EP4013550A1

EP4013550A1 - Dosing system having an adjustable actuator

Info

Publication number: EP4013550A1
Application number: EP20746191.4A
Authority: EP
Inventors: Mario Fließ; Klaus MEHRLE
Original assignee: Vermes Microdispensing GmbH
Current assignee: Vermes Microdispensing GmbH
Priority date: 2019-08-12
Filing date: 2020-07-24
Publication date: 2022-06-22
Also published as: KR20220046559A; DE102019121679A1; CN114173940B; WO2021028197A1; CN114173940A; JP2022543590A; US20220280967A1

Abstract

The invention relates to a dosing system (1) for a dosing material, which dosing system (1) comprises a housing (11) having a nozzle (60) and a feed channel (64) for the dosing material, a discharge element (51) arranged in the housing (11) for discharging dosing material out of the nozzle (60), at least one first actuator (20) coupled to the discharge element (51) and/or the nozzle (60), preferably a piezoactuator (20), and at least one second actuator (30) coupled to the first actuator (20), preferably an expansion material element (30). The second actuator (30) is designed to adjust a position of the at least one first actuator (20) relative to the housing (11), in particular in relation to the discharge element (51) and/or the nozzle (60). The invention also relates to a method for controlling such a dosing system (1).

Description

Dosing system with adjustable actuator

The invention relates to a metering system for a metering substance, which metering system has a housing with a nozzle and a feed channel for metering substance, an ejection element arranged in the housing for ejecting metering substance from the nozzle, at least one first actuator coupled to the ejection element and / or the nozzle, preferably a piezo actuator, and at least one second actuator coupled to the first actuator, preferably an expansion element. The invention also relates to a method for operating such a metering system.

Dosing systems of the type mentioned at the beginning are typically used to selectively deliver a medium to be dosed, ie. H. at the right time, in the right place and in a precisely dosed amount on a target surface. This can be done, for example, by dispensing a metering substance drop by drop via a nozzle of the metering system. In the context of the so-called “microdosing technology”, it is often necessary that very small amounts of the dosing substance are placed on the target surface with pinpoint accuracy and contactless, i.e. without direct contact between the dosing system and the target surface. A typical example of this is the dosage of glue dots, soldering pastes etc. when assembling circuit boards or other electronic elements, or the application of converter materials for LEDs.

Such a contactless process is often referred to as the “jet process”. A metering valve that works according to the jet process is usually referred to as a “jet valve” or “jet valve”. Correspondingly, a dosing system that has at least one such jet valve and possibly also further components can be referred to as a “jetting dosing system”. To dispense the medium from a jetting metering system or jet valve, a movable ejection element can be arranged in the nozzle of the metering system, e.g. B. a plunger. In order to eject metering substance, the ejection element inside the nozzle can be pushed forward in an ejection direction at relatively high speed towards a nozzle opening, whereby a single drop of the medium is ejected from the nozzle. This process is generally referred to below as the ejection process. The ejection element can then be withdrawn again in an opposite retraction direction. The size of the droplets or the amount of medium per droplet are through the structure and the control as well as the effect of the nozzle achieved thereby can be predefined as precisely as possible.

Characteristically - and preferably also within the scope of the present invention - in a jetting dosing system or a jet valve, the dosing substance is "actively" ejected from the nozzle by an (ejecting) movement of the ejection element relative to the nozzle. During the ejection process, an ejection tip of the ejection element comes into contact with the dosing substance to be dispensed and "pushes" or "pushes" the dosing substance out of the nozzle of the dosing system due to the (ejection) movement of the ejection element and / or the nozzle. A jet dosing system thus differs from other dispenser systems in which a movement of a closure element only leads to an opening of the nozzle, with a pressurized dosing substance then exiting the nozzle by itself. This is e.g. B. the case with injection valves of internal combustion engines.

Alternatively or in addition to the movable ejector element, the nozzle of the dosing system, e.g. B. the nozzle of a jet valve, are themselves moved in an ejection or retraction direction. To dispense the dosing substance, the nozzle and an ejector element arranged inside the nozzle can be moved towards or away from one another in a relative movement, the relative movement being able to take place either solely by moving the nozzle or at least partially also by moving the ejector element accordingly.

