EP1111230B1 - Hydraulic device for transmitting an actuator movement - Google Patents

Hydraulic device for transmitting an actuator movement Download PDF

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Publication number
EP1111230B1
EP1111230B1 EP20000127847 EP00127847A EP1111230B1 EP 1111230 B1 EP1111230 B1 EP 1111230B1 EP 20000127847 EP20000127847 EP 20000127847 EP 00127847 A EP00127847 A EP 00127847A EP 1111230 B1 EP1111230 B1 EP 1111230B1
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EP
European Patent Office
Prior art keywords
storage chamber
piston
area
actuator
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20000127847
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German (de)
French (fr)
Other versions
EP1111230A3 (en
EP1111230A2 (en
Inventor
Bernhard Fischer
Bernhard Dr. Gottlieb
Andreas Dr. Kappel
Randolf Dr. Mock
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Siemens AG
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Siemens AG
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Filing date
Publication date
Priority to DE19962177 priority Critical
Priority to DE1999162177 priority patent/DE19962177A1/en
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1111230A2 publication Critical patent/EP1111230A2/en
Publication of EP1111230A3 publication Critical patent/EP1111230A3/en
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Publication of EP1111230B1 publication Critical patent/EP1111230B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603Injectors peculiar thereto with means directly operating the valve needle using piezo-electric or magnetostrictive operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167Means for compensating clearance or thermal expansion
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16Sealing of fuel injection apparatus not otherwise provided for
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Description

The invention relates to a hydraulic device for Transferring a movement of an actuator to an actuator according to the preamble of claim 1, in particular for use in a fluid dispenser. Such a device, hereinafter also referred to as a transmission element, is from DE 197 08 304 A1 and known from US 4858439.

In automotive engineering, memory injection systems are increasingly used used in those with very high injection pressures is worked. In such z. B. under the name "Common rail systems" known injection systems Fuel under high pressure in the cylinders of the internal combustion engine arranged injection valves created. The Injection into the cylinder is done by opening and Closing the injectors triggered, the injectors can be controlled via actuators, which after the electromagnetic and to achieve high switching speeds achieve, even after the piezoelectric, electrostrictive or magnetostrictive principle. The actuators in the Actuate injectors, if necessary with the interposition of a servo valve a valve needle in the injection valve.

In particular, a series-compatible fuel injector the following requirements:

The valve needle should either be unloaded in the injection valve be arranged or loaded with a pressure-dependent force become. If an increasing fuel pressure at the Valve needle is in contact with the valve needle to ensure sufficient tightness with increasing Fuel pressure pressed ever more firmly onto the valve seat becomes.

Furthermore, the injection valve is said to be insensitive to thermal or pressure-induced elongations. Also supposed to the functionality of the injector Setting effects that e.g. B. by aging processes of the actuator can be triggered, impaired. To changes in length in the injection valve caused by thermal, pressure or set effects are prevented usually the valve needle or the other components in the Injector made from special steels, but very are expensive. Furthermore, it is also when using such expensive special steels necessary between the individual Provide sufficient clearance between components to prevent any To be able to absorb elongations between the components. This necessary safety distance of 3 µm to 5 µm however, is lost as a usable stroke of the actuator, which in particular when using a piezo actuator that is only a small one Causes problems when opening the valve needle can lead.

No gap between the individual components in the injection valve To have to provide, is DE 197 08 304 A1 proposed a hydraulic transmission element that the Deflection of the actuator in the injection valve on a drive stamp of the servo valve or a guide shaft of the Valve needle transmits. The hydraulic transmission element is essentially cylindrical and has a hydraulic chamber made by a flexible membrane is limited. The drive stamp is located on the flexible membrane the servo valve or the guide shaft of the Valve needle on. A connecting hole leads from the hydraulic chamber with throttling effect to a storage chamber, the is provided inside the transmission element and by a preloaded spring plate is completed. About the Spring plate is a rigid cover plate in the hydraulic chamber arranged, which rests on the actuator of the injection valve. The hydraulic chamber and the storage chamber are equipped with a hydraulic Medium filled.

