Patent Grant
8038119
This application is a U.S. national stage application of International Application No. PCT/EP2004/052130 filed Sep. 10, 2004, which designates the United States of America, and claims priority to German application number 103 42 308.7 filed Sep. 12, 2003, the contents of which are hereby incorporated by reference in their entirety.
The invention relates to a metering device, especially with an actuator unit as a drive for a valve in a common-rail diesel injector.
Mechanical tolerances, temperature-related and pressure-related changes in length, the effects of aging, especially in a PMA (Piezoelectric Multilayer Actuator), referred to below as a “piezoactuator” in a fluid valve, have a direct effect on the opening stroke of the fluid valve connected to the piezoactuator and thereby on the metered quantity. Conventional methods used to compensate for temperature-related changes in length to the piezoactuator based on suitable combinations of materials however present serious stability and manufacturing problems.
The elongation ratio of the piezoactuator which can be achieved by the inverse piezoelectric effect in high-performance ceramics as a result of the application of a maximum field strength of appr. 2 KV/mm permissible for continuous operation only amounts to 1.2-1.4 promille (that is 1.2-1.4 pm elongation per 1 mm length of the piezoactuator). For a typical length of piezoactuator of appr. 40 mm and a piezolayer spacing of 80 μm at 160V applied voltage, the inverse piezoelectric effect produces an elongation of maximum 56 μm. Thus if there is only a minimal relative deviation in the effective coefficient of thermal expansion of appr. 1*10−6 1/K over the length of the piezoactuator of 40 mm between the piezoactuator and the housing in which the piezoactuator is installed, in the range of temperatures of 40° C. to 140° C. relevant to automotive technology, this leads to a deviation of the reference surfaces relevant for valve operation of −2.4 μm to +4.8 μm or in total to 7.2 μm, and relative to the elongation of the piezoactuator to a variation bandwidth of up to 13%.
In addition the complex process steps in manufacturing, starting with the construction of the piezoactuator ceramics through to the polarization process, lead to component tolerances which make it difficult to keep the temperature expansion of the piezoactuator within a sufficiently narrow field of tolerances.
Since the piezoactuator is a component with a domain structure and hysteresis the temperature expansion coefficient is heavily dependent on the polarization state and the previous history of mechanical and electrical stress on the piezoactuator. The dependency of the length of the piezoactuator on temperature is non-linear. The coefficient of thermal expansion can assume values for the same piezoactuator ranging from −5*10−6 1/K up to +7*10−6 1/K [1].
The positive change in length caused by the electrical charging of the piezoactuator is used in current common rail diesel injectors to close a sealing element. For reasons of tolerance in this case a “thermal gap”, that is a safety margin of typically 3-5 pm between the freely-moveable end of a piezoelectric actuator unit (PAU) which is embodied as a plunger or which is rigidly mechanically coupled to a plunger and the sealing element is provided. The PAU consists of an upper end cap which is mechanically rigidly supported and which contains at least one whole through which the electric connections of the piezoactuator can be routed outwards, a lower end cap which is embodied as a plunger or which is mechanically rigidly coupled to a plunger, the piezoactuator and a tubular spring into which the piezoactuator is welded under a pre-tensioning pressure of appr. 600N-800N between the two end caps. It is not possible to ideally strike a thermal balance between the actuator housing and the PAU. The safety margin is used, in the event of a greater thermal expansion of the PAU relative to the actuator housing, so that the sealing element is opened and there is continuous leakage through the servo valve as a result. However the fluctuations in the PMA temperature coefficients make it clear that even such a margin is not always sufficient.
Directly after the injector is switched off (the motor vehicle or engine is switched off) units of the injector are at high temperature. The associated thermal expansion of the piezoactuator relative to the housing which cannot be perfectly tuned can lead to the thermal margin being exceeded and the sealing element being opened despite lack of piezo activation, particularly if in the off state no opposing force F0 caused by the fluid pressure can operate on the sealing element any longer. The sealing element thus remains open in the switched-off state of the engine.
The fluid pressure which is exerted on the sealing element from the other direction can however subsequently in the switched-on state of the injector reach a pressure of up to 2000 bar and give rise to forces or opposing forces of up to 600 N. During injector operation these forces ensure a defined closure of the sealing element despite an overextension of the actuator. An internal high-pressure pump in the motor vehicle, when another attempt is made to start the engine, and thereby the injector, is however no longer in a position if the injector is still hot, to build up the necessary pressure in order to close the sealing element so that this leads to malfunctions of the injector.