In order to operate the dosing system, e.g. B. with a jetting metering system to achieve the highest possible metering accuracy, a constant relative movement between the ejector element and the nozzle is required. The amount of metering substance that is dispensed from the nozzle during a respective ejection process depends in particular on a (hydraulically) effective stroke of the ejection element and / or the nozzle, ie z. B. of a distance which the ejection element travels with a respective ejection movement in relation to the nozzle.

The smaller the (hydraulically) effective stroke of a dosing system, the more important it is to arrange the ejector element and the nozzle in the dosing system as precisely as possible. Especially with piezoelectrically operated metering systems, the effective stroke of the ejection element and / or the nozzle is comparatively small, e.g. B. compared to dosing systems with pneumatic actuators. This is why it is especially useful for dosing systems Piezo actuators one of the most important tasks is the precise setup of the entire system, i.e. setting the position between the ejection element and the nozzle.

It is true that piezoelectrically operated dosing systems can be set up or adjusted for the first time before delivery to a customer. For example, the piezo actuator and the ejection element and possibly other components can be arranged and adjusted at the factory in the dosing system in such a way that a certain relative movement of the ejection element relative to the nozzle occurs by means of a deflection of the piezo actuator in order to eject a desired amount of dosing substance during the ejection movement.

However, it has been shown that this one-off adjustment of the dosing system is often not sufficient to achieve a consistently high level of dosing accuracy even when the dosing system is in continuous operation. Depending on the operating situation of the dosing system, there may therefore be considerable deviations between a desired target amount and an actual actual amount of dosing substance expelled.

On the one hand, this can be due to the fact that the frequency of the dosing substance delivery, i.e. the actuator frequency, can fluctuate greatly depending on the dosing requirement during operation. The different load situations of the actuator can lead to different power losses, especially in the case of piezo actuators, and the respective temperature of the piezo actuator can fluctuate. This can subsequently lead to thermal elongation of the piezo actuator and possibly other components of the dosing system. Due to a coupling between the piezo actuator and the ejector element, the thermal longitudinal expansion of the piezo actuator can also undesirably change the (hydraulically) effective stroke of the ejector element and thus influence the metering accuracy.

On the other hand, the moving components of the dosing system can be subject to wear and tear during operation. For example, due to frequent contact with the nozzle, an ejection tip of the ejection element can wear out at least in areas such that a desired (hydraulically) effective stroke of the ejection element is no longer reliably achieved. This can also change the amount of dosing substance dispensed.

Furthermore, it may be necessary from time to time that worn components of the dosing system have to be replaced, e.g. B. a worn ejector element. In order to achieve a high level of dosing accuracy even after the replacement, a new Adjustment of the dosing system required. This relatively complex process often cannot be carried out with the necessary precision by a user of the dosing system, so that undesired changes in the required dosing process can occur.

However - as mentioned at the beginning - a highly precise dosing substance delivery is desired, especially in microdosing technology. It is therefore an object of the present invention to reduce the adverse effects described above. This object is achieved by a metering system according to patent claim 1 and by a method for controlling such a metering system according to patent claim 7.

A metering system according to the invention for a liquid to viscous metering substance comprises a housing, the housing having a nozzle with a nozzle opening and a feed channel for feeding metering substance into the nozzle. An ejection element for ejecting the dosing substance from the nozzle and at least one first actuator coupled to the ejection element and / or the nozzle are arranged in the housing of the dosing system. The first actuator can preferably be a piezo actuator, in particular a controllable piezo stack, even if, in principle, other types of actuators are also conceivable. Particularly preferably, the first actuator can be a piezo stack hermetically sealed in an actuator housing. For the sake of better understanding, the invention is explained below using a piezoelectrically operated metering system, that is to say that the first actuator is a piezo actuator. The dispensing of the metering substance from the metering system according to the invention can take place according to one of the principles explained at the beginning. Correspondingly - as is usually the case - an ejection element movable at relatively high speed for ejecting the dosing substance from the nozzle can be arranged in the nozzle of the dosing system (in particular in the area of the nozzle, e.g. shortly before an outlet opening). Alternatively or additionally, as mentioned, the outlet opening, so z. B. the nozzle of the metering system can be made movable. In the following it is assumed that the dosing substance is dispensed by means of a movable ejection element, as is preferred, e.g. B. with a plunger. However, the invention is not intended to be limited thereto. The metering system according to the invention can particularly preferably operate according to the “jet process”. In particular, the metering system can therefore include at least one jet valve. In this regard, reference is made to the definition given at the beginning.