In the idle state, the in the Storage chamber prevailing pressure of the hydraulic medium transferred to the hydraulic chamber so that the flexible membrane always on the drive stamp of the servo valve or on the guide shaft the valve needle is in contact, even if due to thermal effects or aging processes Arrangement of the individual components in the fuel injector result. When the actuator is actuated, the deflection this actuator via the transmission element essentially unchanged on the drive stamp of the servo valve or transfer the guide shaft of the valve needle. The connecting hole between the hydraulic chamber and the storage chamber is designed so that due to the in the area of control times in milliseconds essentially no hydraulic medium from the hydraulic chamber into the Storage chamber can drain.

The transmission element known from DE 197 08 304 A1 is characterized by a complicated structure. Furthermore, it is with this known transmission element difficult, temperature compensation over the entire working area of the fuel injection valve from approx. -40 ° C to Ensure + 150 ° C. In this wide temperature range there may be a change in the volume of the transfer element hydraulic medium of up to 20% come. Such a large fluctuation in volume can, however very difficult of that chosen in DE 197 08 304 A1 Cope with construction.

The object of the present invention is to ensure that there is no play hydraulic device for transmitting a movement of a Provide actuator on an actuator, which is characterized by a great reliability with high permanent loads and strong ones Temperature fluctuations.

This object is achieved by a device according to claim 1 solved. Further advantageous embodiments of the invention are specified in the dependent claims.

The device according to the invention is characterized by Transmission element, which is a first piston element, the is firmly connected to an actuator, and a second piston element, which is firmly connected to an actuator, being between the first piston element and the second Piston element is a hydraulic chamber, and one with the hydraulic chamber via a throttle gap connected storage chamber comprises a pressure-loaded area, whose range limits are elastic. This structure reliably ensures an automatic Compensation for large changes in distance between the actuator and the actuator caused by thermal pressure or setting effects can be caused. In addition, the ensures elastic design of a storage chamber area, that the transmission element over a wide temperature range, especially the entire work area of a Functional fuel injector from approx. -40 ° C to + 150 ° C remains. The transmission element according to the invention can also be both inward and inward outside opening fuel injector used become. Furthermore, the transmission element is characterized by a very compact design, a very high hydromechanical Transmission efficiency and excellent dynamic Transmission properties from, since only a very small hydraulic chamber between the first and the second piston element is needed.

According to the invention, the elastic Storage chamber area by a bellows arrangement, preferably consisting of metal bellows, limited. Such metal bellows are very stiff radially, but very stiff in the axial direction soft design and can therefore reliably change volume in the hydraulic fluid contained in the transmission element take up.

According to a further preferred embodiment, the actuator biased by a spring element that is fixed to the first Piston element of the transmission element is connected. With this configuration, a return spring that Actuator in its starting position after actuation of the actuator has ended resets, small dimensions, because the Function of the return spring by the retracting movement of the Actuator via the transmission element to the actuator works, is supported.

According to a further preferred embodiment, by suitable choice of the proportions of the pressure-effective areas of the first piston element and the second piston element a stroke translation of the actuator movement to the actuator. This ensures that even when using a Piezo element as an actuator a sufficient stroke for actuation of the actuator is generated.

The invention is explained in more detail below with reference to the drawings. Show it:

Figure 1
an outwardly opening fuel injection valve with a hydraulic transmission element according to the invention in a first embodiment;
Figure 2
an inward opening fuel injection valve with a hydraulic transmission element according to the invention in the first embodiment; and
Figure 3
an outwardly opening fuel injection valve with a hydraulic transmission element according to the invention in a second embodiment.