An actuator unit A in accordance with the prior art is shown in
In this layout a stronger thermal expansion of the piezoactuator 2, because of its attachment via the end cap 7 to the fixed end of the housing 1 leads to an extension of the piezoactuator in the direction of the valve seat 12.
It should however be pointed out that thermal changes are not short term processes in the range of below 10 ms but take seconds or minutes to occur. This type of slow expansion of the actuator 2 can however be balanced out by a hydraulic compensation element X, as shown in
The hydraulic compensation element X however exhibits a stiffness comparable with a rigid body when force is applied to it for short periods, in which case despite this stiffness the hydraulic compensation element or a component of the hydraulic compensation element which is connected indirectly or directly to the piezoactuator gives way by a negligible amount. However these distances, which are in themselves negligible, add up with multiple activation of the piezoactuator so that the hydraulic compensation aliment or the component of the hydraulic compensation element is shifted upwards by the maximum deflection of the piezoactuator and thereby the gap between the piston 4 and the sealing element 6 is enlarged such that the piston no longer reaches this sealing element on repeated actuation of the piezoactuator. Opening the sealing element 6 is no longer possible in this case.
The object of the invention is thus to specify a device and/or a method by which a predetermined distance between a sealing element and an actuator unit can be constantly maintained.
The object is achieved by a metering device comprising:
This metering device provides the advantage that even with fluctuating operating temperatures a smallest possible distance between the sealing element and the actuator is maintained. This always guarantees an opening of the sealing element by the actuator, with the compensation for the temperature expansion of the actuator able to be achieved by the hydraulic compensation element being able to be maintained.
In the method for manufacturing the inventive metering device the first end cap is moved past the stop and using a subsequent second rotation of the end cap and the stop they are opposite each other so that, with a movement of the end cap in the direction of the hydraulic compensation element the end cap hits the stop and this movement is blocked.
The method corresponds to a simple key-lock relationship between the end cap and the stop. It is especially suitable and safe for simple manufacturing of the metering device.
The key-lock relationship preferably represents a bayonet lock.
The actuator is preferably a piezoactuator.
Further benefits and a more detailed explanation of the invention are given on the basis of the following exemplary embodiments.
The Figures show:
The hydraulic compensation element 13 can be installed in the metering device in a simple manner between an end of the housing 1 and the piezoactuator 2, a process which advantageously simplifies the integration into or modification of existing injectors. The hydraulic compensation element is preferably fixed to the inner wall of the housing 1.
The hydraulic compensation element 13 is basically rigid in relation to the brief application of a force and simultaneously gives way to a thermally-induced change in length of the actuator.
The hydraulic compensation element 13 preferably features at least one hydraulic chamber 13c, a hollow-cylinder-shaped housing 13a and a piston 13b, with the piston 13b or the housing 13a being connected to the second end cap 7′ of the actuator 2. The hydraulic chamber 13c lies between axially effective pressure surfaces of the piston and the housing in each case and between at least two clearances 13g, which are embodied between the piston and the housing. The axially effective pressure surfaces are essentially aligned axially. The term “axial” is understood as being the direction of the force effects and transmissions of the piezoactuator or of the hydraulic compensation element. “Axial” is however also taken to mean “essentially axial”. The clearances 13g basically have a strongly fluid-restricting effect. The hydraulic compensation element can be filled under pressure with a fluid, preferably silicon oil. It his preferred that the hydraulic compensation element features an axial through-hole 13d through which the leads 17 to the piezoactuator 2 can be routed. In particular the piston 13b is provided with this through-hole 13d.
The piston 13b and the housing 13a, with a slow thermally induced length change of the actuator are able to be displaced relative to each other without any force being exerted so that the hydraulic compensation element gives way during this time. With a brief application of a force the piston only moves by a negligible amount relative to the housing however so that the hydraulic compensation element can be considered as being rigid.
It is also preferred that the hydraulic compensation element for increased rigidity features several, especially two, hydraulic chambers. In this case the housing 13a a is expanded by a part to form a further hydraulic chamber similar to the first hydraulic chamber 13c between the piston 13b and the housing 13a as previously stated. The hydraulic compensation element would operate bidirectionally in this case.
The hydraulic compensation element 13 is provided with membranes 13f on its two end faces which preferably are attached to the piston 13b and the housing 13a. Through the membranes storage volumes 13e are embodied between the housing, the membranes and the piston. The membranes can also expand at increased temperature so that they can compensate for a thermal volume change of the fluid in the hydraulic compensation element. They each preferably have coefficients of thermal expansion which differ from those of the housing and/or the piston. The membranes of preferably embodied as annular flat membranes.