The first actuator of the dosing system is functionally coupled at least at times to the ejection element or the nozzle. The coupling takes place in such a way that the forces and movements exerted by the first actuator are passed on to the ejection element (or the nozzle) in such a way that a desired, preferably vertical, movement of the ejection element and / or the nozzle for dispensing the metering substance from the nozzle is derived from this results. The first actuator can directly, i. H. act on the ejection element without further movement-imparting components. However, it is preferred that the metering system comprises a movement mechanism in order to transmit a deflection of the first actuator over a certain distance (that is, indirectly) to the ejection element. This will be explained later.

According to the invention, there is at least one further second actuator in the housing of the metering system, which is coupled to the first actuator, in particular to the piezo actuator. The second actuator is designed to set a position of the first actuator, for example the piezo stack encapsulated in an actuator housing, relative to the housing, in particular with respect to the ejection element and / or the nozzle. The first actuator and the second actuator can be controlled separately for this purpose. The second actuator can therefore also be referred to as a positioning actuator for positioning the first actuator coupled to the ejection element and / or the nozzle. The coupling can take place in such a way that the positioning actuator only rests and / or rests on the first actuator. This means that the positioning actuator is in operative contact with the first actuator, but a fixed connection between the two components is not absolutely necessary. The positioning actuator can in principle be any type of actuator, e.g. B. a controllable piezo actuator, for example again a piezo stack encapsulated in its own actuator housing, a shape memory actuator, a magnetistictive actuator or the like. The second actuator is preferably a different type of actuator than the first actuator, since the second actuator does not, in principle, have to work at such high expansion speeds as the first actuator.

The positioning actuator can preferably comprise at least one expansion element. The second actuator can particularly preferably be implemented by means of an expansion element. Accordingly, the expansion element can be designed to a position of the at least one first actuator relative to the housing, in particular with respect to the ejection element and / or the nozzle to adjust. The advantage of such an expansion element lies in a better ratio between the overall height (and also the volume) and the usable maximum stroke for comparable forces. The invention is described below, without being restricted thereto, on the basis of a second actuator implemented by means of an expansion element. In other words, unless otherwise mentioned, the first actuator (for moving the plunger and / or the nozzle) is only briefly referred to as “actuator” or “piezo actuator”, with the second (positioning) actuator is referred to as “expansion element” without loss of generality.

Under an expansion element or expansion material working element, according to the general definition, an expansion material having e.g. B. understood with an expansion material filled, actively expandable element, which can also be referred to as a "thermal expansion actuator". The expansion element can include other components in addition to the expansion material, such. B. a housing enclosing the expansion material and a working piston, as will be explained later. As is generally customary, the expansion material is preferably designed such that a change in temperature of the expansion material leads to a change in volume of the expansion material. A specific or directed movement (a stroke) can be generated by means of a corresponding design of the expansion element via the change in volume of the expansion material. The extent of the movement generated (as usual) can be roughly proportional to the change in volume of the expansion material.

In order to generate a certain stroke by means of the expansion element, the expansion element can be controlled and / or regulated via a control unit of the dosing system. To control and / or regulate the expansion element, in particular a temperature of the expansion element is controlled and / or regulated within the scope of the invention. Further details on the expansion element and the control unit will be given at a later date.

According to the invention, the expansion element is designed for this purpose and is arranged in the metering system in such a way that a specific position of the (first) actuator can be set relative to the housing of the metering system. This means that a desired spatial arrangement of the actuator, in particular the piezo actuator, within the housing can be achieved by means of the expansion element. In particular, the position of the actuator be actively changed in the housing by means of the expansion element during operation, z. B. during a respective ejection movement and / or a respective retraction movement of the ejection element. In other words, the actuator can be moved in the housing by the expansion element, at least to a small extent.

