EP0795081A1 - Electrohydraulic drive - Google Patents
Electrohydraulic driveInfo
- Publication number
- EP0795081A1 EP0795081A1 EP95940120A EP95940120A EP0795081A1 EP 0795081 A1 EP0795081 A1 EP 0795081A1 EP 95940120 A EP95940120 A EP 95940120A EP 95940120 A EP95940120 A EP 95940120A EP 0795081 A1 EP0795081 A1 EP 0795081A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- actuator
- piston
- electro
- hydraulic drive
- drive according
- 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.)
- Granted
Links
- 238000002347 injection Methods 0.000 abstract description 10
- 239000007924 injection Substances 0.000 abstract description 10
- 238000006073 displacement reaction Methods 0.000 abstract description 9
- 238000004519 manufacturing process Methods 0.000 abstract description 7
- 229910000831 Steel Inorganic materials 0.000 abstract description 2
- 239000010959 steel Substances 0.000 abstract description 2
- 208000006011 Stroke Diseases 0.000 description 12
- 239000010720 hydraulic oil Substances 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 5
- 239000000446 fuel Substances 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000004044 response Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- VNNRSPGTAMTISX-UHFFFAOYSA-N chromium nickel Chemical compound [Cr].[Ni] VNNRSPGTAMTISX-UHFFFAOYSA-N 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000002277 temperature effect Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
Definitions
- the injection valve known from /! / Contains a compact drive, which has very good dynamic properties and still works reliably even at high actuation frequencies (f> 1 kHz). Since the drive enables valve opening and closing times in the range of ⁇ ⁇ 0.1 ms, even the smallest amounts of fuel can be injected precisely and reproducibly into the combustion chamber of an engine.
- the main components of the drive are a piezo actuator generating the primary travel range and a hydraulic stroke transformer, which essentially consists of a pressure piston driven by the piezo actuator and a stroke piston which is axially displaceably mounted in a pressure piston bore and is connected to the valve needle.
- the piezo actuator arranged in one of the hydraulic chambers is supported on the housing side on a ball cap bearing. This measure ensures that the actuator always rests on the pressure piston over the entire surface even when the end faces are non-parallel, and that there are no stroke losses.
- the structure of the known valve places high demands on the axial symmetry and dimensional accuracy of the individual components.
- the multiply guided reciprocating piston has to be manufactured to an accuracy of a few ⁇ m in order to prevent tilting or jamming. This complicates mass production and considerably increases the cost of manufacturing the valve.
- the aim of the invention is to provide a reliable electrohydraulic drive which has a compact structure. sits, works within a wide temperature range and has good dynamic properties.
- An electro-hydraulic drive with the features specified in claim 1 has these properties.
- the advantage that can be achieved with the invention is, in particular, that even a comparatively large decentration of one of the multiply guided parts does not impair the functionality of the drive.
- the drive can therefore be manufactured with much less effort and manufactured more cost-effectively.
- Figure 1 shows an electro-hydraulic drive for a fuel injection valve in section
- Figure 2 is a two-part reciprocating piston of the force-translation of the drive in section
- FIG. 1 essentially shows only the components of a fast fuel injection valve relating to the drive according to the invention, as is known, for example, from / l / or described in more detail in the older German application / 2 /.
- the injection valve contains an electromechanical actuator P which acts on a hydraulic stroke transformer DK / HK and which is supplied with the required operating voltages via a pressure-tight housing bushing LD.
- the actuator P In order to initiate the injection of the fuel into the combustion chamber of the engine, the actuator P is activated and thereby elongated in the axial direction.
- the change in length .DELTA.l of the actuator P results in a corresponding displacement of the pressure piston DK mounted in a cylindrical bore of the housing VG so that there is an overpressure p 1 # in the hydraulic oil-filled chamber KAI in the hydraulic oil-filled chamber and through a pressure piston bore Bl fluidly connected chambers KA2 and KA3 a vacuum P2 / 3 ⁇ Pi on aut.
- the fuel injection is ended by the electrical discharge of the piezo actuator P.
