pressure booster piston 32, 33 is positioned at hydraulic force balance by the spring force of the return spring 34 at its stop limit 48.

Preferably, the activation of each of a pressure intensifier 24 associated switching valves 50 is synchronized with the injections, so that per cylinder of fuel to be supplied internal combustion engine and each 720 ° crankshaft angle in a four-stroke internal combustion engine, a delivery stroke of the booster 24 takes place. Accordingly, it is ensured that the reset time of each pressure booster piston 32 or 33 of the at least one pressure booster 24 is sufficiently short in order to be able to deliver at every second injection at a pressure booster unit 16 equipped with two pressure booster 24.

The pressure booster unit 16 according to the representations of Figures 1 and 2 In addition to the buffer (Zwischenrail) preferably comprises two pressure booster 24 and optionally - as in the embodiment according to FIG. 2 illustrated - a high-pressure accumulator 20 (high-pressure rail), which is integrated in the pressure booster unit 16.

In the FIGS. 4 and 5 are various embodiments of pressure booster units incorporated in the Figures 1 and 2 are shown only schematically reproduced. The buffer 18 (Zwischenrail) does not necessarily represent a separate component, but is divided into a storage volume 38 (see FIG. 3 ) preferably two built in a pressure booster unit 16 pressure booster 24.

As for example from the illustration according to FIG. 4 As can be seen, the pressure booster unit 16 may comprise a U-shaped central body 94 having storage pots 92, in which the individual pressure booster 24 of the booster unit 16 are embedded. On one end face of the central body 94 is in each case a first switching unit 84 and a second switching unit 86, each formed as a 3/2-way valve 50. Side of the U-shaped central body 94 of the pressure booster unit 16 ports 82 are executed, in which there around the in FIG. 3 represented connections 82, namely pressure booster inlet 52, storage supply line 54 and pressure booster 56 return. At the pressure booster inlet 52, cf. also reference numeral 98, for example, the in FIG. 1 shown high pressure pump 14 connected, see. Position 98 in FIG. 1 , Furthermore, the connections on the 82 U-shaped central body 94 of the pressure booster unit 16 as shown in FIG FIG. 4 , High Pressure Connections 100, for example, to the in FIG. 1 lead described high-pressure accumulator 20 lead.

From the illustration according to FIG. 4 also shows that the two pressure amplifiers 24, of which the pressure booster 24, the pressure booster piston 32 and the pressure booster 24 has the pressure booster piston 33, are arranged parallel to each other. The pressure booster 24 with pressure booster piston 32 is inactive, the other pressure booster 24 with pressure booster piston 33 is active. At the central body 94 of the pressure booster unit 16 is a pressure control valve 102 and a pressure sensor 104. Off FIG. 4 can be further seen that the active of the two pressure booster 24 compressed according to the pressure boosting ratio i fuel via the memory leads 54 and 100 to the in FIG. 1 shown high-pressure accumulator 20 leads. The structure of in the embodiment according to FIG. 4 illustrated pressure amplifier 24 substantially corresponds to the representation of the pressure booster 24 according to FIG. 3 ,

The pressure booster unit 16 in the in FIG. 5 illustrated embodiment also has ports 82, each representing the pressure booster inlet 52 and the memory feed 54. The pressure booster return is not shown.

In the FIGS. 4 and 5 each pressure booster units 16 are shown, which have a reduced overall length, which is achieved due to the formed in a U-shaped one-piece central body 94. Furthermore, in the embodiments according to the FIGS. 4 and 5 Connection possibilities for the pressure sensor 104 or the one shown there schematically Pressure control valve 102 provided on the end face of the integrally formed central body.

While FIG. 4 an embodiment of the first embodiment according to FIG. 1 represents shows FIG. 5 an embodiment of the second embodiment according to FIG. 2 with integrated high pressure accumulator 20.

From the illustration according to FIG. 5 can be seen, for example, that the pressure booster unit 16 has a very compact design, which is achieved by the integrally formed central body 94. Also in this embodiment, the pressure booster unit 16 according to the schematic representation in the FIG. 1 , two pressure storage pots 92 are provided, which are placed side by side. The two pressure accumulator heads 92 are located opposite the one-piece central body 94, the first switching unit 84 and the second switching unit 86, which may be formed, for example, as solenoid valves, see. Position 50 in FIG. 3 ,

From the illustration according to FIG. 5 is an embodiment of the pressure intensifier unit 16 with integrated high-pressure accumulator according to FIG. 2 out.

The representation according to FIG. 5 is also a pressure amplifier unit 16 with a here also analogous to FIG. 4 to take one-piece formed central body 94. According to this embodiment, the two pressure storage pots 92 and the first switching unit 84 and the second switching unit 86 are adjacent to each other lying on the one-piece central body 94. In the illustration according to FIG. 5 reference numeral 98 denotes a pump port analogous to reference numeral 52 in the embodiment according to FIG FIG. 3 , which denotes the pressure booster unit inlet. The reference numeral 100, however, denotes a high pressure port, analogous to reference numeral 54 in the embodiment according to FIG. 3 , there are the fuel injectors or high pressure lines that run to these, connected.