The fuel injector shown in Figure 1, which opens out into a combustion chamber of an internal combustion engine, is operated with fuel under high pressure. This injector is in the upper part of a housing 1 installed a drive unit that is essential Component a piezoelectric multilayer actuator 8 in low voltage technology having. This piezoelectric multilayer actuator 8 is surrounded by a tube spring 9, which is between a head plate 10 and a base plate 11 is welded, the Bourdon tube 9 is biased so that the piezoelectric multilayer actuator 8 under a mechanical pressure preload stands. The housing 1 is also with a base plate 11 of the Drive unit as stiff as possible, preferably via a Weld 12, connected.

The piezoelectric multilayer actuator 8 acts when it is electrical is controlled via its feed lines 19, via a hydraulic transmission element on the rear end of a Valve needle 3 on. The valve needle 3 is in the front part of the Housing 1 of the injection valve in a continuous inner bore 30 arranged and closes with one at rest at the front end of the valve needle 3 arranged valve plate 4 a valve seat 2 on the housing 1. The closed one The initial state in the injection valve is prestressed Nozzle spring 5 ensures that with the valve needle 3 is connected via a snap ring 6 and the valve plate 4 presses on valve seat 2. When the piezoelectric Multilayer actuator 8 lifts the transmission element transferred to the rear end of the valve needle 3 Deflection the valve plate 4 from the valve seat 2, so that Fuel that into a fuel chamber 13 in the housing 1 a fuel supply line 7 is fed in on the valve needle 3 injected past into the combustion chamber of the internal combustion engine can be.

Because the fuel is under very high pressure in the fuel chamber 13 in housing 1, this area must be reliable from the other areas in the housing 1 of the injection valve, in particular be sealed by the drive area. to hermetically sealed and axially very soft implementation of the Valve needle 3 from the fuel chamber 13 in the area in which the transmission element and the drive unit installed are a metal bellows 15. To the fuel chamber 13th adjoins an annular shoulder 14, which in the inner bore 30 protrudes. On the valve needle 3 there is still an annular one Connector 16 attached. Between the connector 16 on the valve needle 3 and the annular circumferential Paragraph 14 in the housing 1 is parallel to the valve needle 3 running metal bellows 15 welded to the hermetic Sealing the fuel chamber 13 against the other housing areas in which the drive unit and the transmission element is used. Will continue the valve needle 3 secured by the metal bellows 15 against rotation. This can be particularly advantageous if a stroke-limiting stop for the valve needle 3 in the Fuel injector is installed.

The use of the metal bellows 15 enables the passage of needles a perfect, permanent and reliable seal the high pressure area in the injection valve compared to the rest Areas. The metal bellows 15 holds, like calculations and Tests have shown, despite small wall thicknesses of e.g. 50 µm to 500 µm due to its high radial rigidity very high pressures without being irreversibly deformed. The metal bellows 15 can also be designed that by a sufficient number of waves a high one axial compliance, d. H. low spring rate in the direction of movement the valve needle 3 is reached to the deflection not to affect the valve needle 3 and by the temperature-related changes in length of the needle guide in the valve needle 3 forces introduced as low as possible to keep. Furthermore, by using the metal bellows 15 in the needle feedthrough with high reliability Fuel leakage can be prevented.

The needle feed-through from annular shoulder 14, metal bellows 15 and connector 16 can also be designed such that the pressure-related acting on the valve needle 3 Forces compensate each other so that the valve needle 3 is kept force-free overall. This enables the Design the injector so that one of the fuel pressure almost independent switching behavior is possible because the opening and closing forces then only from the piezoelectric Multilayer actuator 8 and the force of the preloaded nozzle spring 5 can be determined.

On the other hand, that of the annular shoulder 14, the metal bellows 15 and the connecting piece 16 formed valve needle bushing can also be designed so that one with increasing fuel pressure in the fuel chamber 13 increasing Force results with which the valve plate 4 in the Valve seat 2 is pressed. By choosing the hydraulic Diameter through the paragraph 14, the metal bellows 15 and the connector 16 is fixed, there is thus the possibility the valve needle 3 of the injector in the desired Wise pressure, d. H. completely free of pressure forces, overcompensated or keep undercompensated.