- the pressure piston DK moves back down to its starting position under the force of the restoring force exerted by a strong plate spring TF.
- the spiral spring SF Supported by the spiral spring SF and the pressure difference existing between the chambers KAI and KA2 / KA3, the reciprocating piston HK executes an opposite movement upwards, so that the valve needle VN guided out of the housing VG is lowered onto the sealing seat and closes the injection opening.
- the transient mode of operation of the drive makes it necessary to mechanically pretension the piezo actuator P.
- the force required for this is generated by the plate spring TF arranged in the chamber KAI, which also supports the return of the pressure piston DK to its rest position.
- Flow channels SK in the chamber ceiling ensure an unimpeded inflow and outflow of the hydraulic oil into the volume enclosed by the plate spring TF and the valve housing VG.
- the compensation element AE which is in the form of a spherical layer, is preferably made of stainless steel or a chromium-nickel steel. Due to its polished surfaces, the compensating element AE can slide freely on the piezoceramic during assembly of the hydraulics and thus compensate for a non-concentric alignment of actuator P and pressure piston DK.
- the free rotatability of the compensating element AE within the conical abutment WL also ensures that the upper part of the piezo actuator P, which is secured against rotation on the housing base, is always in contact with the pressure piston DK over the entire surface.
- the disc spring TF which mechanically pre-stresses the piezo actuator P, ensures the frictional contact between the parts.
- the force / displacement ratio driven by the actuator P consists of two coupled hydraulic transformers, the transmission ratio t
- AD1 area of the piston top
- AH1 area of the piston top
- AD2 Actuator-side pressure piston surface
- AH2 Actuator-side reciprocating piston surface
- Equation (2) only applies on the condition that the actuator P arranged in the hydraulic chamber KA3 has the same volume in the elongated and unloaded state. Like the piezo stack P used, electrostrictive and magnetostrictive actuators also show such behavior in good proximity.
- the pressure piston DK of the force / displacement ratio shown in FIG. 1 is designed in stages (AD1 ⁇ AD2) in order to take into account the inequality of the pressure-effective piston surfaces AH1 ⁇ AH2 caused by the valve needle.
- the hydraulic coupling of the two stroke transformers has the result that with each change in length of the actuator P complementary pressures build up in the chambers KAI and KA2 / KA3, whereby a displacement of the pressure piston DK by ⁇ l increases in an opposite manner corresponding to the hydraulic transmission ratio ⁇ »1 Displacement of the HK piston in the pressure piston bore ZY.
- the hydraulic chambers KAI, KA2, KA3 are connected both to one another and to the compensating volume AV, which is under pressure, between the pistons DK, HK and the corresponding cylinder bores KS. Temperature-related changes in volume of the hydraulic oil can therefore neither lead to the formation of static pressure differences between the chambers KAI and KA2 / KA3 (this would result in undefined positions of the HK reciprocating piston), nor to the formation of undefined pressure states in the entire system.
- the connection between the ring chamber RV and the equalizing volume AV has been established via the housing bore Gl furthermore the advantage that there is no cavitation in the hydraulic oil which reduces the maximum actuation frequency.
- the valve shuts off in the relevant working temperature range with the frequency and the desired duration specified by the control signal.
- it is advisable, for example, to provide the bore G1 in the area of the pressure piston sealing surface. In principle, however, it can also open into the annular chamber RV (see FIG. 1) or be fitted in any other area of the valve housing VG, provided that flow resistances in the form of orifices, gaps, restrictors, constrictions etc. ensure that between the different volumes or chambers only comparatively slow compensation processes take place.
- the chambers have to be sealed against one another to such an extent that the required shut-off times are achieved and the temperature independence of the drive is still guaranteed.
- Temperature-dependent control of the gap flows is possible if the valve housing VG and the internals (pressure piston DK, reciprocating piston HK) are made from materials with different thermal volume / length expansion coefficients. It can thus be achieved that the gap widths decrease with increasing temperature, which increases the flow resistance accordingly.
- Temperature-controlled flow resistances can of course also be manufactured as discrete components and installed in the corresponding holes G3 or supply lines.