It is preferable for the hydraulic compensation element to be hydraulically connected via a hole in the housing 13a of the hydraulic compensation element with a compensation store in order to compensate for an increasing volume change of the fluid located in the hydraulic compensation element at increased temperature even better than with the previously mentioned membranes 13f and storage volumes 13e. The compensation store preferably features a membrane which can be implemented as an elastic sleeve and a storage volume enclosed below it. The elastic sleeve of the compensation store is preferably arranged on the lateral surface of the housing 13a. At increased temperature of the fluid the membrane expands so that the fluid in the hydraulic compensation area has a greater volume at its disposal and thus no disruptive net force effect between the piston and the housing arises. To provides sufficient space for the expansion of the elastic sleeve of the compensation store between the housing 13a of the hydraulic compensation element and the inner wall of the housing 1 of the metering device, it is preferred that the housing 13a of a hydraulic compensation element is mechanically connected by means of a spacer to the inner wall of the housing 1 of the metering device.
The compensation store can however also be implemented in the form of an external hydrostore.
The piston 13b or the housing 13a are also preferably provided with axial holes, which connect the storage volume 13e to the hydraulic chambers 13c, in order to facilitate the fluid flowback during the blanking interval of the piezoactuator into the hydraulic chambers and into the storage volume. The openings of the holes are provided in such cases with non-return valves known as flapper valves, so that the opening of the holes close during a brief deflection of the piezoactuator and thereby the hydraulic compensation element remains rigid when a force is briefly applied to it. During the planking intervals of the piezoactuator the flapper valves open in these cases as a result of a pressure drop in the hydraulic chambers 13c.
With a hydraulic compensation element 13 of the type presented a smooth movement of the piston 13b relative to the housing 13a of the hydraulic compensation element must be guaranteed since otherwise its desired compensation function would not be provided or would only be provided to a limited extent. In this case clearance dimensions and tolerances of piston and housing are to be selected so that positive play is available. For a smooth and jolt-free movement between piston and housing a sufficient surface quality of the outside surface of the piston and/or the inner wall of the housing, especially a slight surface roughness as can for example be produced by grinding, and to avoid tilting, a suitable guide length, are advantageous. Compliance with the clearance dimensions of piston and cylinder is ensured such that not only in the assembly state but also in stationary and non-stationary operation of the hydraulic compensation element no sticking or friction-related slipping (stick-slip) of the piston in the housing can arise, for example through a stronger thermal expansion of the piston in relation to the housing or a stronger thermal contraction of the housing in relation to the piston. In non-stationary operation in particular and at higher operating frequencies, radial temperature gradients arise because of the high and greatly changing release of heat over time of the piezoactuator with simultaneous cooling by the fuel, which can lead to a differing thermal expansion of piston and cylinder and can result in sticking if the system is not designed correctly. This can be prevented by the following measures:
a.) the piston and the housing consist of the same material or materials with the same coefficients of thermal expansion. To avoid sticking a sufficiently large gap between a piston and cylinder in a range of 10 to 50 μm combined with a fluid of higher basic viscosity in the range of 100 to 1000 Centistokes with a sufficient guide length of the piston in the housing to avoid tilting is to be selected.
b.) If the piston heats up for example more than the housing as a result of a driver element connected to it, such as for example because of the piezoactuator (a not inconsiderable radial temperature gradient arises here) a material is then selected for the piston 3 with a lower thermal expansion which means that the piston does not begin to stick in narrow clearances 13g.
c.) If it can be assumed that the piston 13b, the hydraulic fluid and the housing 13a are always at around the same temperature, the temperature influence on the gap flow between the clearances 13g in the state of the hydraulic system when subjected to a load by the actuator can be compensated for in wide ranges if the piston has a suitably selected higher thermal expansion than the housing. The explanation is to be found in the fact that the viscosity of the hydraulic fluid reduces in accordance with an exponentially with temperature and the volume flow of the hydraulic fluids along the clearances increases exponentially accordingly. The volume flow in this case is proportional to the third power of the width of the clearances which can also be referred to as the size of fit. The size of fit increases linearly with temperature and thus the temperature effects on the size of fit and on the viscosity are opposing.
The housing 1 of the metering device is lengthened when necessary in comparison to the original layout shown in
Despite this the relatively small space requirement of the hydraulic compensation element 13 with maximum rigidity for the metering device is especially advantageous for installation in an injector of a motor vehicle with the usual stringent space requirements in such cases.