The metal bellows 15 still has due to its metallic Material over a wide working temperature range with constant functionality. The thermal changes in length of the metal bellows 15 lead due to the low axial spring constant of the metal bellows 15 only to a negligible introduction of force into the valve needle 3 in the axial direction. The metal bellows 15 can over it addition due to its mechanical spring action in Axial direction, the nozzle spring 5 partially or completely replace.

To the stroke of the piezoelectric multilayer actuator 8 on the To transmit valve needle 3, the transmission element is between the drive unit and the valve needle 3 are provided. This transmission element serves primarily as a hydraulic one Game balancing element to prevent any game between the piezoelectric multilayer actuator 8 and the valve needle 3 excluded. Furthermore, with the transmission element a stroke translation take place.

The transmission element has a primary piston 21 and one Secondary piston 23, which in a to the annular shoulder 14 arranged in the housing 1 adjacent bore section are. This bore section is of two stages, with a first, following the drive unit wider bore section 31 in which the primary piston 21 sits and a second narrower bore section 32, which is adjacent to the stop 14 in the housing 1 and in which the secondary piston 23 is arranged. The primary piston 21 is essentially cylindrical and on the top plate 10 attached to the drive unit or preferably fixed over a weld connected to this. Preferably exist the head plate 10 and the primary piston from one part. The secondary piston 23 is designed as a hollow cylinder and plugged onto the rear end of the valve needle 3, the the end face of the secondary piston facing the primary piston 21 23 essentially flat to the end surface of the valve needle 3 is arranged. The valve needle 3 and the secondary piston 23 are also preferably fixed via a weld, at least but without play and mechanically as stiff as possible connected.

The primary piston 21 and the secondary piston 23 are still spaced from each other so that between the opposite End faces in the area of the transition from the first Bore section 31 to the second bore section 32 a Hydraulic chamber 22 is formed. Furthermore is in the transmission element a two-part storage chamber 24 is provided, a first storage chamber area 241 in the inner bore 30 has that through the lower end face of the secondary piston 23 and through the connector 16 of the metal bellows 15 is limited to the valve needle 3. This first storage chamber area 241 is formed in the housing 1 unthrottled connection bore 223 to a second storage chamber area 242 connected in the first bore section 31 adjacent housing area 34 around the drive unit is arranged around. The second storage chamber area 242 is arranged by two concentric to each other Bellows 25, 26 and a pressure ring 27 limited, which in turn is held by a compression spring 28 which a perforated plate 29 is supported in the housing area 34. The Inner bellows 25 is between the inside of the pressure ring 27 and the rear face of the primary piston 21, which protrudes from the first bore section 31, shrink wrapped. The outer bellows 26 is on the outside of the pressure ring 27 and to one of the first bore section 31 adjacent housing stage 30 welded. In the housing stage 30 between the two bellows 25, 26 opens the connection bore 223.

The hydraulic chamber 22 and the storage chamber 24 protrude a throttle gap 36 which between the peripheral wall of the Secondary piston 23 and the inner wall of the second bore section 32 is formed, and via a throttle gap 37, the between the peripheral wall of the primary piston 21 and the Inner wall of the first bore section 31 is formed is in communication with each other. Furthermore, the entire interior the transmission element with a hydraulic fluid filled, which is under a slight positive pressure, the is generated by the compression spring 28, which over the pressure ring 27 acts on the second storage chamber area 242. In front filling the interior of the transmission element with hydraulic fluid this hydraulic fluid is degassed, to dissolve any gas bubbles in the liquid.

The injection valve with the transmission element works like follows:

The piezoelectric is used to initiate the injection process Multilayer actuator 8 via the electrical feed lines 19 loaded. This causes the piezoelectric multilayer actuator 8 deflects axially and via the top plate 10 Primary piston 21 down into the first bore section 31 pushes in.