- the drive according to the invention has a number of advantages.
- the drive thus allows symmetrical, cavitation-free switching with very short switching times, extremely short idle times and high actuation frequencies.
- the drive is characterized by a high level of operational reliability.
- the fact that the actuator P is hermetically encapsulated in one of the hydraulic chambers KA3 also contributes to this. A good dissipation of the generated heat and optimal protection against environmental influences are therefore guaranteed.
- the drive is also largely closed, since the electrical connections L of the actuator P are led outside through a pressure-tight, electrically insulating element LD.
- the reciprocating piston of the force / displacement transmission shown in FIG. 2 consists of two parts HK1, HK2, the cup-shaped outer part HKl, which is open on the valve needle side and rests on the spring SF, is guided with close tolerance in the pressure piston bore ZY.
- This is the basis for the cup-shaped inner piston part HK2, which is open on the actuator side.
- a screw S connects the inner part HK2, which can be moved transversely to the stroke direction, with the valve needle VN. Both parts can also be soldered or welded.
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4442649 | 1994-11-30 | ||
DE4442649A DE4442649C2 (en) | 1994-11-30 | 1994-11-30 | Electro-hydraulic drive |
PCT/DE1995/001702 WO1996017165A1 (en) | 1994-11-30 | 1995-11-30 | Electrohydraulic drive |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0795081A1 true EP0795081A1 (en) | 1997-09-17 |
EP0795081B1 EP0795081B1 (en) | 1998-05-27 |
Family
ID=6534560
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95940120A Expired - Lifetime EP0795081B1 (en) | 1994-11-30 | 1995-11-30 | Electrohydraulic drive |
Country Status (5)
Country | Link |
---|---|
US (1) | US5875632A (en) |
EP (1) | EP0795081B1 (en) |
JP (1) | JPH10509790A (en) |
DE (2) | DE4442649C2 (en) |
WO (1) | WO1996017165A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6345771B1 (en) | 2000-06-30 | 2002-02-12 | Siemens Automotive Corporation | Multiple stack piezoelectric actuator for a fuel injector |
US6400066B1 (en) | 2000-06-30 | 2002-06-04 | Siemens Automotive Corporation | Electronic compensator for a piezoelectric actuator |
US6499471B2 (en) | 2001-06-01 | 2002-12-31 | Siemens Automotive Corporation | Hydraulic compensator for a piezoelectrical fuel injector |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19743669A1 (en) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Fuel injection valve for motor vehicle IC engine |
DE19818475C2 (en) * | 1998-04-24 | 2001-05-31 | Siemens Ag | Fluid seal assembly and method of sealing |
DE19821768C2 (en) * | 1998-05-14 | 2000-09-07 | Siemens Ag | Dosing device and dosing method |
US6291928B1 (en) * | 1998-12-16 | 2001-09-18 | Active Control Experts, Inc. | High bandwidth, large stroke actuator |
DE19939487A1 (en) * | 1999-08-20 | 2000-10-19 | Bosch Gmbh Robert | Control valve for liquid, e.g. for diesel injectors, has piezoactor and hydraulic transmission consisting of two pistons enclosing hydraulic chamber (6') is activated by which is filled with silicone |
DE19950760A1 (en) † | 1999-10-21 | 2001-04-26 | Bosch Gmbh Robert | Fuel injection valve esp. for fuel injection systems of IC engines with piezo-electric or magneto-strictive actuator and valve closing body operable by valve needle working with valve |
DE10141135A1 (en) * | 2001-02-22 | 2002-09-05 | Continental Teves Ag & Co Ohg | Hydraulic valve with smooth piezoelectric actuation, for anti-skid vehicle braking system, includes resiliently-deformable thrust transmission system |