At the in FIG. 5 The illustrated embodiment of the pressure booster unit 16 is one with which, for example, a 4-cylinder internal combustion engine can be supplied with under system pressure fuel. On the side of the one-piece central body 94 are the connections 82. Together with the side of the central body 94 arranged high-pressure connections 82 and 100 can be connected to the in FIG. 5 For example, 4 fuel injectors or 4 high-pressure lines leading to 4 fuel injectors shown connected.

FIG. 6 shows an alternating operation of two pressure booster piston with synchronous injection.

Out FIG. 6 shows that a piston stroke h of a first pressure booster piston 32 and a second - indicated by dashed lines - pressure booster piston 33 is plotted over time. Reference numeral 22 represents the activation of each fuel injector 22, wherein the fuel injectors 22 have, for example, an in each case ramp-shaped injection characteristic, while the fuel is introduced into the respective cylinders of the internal combustion engine. In addition to a ramp-shaped injection characteristic, multiple injections can also be run, or any further injection strategies can be implemented. As shown in the illustration FIG. 6 As can be seen, respective strokes 112 and 114 may overlap each other slightly in alternate operation 110 of the intensifier pistons 32,33. While the first stroke 112 and the second stroke 114 of the first pressure booster piston 32 are shown in solid lines, in contrast, the first stroke 112 and the second stroke 114 of the second pressure booster piston 33 are indicated in dashed lines. The in FIG. 6 indicated by reference numeral 110 alternately operation of the pressure booster unit 16 assumes that the schematic in the Figures 1 and 2 illustrated pressure booster unit 16 two pressure booster 24 as shown in FIG FIG. 3 includes.

The representation according to FIG. 7 can be a synchronous operation of a pressure booster unit 16 with two pressure amplifiers 24 refer. From the in FIG. 7 shown Hubverläufen the first stroke 112 and the second stroke 114 shows that in this case the first high-pressure piston 32 and the second - dashed lines indicated - high-pressure piston 33 are operated synchronously. In this case fall respectively the first strokes 112 and the second strokes 114 together. By the overlapping delivery strokes 112 and 114 of the two pressure booster piston 32 and 33, the flow rate can be increased and the pressure drop in the high pressure accumulator 20 of the high pressure injection system 10 according to the schematic overview drawings in the Figures 1 and 2 further reduce. The individual injection processes preferably take place synchronously with the delivery - as shown in the illustration FIG. 7 indicated - in order to keep the pressure drop low in this way. As related to FIG. 8 Also, if necessary, the injections can be made between the individual intensifier strokes 112 and 114 of the first pressure intensifier piston 32 and the second pressure intensifier piston 33, which shows an alternate operation of the pressure booster piston in asynchronous injection. For this purpose, an after-delivery may be provided in the pauses between the individual injection processes, as indicated in the illustration according to FIG. In difference for illustration according to FIG. 7 lead the first pressure booster piston 32 and the second pressure booster piston 33 in the injection pauses of the exemplary fuel injectors 22 picked out here, a first stroke 112 from. A further hub 114 may partially, completely or not coincide with an injection. Characteristic in this context is that the first hub 112 does not coincide with the injection, but takes place in an injection pause.

As from the figure sequence the FIGS. 9.1 to 9.5 As can be seen, the pressure booster unit 16 according to the schematic representation in the Figures 1 and 2 be hydraulically connected in various ways with the fuel injectors.

Figure 9.1 shows that the high-pressure pump 14, the pressure booster unit 16 with high-pressure fuel at a pressure level of about 2000 applied bar. The pressure booster unit 16 in turn pressurizes the externally arranged high-pressure accumulator 20 with a pressure which is increased in accordance with the transmission ratio i of the two pressure booster 24, wherein it is an externally arranged high-pressure accumulator 20 according to the illustration 9.1. From this, in each case individual high-pressure lines 140 extend to the fuel injectors 22. These supply in accordance with this piping variant Figure 9.1 a six-cylinder combustion engine.