In the transmission element, the throttle gap 36 on the secondary piston 23 and the throttle gap 37 on the primary piston 21, which establish a connection between the hydraulic chamber 22 and the storage chamber 24, are dimensioned such that during the typical activation times of the piezoelectric multilayer actuator 8 from 1 to 5 ms only one vanishing little exchange of hydraulic fluid between the hydraulic chamber 22 and the storage chamber 24 can take place. This means that the volume of the hydraulic fluid during the injection time is only determined by the compressibility of the hydraulic fluid, and the hydraulic chamber 22 can thus be regarded as a rigid piston. The spring constant c of the hydraulic chamber 22 can be estimated as follows. κ = -1 / V * δ and V = A * H ⇒ dP = -1 / (κ V) * A ie

κ:
Hydraulic fluid compressibility
V:
Volume of the hydraulic chamber
P:
print
A:
Cross-sectional area of the hydraulic chamber
H:
Hydraulic chamber height
With dF = dP / A ⇒ dF = -1 / (κ V) A 2 ie F: strength
surrendered c = -dF / dh ⇒ c = A / (κ h)

The above equation shows that the spring constant c of the hydraulic chamber 22 is greater, the lower its height and the larger its effective cross-sectional area. Simulation calculations have also shown that thermal and pressure-induced expansion of a maximum of 50 µm can be expected. In order to consider the hydraulic chamber 22 as a rigid piston, the spring constant c of the hydraulic chamber 22 should be in the range of 10 8 N / m or higher. This means that, assuming that the compressibility of the hydraulic fluid κ is approximately 10 * 10 -10 m 2 / N, which corresponds to a typical value for a hydraulic fluid, the desired value for the spring constant c z. B. can be achieved with a cross-sectional area of 1 cm 2 and a height of 0.1 cm. The exact design of the height and cross-sectional area of the hydraulic chamber 22 can, however, be adapted to the conditions in the injection valve in order to achieve a compact design.

By designing the hydraulic chamber 22 as a rigid piston is the movement of the primary piston 21 by the piezoelectric Multilayer actuator 8 is triggered, low loss directly on transfer the secondary piston 23. The movement of the secondary piston 23 is only slightly different from that in the first Hydraulic fluid storage chamber area 241 damped because of the excess hydraulic fluid the rapid rise in pressure in the first storage chamber area 241 via the unthrottled connecting bore 223 in the second storage chamber area 242 is pushed away. The two Bellows 25, 26 arranged concentrically to one another that delimit the second storage chamber region 242 are radial very stiff, but very soft in the axial direction. Metal bellows are preferably used as spring bellows, which essentially the metal bellows 15 of the needle feedthrough correspond. At this point it is the same the use of elastomeric materials for the bellows 25, 26 possible. When hydraulic fluid from the first storage chamber area 241 via the connection bore 223 in the second Storage chamber area 242 is pressed, the second expands Storage chamber area 242 against the holding force on the Compression ring 27 axially loaded compression spring 28 in the direction the foot plate 11 of the drive unit.

The movement of the secondary piston triggered by the primary piston 21 23 moves the one connected to the secondary piston 23 Valve needle 3 against the restoring force of the nozzle spring 5 after below, so that the valve plate 4 lifts off the valve seat 2 and the injector opens. The elongation of the piezoelectric Multilayer actuator 8 is in a shift of the secondary piston 23 and thus the valve needle 3, the the ratio of the pressure-effective areas of the primary piston 21 and the secondary piston 23 in the hydraulic chamber 22 corresponds. By suitable adjustment of the primary piston surface to the secondary piston surface can be z. Legs Extension of the stroke of the piezoelectric multilayer actuator 8 in relation to the stroke of valve needle 3. hereby can be reliably guaranteed that the extreme short stroke of the piezoelectric multilayer actuator 8 in all Operating conditions of the injection valve are sufficient, the valve needle 3 to open.