The expansion element is accordingly arranged in the metering system in such a way that the stroke generated by means of the expansion element can predominantly be completely transferred to the actuator, in particular the piezo actuator, and used for positioning the actuator.

The expansion element is designed in particular and arranged in the dosing system in order to set the position of the (first) actuator, in particular the piezo actuator, in relation to the ejection element and / or the nozzle of the dosing system. Particularly preferably, a position of a pressure piece of the actuator, which transfers the forces generated by the actuator (directly or indirectly) to the ejection element and / or the nozzle, can be set and / or changed in relation to the ejection element and / or the nozzle by means of the expansion element . For example, depending on the specific structure of the metering system, the expansion element can be used to set a certain distance between the pressure piece of the actuator and a nozzle opening of the nozzle. In the same way, a distance between the pressure piece of the actuator and the ejection element can also be set.

Advantageously, the expansion element can be used to set a specific target arrangement between the (first) actuator and the ejection element or the nozzle, so that a specific amount of dosing agent is ejected from the nozzle by a respective deflection of the actuator. The dosing system according to the invention thus comprises with the expansion element an additional actuator for "precise" positioning of the actuator in the housing, so that, for. B. the high dynamics of the piezo actuator can be used almost completely for the actual dosing function of the dosing system.

A particular advantage is that such a target arrangement or target position of the actuator can be kept largely constant even when the metering system is in operation. On the one hand, the expansion element can be used to perform thermal compensation functions, which is also referred to as “thermal compensation”. For example, thermal changes in length of the Actuator, in particular the piezo actuator, can be compensated for by operating the expansion element in opposite directions, so that a position of the actuator relative to the ejection element and / or the nozzle can be kept constant during operation.

On the other hand, the expansion element can also perform mechanical compensation functions, e.g. B. to compensate for operational wear of components of the dosing system. For example, the actuator, in particular the piezo actuator, can be routinely (re) positioned in the housing by means of the expansion element during operation in such a way that the target arrangement remains largely constant during operation despite signs of wear and tear on particularly moving components (such as the ejector element) .

Furthermore, the expansion element can advantageously also be used to (re) set the entire system correctly after a temporary interruption in the metering operation. This makes it z. B. possible that if necessary, only one worn component of the dosing system needs to be replaced, z. B. a plunger instead of a fitted assembly. The desired arrangement can then be restored by means of the expansion element. Therefore, with the metering system according to the invention, the wear-related costs can be reduced compared to known metering systems.

On the basis of the advantageous effects explained above, the metering accuracy in the metering system according to the invention can be considerably improved compared to known metering systems.

In a method according to the invention for controlling a metering system for a liquid to viscous metering substance, the metering system comprises a housing, the housing having a nozzle and a feed channel for metering substance. The dosing system further comprises an ejector element arranged in the housing for ejecting dosing substance from the nozzle, at least one first actuator coupled to the ejector element and / or the nozzle, preferably a piezo actuator, and at least one second actuator coupled to the first actuator, preferably an expansion element. The second actuator is controlled and / or regulated by means of a control unit in such a way that a position of the at least one first actuator relative to the housing, in particular in relation to the ejection element and / or the nozzle, is set. To position the (first) actuator in the housing, an expansion length or expansion of the expansion element can be controlled and / or regulated in at least one direction. Particularly preferably, the expansion length of the expansion element can be controlled and / or regulated via the temperature of the expansion element. This will be explained in detail later.

Further, particularly advantageous configurations and developments of the invention emerge from the dependent claims and the following description, whereby the independent claims of one claim category can also be developed analogously to the dependent claims and exemplary embodiments of another claim category and in particular also individual features of various exemplary embodiments or variants can be combined to new embodiments or variants.

The second actuator, in particular the expansion element, is preferably designed and arranged in the housing in order to set a position of the ejection element in relation to the nozzle of the dosing system via the position of the (first) actuator, in particular the piezo actuator. In particular, a distance between an ejection tip of the ejection element and a nozzle opening of the nozzle can be set by means of the expansion element via the position of the (first) actuator.

In a corresponding method for controlling the dosing system, the second actuator, in particular the expansion element, can therefore be controlled and / or regulated in such a way that a position of the ejection element is set in relation to the nozzle of the dosing system. The expansion element can preferably be controlled and / or regulated in such a way that a certain distance between the ejection tip of the ejection element and the nozzle opening of the nozzle is set via the position of the (first) actuator, in particular the piezo actuator.