The representation according to FIG. 9.2 is to be taken in view of the variant according to 9.1 slightly modified casing variant. In the embodiment according to FIG. 9.2 acts on the high-pressure pump 14, the pressure booster unit 16, which in turn acts on the external high-pressure accumulator 20. Between the individual fuel injectors 22 according to FIG. 9.2 runs through a single connecting pieces 144 indicated ring line 142. As a result, each of the individual fuel injectors 22 associated with individual high-pressure lines 140 - as in Figure 9.1 used - avoided. The ring line 142 for connecting the fuel injectors 22 has a significant hydraulic advantage, because the storage volume in the fuel injectors 22 at low spatial distances reduces pressure drops and resulting pressure oscillations. Will on the in the Figures 9.1 and 9.2 Rail disposed externally with respect to the pressure intensifier unit 16, that is to say the high-pressure accumulator 20 is dispensed with, can, in addition, be provided via the ring line 142 in comparison to the embodiment variant according to FIG Figure 9.3 the number of necessary connections to the pressure booster unit 16 are reduced, cf. such as in the embodiments according to Figure 9.4 and 9.5 ,

At the in Figure 9.3 illustrated embodiment of the piping scheme are at the there schematically indicated pressure booster unit 16 six single high-pressure lines 140 to connect to the individual fuel injectors 22, while in the embodiment according to 9.3 facing embodiments according to the Figures 9.4 or 9.5 are connected to the pressure booster units 16 shown there only two single high-pressure lines 140, since the fuel injectors 22 are in turn connected to each other via connecting pieces 144 within the loop 142. In the in Figure 9.5 is shown, the high-pressure accumulator 20 is located externally with respect to the pressure booster unit 16 and acts on a connector 144 of the ring line 142 between the fuel injectors 22 directly.

Claims (14)

1. High-pressure injection system (10), particularly for autoignition internal combustion engines, with at least one high-pressure pump (14) and with a high-pressure reservoir (20), via which at least one fuel injector (22) is supplied with pressurized fuel, the high-pressure injection system (10) comprising at least one pressure amplifier unit (16), characterized in that the pressure amplifier unit (16) has at least two pressure amplifiers (24), each with a high-pressure piston (32, 33), which high-pressure pistons can be operated independently of one another, either the pressure amplifier unit (16) acting upon the high-pressure reservoir (20) and the high-pressure reservoir (20) being arranged externally and having high-pressure connections (26) or the high-pressure reservoir (20) being formed as an integrated component of the pressure amplifier unit (16) which has high-pressure connections (26), the number of high-pressure connections (26) corresponding to the number of fuel injectors (22) to be supplied.
2. High-pressure injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) comprises an intermediate reservoir (18) as an integrated component.
3. High-pressure injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) comprises an intermediate reservoir (18) and a high-pressure reservoir (20).
4. High-pressure injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) is designed in an extended form of construction (80) and at least one switching unit (84) is accommodated on the end face.
5. High-pressure injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) has lateral mounting positions (90) for at least one switching unit (84, 86) and a pressure reservoir head (92) is in each case provided on the pressure amplifier unit (60) on the end faces.
6. High-pressure injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) comprises a one-part central body (94), on which are provided connections (82) which comprise pump connections (52, 58), high-pressure connections (54) for pressure reservoirs (20) and high-pressure connections (100) for the connection of fuel injectors (22).
7. High-pressure reservoir injection system (10) according to Claim 1, characterized in that, at injection pressures below the maximum pressure of the high-pressure pump (14), the required quantity is conveyed to the fuel injectors (22) without the activation of the pressure amplifier unit (16).
8. High-pressure reservoir injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) comprises at least one switching valve (50) which is assigned to the at least one pressure amplifier (24) and in which the at least one switching valve (50) is synchronized with the injection operations in such a way that a feed stroke (112, 114) of the at least one pressure amplifier (24) takes place per cylinder and per 720° crankshaft angle.
9. High-pressure reservoir injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) acts upon the externally arranged high-pressure reservoir (20) which in turn acts with high-pressurized fuel upon the fuel injectors (22) which are connected to one another via a ring line (142, 144), or the high-pressure reservoir (20) acts upon the ring line (142) connecting the fuel injectors (22) to one another.
10. High-pressure reservoir injection system (10) according to Claim 1, characterized in that the pressure amplifier unit (16) is acted upon by the high-pressure pump (14) and acts upon the fuel injectors (14) which are connected to one another hydraulically via a ring line (142, 144).
11. High-pressure reservoir injection system (10) according to Claim 1, characterized in that the feed quantity of the pressure amplifier unit (16) is increased and the pressure drop in the high-pressure reservoir (20) is reduced by an at least partial overlapping of feed-stroke travels (112, 114) of the pressure amplifier pistons (32, 33).
12. High-pressure reservoir injection system (10) according to Claim 1, characterized in that injections (122) take place synchronously (120) with the operation of the pressure amplifier unit (16).
13. High-pressure reservoir injection system (10) according to Claim 1, characterized in that injection (122) takes place asynchronously (130) with the operation of the pressure amplifier unit (16).
14. High-pressure reservoir injection system (10) according to Claim 11, characterized in that a higher-pressure afterfeed of the pressure amplifier unit (16) during injection (122) reduces pressure loss in the high-pressure reservoir (20) by quantity extraction.

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