The injection process is ended by the piezoelectric Multilayer actuator 8 over the electrical leads 19 again is discharged. This shortens the piezoelectric Multilayer actuator 8 to its initial length, with the Bourdon tube 9 prevents the piezo ceramic due to inertia effects when contracting under tension. There the primary piston 21 is fixed to the drive unit via the head plate 10 is connected by the contraction of the piezoelectric multilayer actuator 8 also the primary piston 21 withdrawn from the first bore section 31. hereby there is a brief drop in pressure in the hydraulic chamber 22, which due to the extremely short switching times of the piezoelectric Multilayer actuator 8 and the small size Throttle gap 36 on secondary piston 23 is not caused by reflow hydraulic fluid from the storage chamber 24 can be compensated immediately via the throttle column 36, 37 can. This pressure drop in the hydraulic chamber 22 compared the pressure in the storage chamber 24 leads to a pressure difference across that facing the hydraulic chamber Side of the secondary piston 23 and the first storage chamber area 241 facing side of the secondary piston 23 drops. This will reset the valve needle 3 supported by the nozzle spring 5, so that a quick Closing the injector is achieved, which is convenient affects the course of combustion.

The inventive design of the transmission element it is still possible to automatically switch all thermal, by setting effects of the drive unit or caused to compensate for pressure-related changes in length in the injection valve. Is z. B. the valve needle 3 due to thermal or expansion due to pressure in relation to the housing 1 of the Injector, the secondary piston 23 is up in the second bore section 32 drawn. The throttle gap 36 on the secondary piston 23 is also designed so that during the thermal processes, which are in the time range of a few seconds to minutes, hydraulic fluid via the throttle column 36, 37 between the storage chamber 24 and the hydraulic chamber 22 can be replaced. If the Secondary piston 23 is therefore due to the thermal processes hydraulic fluid flows into the second bore section 32 so long from the hydraulic chamber 22 over the throttle column 36, 37 in the storage chamber 24 until in the hydraulic chamber 22 and in the storage chamber 24 again establishes a pressure balance. The length compensation will only by the height of the hydraulic chamber 22 limited.

For a reliable function of the transmission element especially a hermetic seal of the hydraulic fluid opposite the fuel chamber or the drive unit required. The requirements are so high the bellows 25, 26, which are therefore preferably as metal bellows are trained. These metal bellows are wavy formed, as a result of which a very small axial spring constant can be achieved. The axial deformation of the metal bellows by a pressure load is not at all low, but stands out, just like that on the individual Bellows waves acting forces, in total over the entire length of the metal bellows almost on. As a particularly cheap one The shape for the bellows shaft has been considered, in longitudinal section, from joined semicircle segments with straight Intermediate pieces existing geometry proved. Across from the semicircular segments have a sinusoidal wave shape existing walls lower mechanical stresses in the axial direction with higher axial compliance on.

The hydraulic fluid in the hydraulic chamber 22 and the Storage chamber 24 is, as shown, under a small Overpressure generated by the compression spring 28, the acts on the pressure ring 27 of the second storage chamber area 242. Because of this slight overpressure at the same time bubble-free filling of the hydraulic fluid into the transmission element ensures that the fast Switching operations of the piezoelectric multilayer actuator 8 are not lead to cavitation in the hydraulic fluid. The Compression spring 28 can alternatively also partially or completely a spring action of the bellows 25, 26 to be replaced. Farther there is the possibility of throttling gaps 36, 37 each to be provided only on the secondary piston 23 or on the primary piston 21, so an exchange of hydraulic fluid between one of the storage chamber areas 241, 242 and the hydraulic chamber 22 takes place. However, throttle gaps can also be used be provided on the primary piston 21 and on the secondary piston 23.

In Figure 1 is an outwardly opening injection valve shown. However, there is also the possibility of the invention Transmission element with one inside opening injector. As shown in Figure 2 is then the valve needle 3 by the nozzle spring 5 instead under tensile stress under compressive stress so that the Valve needle 3 at rest with a conical needle tip 104 on a conical valve seat 102 in the injection valve sits below which an injection hole 103 for injection of fuel is formed in the internal combustion engine.