The piezoelectric actuator unit PAU mentioned at the start of the description, referred to below as actuator unit A, comprises the arrangement of features which are mechanically indirectly or directly connected to the piezoactuator and features, in addition to the known features from
Below the stop 14 in the direction of the valve unit B a membrane 5 seals piezoactuator 2 against fuel in the metering device, which on opening of the sealing element 6 flows from the inlet 9 through the seat valve 12 to the return 10. The membrane 5 preferably connects the housing 1 to the end cap 3′.
The piezoactuator 2 is preferably also provided with a second upper end cap 7′ which is connected to the hydraulic compensation element. It is preferred that the end cap 7′ has an axial hole 16 for connecting leads 17, to simplify the contacting of the piezoactuator 2 to control electronics (not shown).
A significant element of the metering device is the stop 14, which counteracts a change in the position of equilibrium of the piston 13b of the hydraulic compensation element, and thus also the position of the end cap 3′.
The stop 14 can be seen as a tapering in the internal diameter of the housing 1. In this case the term “internal diameter” or “diameter” is always taken to mean a trans-axial diameter which runs at right angles to the longitudinal axis of the actuator. The stop is preferably penetrated by two holes. The stop allows the actuator to expand in the direction of the sealing element 6, but prevents the end cap 3′ from withdrawing beyond a predefined distance from the sealing element 6. If the piston 3b of the hydraulic compensation element also wishes to remove itself from its position of equilibrium originally set, a force which pushes it back is produced as a result of the inelasticity of the piezoactuator, which after the activation voltage for the piezoactuator has been removed (the blanking interval) once again forces the piston 13b to return to its position of equilibrium originally set.
A fine adjustment of the maximum gap between the plunger 4 of the end cap 3′ and the valve seat 12 can be obtained with the aid of shims. The requirements for the accuracy of this fine adjustment however are very small as a result of the compensating effect of the hydraulic compensation elements.
The stop 14 can be embodied in a plurality of variants. Of significance for an actual embodiment is its installation below the piezoactuator, to allow the expansion of the actuator upwards or in the opposite direction towards the sealing element.
In the manufacturing of the metering device the ears 3′a of the end cap 3′ are especially moved past the cutouts 14a of the stop 14. Subsequently the end cap is rotated so there a pulling back of the end cap means that the ears 3′a can no longer be moved past the stop.
The end cap 3′ is also basically the matching part for the stop 14 so that a key-lock arrangement is basically formed by the two parts. The stop and the end cap thus form a bayonet locking connection.
A further option for embodiment of a stop 14 consists of a direct connection between the plunger 4 and the sealing element 6 of the seat valve 12, so that the plunger also takes over the role of the sealing element. When the end cap is withdrawn the valve seat itself then hits the stop element, since the sealing element or the plunger has a diameter so that it cannot move past the valve seat.
The stop 14 can also be replaced by an additional spring between piston 13b and the fixed support 15. The pre-tensioning of the spring in the manufacturing of the metering device ensures an effective downwards force which operates via the plunger 4 on the sealing element 6 of the valve unit B and operates against a change in the equilibrium position of the piston. This means that the piston is always subject to a reset force, to prevent a shift in the equilibrium position of the piston and guarantee a defined contact between the plunger and the sealing element.
Depending on the embodiment the elasticity of the membrane 5 is also suitable as a reset element for a desired equilibrium position. Welding of the membrane 5 onto the end cap 3′ and onto the housing 1 ensures in this case that the end cap is prevented from turning in the position in which the cutouts 14a and the ears 3′a are opposite each other in the assembled state of the metering device, and the end cap is thereby accidentally pulled past the stop again.
It is preferred that the inventive metering device is used in a common-rail diesel injector.
The followed sources are cited within the context of this document:
| Number | Date | Country | Kind |
|---|---|---|---|
| 103 42 308 | Sep 2003 | DE | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP2004/052130 | 9/10/2004 | WO | 00 | 2/20/2007 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2005/026532 | 3/24/2005 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 2922614 | Nickells | Jan 1960 | A |
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| 4725002 | Trachte | Feb 1988 | A |
| 6953158 | Liskow | Oct 2005 | B2 |
| 20020139863 | Lorraine et al. | Oct 2002 | A1 |
| 20030042325 | D'Arrigo | Mar 2003 | A1 |
| 20030098428 | Mattes | May 2003 | A1 |
| 20030150939 | Lorraine et al. | Aug 2003 | A1 |
| Number | Date | Country |
|---|---|---|
| 198 26 341 | Dec 1999 | DE |
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| 61008462 | Jan 1986 | JP |
| Number | Date | Country | |
|---|---|---|---|
| 20070131884 A1 | Jun 2007 | US |