DE50206891D1 (en) | 2001-02-22 | 2006-06-29 | Continental Teves Ag & Co Ohg | VALVE, ESPECIALLY FOR HYDRAULIC MOTOR VEHICLE BRAKING SYSTEMS |
US6766965B2 (en) | 2001-08-31 | 2004-07-27 | Siemens Automotive Corporation | Twin tube hydraulic compensator for a fuel injector |
DE10148874C2 (en) * | 2001-10-04 | 2003-12-24 | Siemens Ag | Nozzle device, in particular for fuel injection |
DE10149286C2 (en) | 2001-10-05 | 2003-12-11 | Siemens Ag | Nozzle device, in particular for fuel injection |
DE10248433B4 (en) * | 2002-10-17 | 2015-01-15 | Cummins Ltd. | Device for conveying media, in particular injection device for internal combustion engines of motor vehicles |
JP4270294B2 (en) * | 2007-03-05 | 2009-05-27 | 株式会社デンソー | Fuel injection valve |
US8683982B2 (en) | 2010-08-10 | 2014-04-01 | Great Plains Diesel Technologies, L.C. | Programmable diesel fuel injector |
DE102012213827A1 (en) | 2012-08-03 | 2014-02-06 | Röchling Automotive AG & Co. KG | Ventilation box for actuators |
EP2954569A4 (en) | 2013-02-06 | 2016-11-02 | Great Plains Diesel Technologies L C | Magnetostrictive actuator |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3501099A (en) * | 1967-09-27 | 1970-03-17 | Physics Int Co | Electromechanical actuator having an active element of electroexpansive material |
DE2711393A1 (en) * | 1977-03-16 | 1978-09-21 | Bosch Gmbh Robert | FUEL INJECTOR |
DE4005774A1 (en) * | 1990-02-23 | 1991-08-29 | Bosch Gmbh Robert | IC engine fuel-injection nozzle - has coaxial thrust pins with fingers passing between each other and supporting springs |
JPH04175533A (en) * | 1990-11-05 | 1992-06-23 | Nissan Motor Co Ltd | Displacement magnifying mechanism for piezoelectric actuator |
DE4306073C1 (en) * | 1993-02-26 | 1994-06-01 | Siemens Ag | Metering system for dosing of fluids with injection valve for IC engine - has piston acting on closing unit, and spring with actuator acting on large dia. piston moving in cylinder |
DE4406522C1 (en) * | 1994-02-28 | 1995-07-13 | Siemens Ag | Electrohydraulic drive element for e.g. injection valve |
-
1994
- 1994-11-30 DE DE4442649A patent/DE4442649C2/en not_active Expired - Fee Related
-
1995
- 1995-11-30 US US08/849,565 patent/US5875632A/en not_active Expired - Lifetime
- 1995-11-30 DE DE59502365T patent/DE59502365D1/en not_active Expired - Lifetime
- 1995-11-30 EP EP95940120A patent/EP0795081B1/en not_active Expired - Lifetime
- 1995-11-30 WO PCT/DE1995/001702 patent/WO1996017165A1/en active IP Right Grant
- 1995-11-30 JP JP8518051A patent/JPH10509790A/en not_active Ceased
Non-Patent Citations (1)
Title |
---|
See references of WO9617165A1 * |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6345771B1 (en) | 2000-06-30 | 2002-02-12 | Siemens Automotive Corporation | Multiple stack piezoelectric actuator for a fuel injector |
US6400066B1 (en) | 2000-06-30 | 2002-06-04 | Siemens Automotive Corporation | Electronic compensator for a piezoelectric actuator |
US6650032B2 (en) | 2000-06-30 | 2003-11-18 | Siemens Automotive Corporation | Electronic compensator for a piezoelectric actuator |
US6499471B2 (en) | 2001-06-01 | 2002-12-31 | Siemens Automotive Corporation | Hydraulic compensator for a piezoelectrical fuel injector |
Also Published As
Publication number | Publication date |
---|---|
DE4442649C2 (en) | 1996-10-24 |
EP0795081B1 (en) | 1998-05-27 |
US5875632A (en) | 1999-03-02 |
JPH10509790A (en) | 1998-09-22 |
WO1996017165A1 (en) | 1996-06-06 |
DE4442649A1 (en) | 1996-07-18 |
DE59502365D1 (en) | 1998-07-02 |
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