The injection valve shown in Figure 2 is exactly the opposite operated to the injection valve shown in Figure 1. For safety reasons, the injection valve is designed so that when the piezoelectric multilayer actuator is not controlled 8 the injector is closed, d. H. the Needle tip 102 is pressed against the valve seat 104.

At the start of the internal combustion engine, the piezoelectric multilayer actuator 8 controlled. This is long and thereby pushes the primary piston 21 into the first Bore section 31. The resulting pressure increase in the hydraulic chamber 22 is via the throttle gap 36 Secondary piston 23 and the throttle gap 37 on the primary piston 21, for an exchange of hydraulic fluid with the Storage chamber 24 worry, balanced. This poses then a state of equilibrium again within fractions of a second a, at which the injector continues to be closed remains. The injection valve is operated in such a way that the valve needle 3 always opens when the piezoelectric Multilayer actuator 8 is discharged and thereby the Primary piston 21 and thus also the secondary piston 23 on which the valve needle 3 is attached, withdraw.

Figure 3 shows a further embodiment of a outside opening injection valve, with the base pressure on the hydraulic fluid in the transmission element through a Compression spring 128 arranged centrally in the primary piston 121 is generated becomes. For this purpose, the primary piston 121 is cup-shaped, being between the head plate 10 and a bottom surface of the primary piston 121 an additional third storage chamber area 243 is formed. The primary piston 121 is arranged so that it is in with its bottom surface extends the first bore portion 31. The sidewalls the primary piston 21, on the other hand, are essentially located in the Housing area 34 in which the drive unit is arranged.

The compression spring arranged in the third storage chamber area 243 128 is between the head plate 10 of the drive unit and a pressure plate 127 located in the third storage chamber area 243 is provided, welded. The compression spring 128 becomes the third storage chamber area 243 from protected by a metal bellows 125.

The second storage chamber area 242 is between the top plate 10 of the piezoelectric multilayer actuator 8 and Housing stage 35 around the wall of the primary piston 121 educated. This second storage chamber area 242 is over a connection bore 136 with the third storage chamber area 243 connected in the primary piston 121. How it works of the transmission element shown in Figure 3 corresponds to that shown in Figure 1 transmission element. By providing an internal compression spring 128 can, however, be a higher one Base pressure and a possibly more compact design of the transmission element can be achieved.

Instead of the internal compression spring 128, the metal bellows 125 and the top plate 10 limited gas-tight volume also be pressurized with a pressurized gas, so that instead the mechanical compression spring 128 a gas pressure spring for maintaining the basic pressure in the storage chamber areas 241, 242, 243.

The in the above description, the drawings and the Features of the invention disclosed in claims can be both individually as well as in any combination for the realization of the invention in its various configurations in Be meaningful.

Claims (11)

  1. Device for transmitting an actuator (8) movement to a controlling element (3) having
    a transmission element which establishes an acting connection between said actuator (8) and said controlling element (3) and determines a hydraulic chamber (22) and a storage chamber (24) which are filled with a hydraulic fluid and are interconnected via at least one throttle gap (36, 37), wherein
    the transmission element has a first and a second piston element (21, 23; 121), with the first piston element (21; 121) being securely linked to the actuator (8) and the second piston element (23) being securely linked to the controlling element (3), with the hydraulic chamber (22) being embodied between the first piston element (21; 121) and the second piston element (23) and with the storage chamber (24) containing a pressure-loaded storage chamber area (242, 243) delimited by metal bellows, characterised in that said metal bellows form a bellows arrangement (25, 26, 125) and are prestressed by a spring element in such a way that the storage chamber area is under a pressure load and its pressure is approximately constant.
  2. Device according to Claim 1 characterised in that the storage chamber area (242, 243) on which pressure impinges is impinged upon by a pressure spring (28) via a pressure plate (27; 127).
  3. Device according to Claim 1 characterised in that the storage chamber area (242, 243) on which pressure impinges is impinged upon by a gas-pressure spring.
  4. Device according to one of Claims 1 to 3 characterised in that the first piston element (21; 121) and the second piston element (23) are located in an inner bore area, embodied in a two-stage manner, of a housing (1), with the first piston element (21; 121) and the second piston element (23) being spaced apart such that the hydraulic chamber (22) is embodied between the opposite front faces in the area of the transition from a first bore section (31) to second bore section (32), with the travel of the first piston element (21; 121) being translated to the second piston element (23) corresponding to the relationship between said front faces.
  5. Device according to Claim 4 characterised in that the storage chamber (24) is embodied as a two-part storage chamber having a first storage chamber area (241), delimited by the lower front face of the second piston element (23) and by a lead-through (14, 15, 16) on the controlling element (3), and having a second storage chamber area (242) which is located in a housing area (34) accommodating the actuator and which is linked to the first storage chamber area (241) via a connecting bore (223), with the second storage chamber area (242) being delimited by two mutually concentrically arranged bellows (25, 26) and by a pressure ring (27) under the load of a pressure spring (28).
  6. Device according to Claim 4 characterised in that the first piston element (121) is embodied as being pot-shaped and in that the storage chamber (24) is of three-part design, having a first storage chamber area (241) delimited by a lower front face of the second piston element (23) and by a lead-through (14, 15, 16) on the controlling element (3), having a second storage chamber area (242) embodied in a housing area (34) accommodating the actuator (8) around the first piston element (121), and having a third storage chamber area (243) embodied in the first piston element (121), with the first storage chamber area (241) being linked to the second storage chamber area (242) via a first connecting bore (223) in the housing (1) and the second storage chamber area (242) being linked to the third storage chamber area (243) via a second connecting bore (136) in the first piston element (121) and with a pressure spring (128), clamped between a head plate (10) of the actuator (8) and a pressure plate(127) and delimited by bellows (125), or a gas-pressure spring being located in the third storage chamber area (243).
  7. Device according to one of Claims 1 to 6 characterised in that the actuator (8) is a piezoelectric multi-layer actuator prestressed by a spring element (9) and in that the first piston element (21; 121) is securely attached to a head plate (10) of the multi-layer actuator (8).
  8. Device according to one of Claims 1 to 6 characterised in that the actuator operates according to the electrostrictive or magnetostrictive principle.
  9. Device according to one of Claims 1 to 8 characterised in that the bellows (25, 26; 125) are metal bellows consisting preferably of semicircular segments having straight intermediate sections.
  10. Device according to one of Claims 1 to 9 characterised in that the bellows (25, 26; 125) are produced from an elastomeric material.
  11. Device according to one of Claims 1 to 10 characterised in that the hydraulic chamber (22) is embodied such that the spring constant of the hydraulic chamber (22) is at least 108 N/m.
EP20000127847 1999-12-22 2000-12-19 Hydraulic device for transmitting an actuator movement Expired - Fee Related EP1111230B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19962177 1999-12-22
DE1999162177 DE19962177A1 (en) 1999-12-22 1999-12-22 Hydraulic device for transmitting an actuator movement

Publications (3)

Publication Number Publication Date
EP1111230A2 EP1111230A2 (en) 2001-06-27
EP1111230A3 EP1111230A3 (en) 2002-05-08
EP1111230B1 true EP1111230B1 (en) 2004-11-24

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EP20000127847 Expired - Fee Related EP1111230B1 (en) 1999-12-22 2000-12-19 Hydraulic device for transmitting an actuator movement

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EP (1) EP1111230B1 (en)
DE (1) DE19962177A1 (en)
ES (1) ES2228394T3 (en)

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Also Published As

Publication number Publication date
EP1111230A3 (en) 2002-05-08
EP1111230A2 (en) 2001-06-27
DE19962177A1 (en) 2001-07-12
ES2228394T3 (en) 2005-04-16

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