In a preferred method for controlling the metering system, the control and / or regulation of the second actuator, in particular the expansion element, can be carried out such that a temperature of the second actuator, preferably the expansion element, in particular a temperature of the expansion material, is controlled and / or regulated. For this purpose, at least one heating device assigned to the expansion element and / or at least one cooling device assigned to the expansion element can preferably be controlled and / or regulated, as will be explained later. Particularly preferred can be a Temperature of the expansion element can be set so that a certain stroke of the expansion element is generated in order to arrange the actuator, in particular the piezo actuator, and / or the ejection element in a certain position in the housing.

As mentioned, the ejection element can preferably be coupled to the (first) actuator, in particular to the piezo actuator, by means of a movement mechanism. The ejection element is also referred to synonymously as the ram. The invention is described below, without being restricted thereto, on the basis of a metering system with a movement mechanism. The movement mechanism can comprise a coupling element in order to transmit the movements of the actuator to the ejection element. The coupling between the actuator, or the piezo actuator, in particular its pressure piece, and the movement mechanism and / or between the movement mechanism and the ejector element is preferably not a fixed coupling, ie. H. the respective components are preferably not screwed, welded, glued, etc. to one another for coupling.

Particularly preferably, the coupling element can have a translation element, for. B. a lever system with a tiltably mounted lever or the like to increase a deflection of the actuator by a certain factor. In particular, the transmission element can be designed to generate a specific transmission ratio between a deflection or a stroke of the actuator and a resulting movement or a stroke of the plunger. On the one hand, this means that a deflection of the (first) actuator can be translated into a specific, desired stroke of the plunger by means of the translation element.

On the other hand, the translation element can advantageously also be used to transmit a change in position of the (first) actuator, preferably caused by the expansion element, to the ejection element to a greater extent. This means that a relatively large change in position of the ejector element can be brought about by means of a comparatively small change in position of the actuator through the expansion element.

The second actuator, in particular the expansion element, is preferably designed and arranged in the housing to move the ejection element into a suitably defined “adjust position” of the ejection element during a defined operating state of the dosing system. The operating state preferably corresponds to the greatest possible deflection of the (first) actuator, in particular the piezo actuator, provided during operation. In order to set the “adjust position”, a change in position of the (first) actuator can preferably be transmitted to the ejector element by means of the movement mechanism.

The “adjust position” is here preferably characterized or defined in that the ejection element, in particular the ejection tip of the plunger, is pressed into the nozzle with a certain force. The force exerted by the plunger on the nozzle in the adjust position is referred to as the push-in force or the sealing force. In the adjust position, the plunger can be pressed into a sealing seat of the nozzle in such a way that a sealing area of the nozzle is preferably completely filled by the plunger. The sealing area is understood to mean an area in the sealing seat of the nozzle which is directly adjacent to the nozzle opening in the interior of the nozzle (nozzle chamber). In the sealing area, the plunger and the nozzle can cooperate in a sealing manner, in particular in that the plunger is pressed against the sealing seat.

In the adjust position, the tappet preferably builds up a certain sealing force with respect to the nozzle. The sealing force of the ejection element can be at least 1 mN, preferably at least 1 N, preferably at least 10 N, for example.

In a preferred method for controlling the metering system, the second actuator, in particular the expansion element, can therefore be controlled and / or regulated in such a way that the ejection element is brought into the adjust position of the ejection element during the defined operating state of the metering system. The expansion element can preferably be controlled and / or regulated in such a way that the ejection tip of the ejection element is pressed against the nozzle with a certain sealing force when the piezo actuator is maximally provided during operation.

A “(hydraulically) effective stroke” of the plunger can advantageously be precisely set and maintained via the adjust position of the ejector element, the metering accuracy of the metering system being able to be further improved. This is explained below.

In a preferred method for controlling the metering system, the deflection of the (first) actuator (actuator deflection), in particular the electrical control voltage applied to the piezo actuator, can be added during a respective ejection process can be used to move the plunger in the direction of the nozzle from an initial ejection position until it has reached “full contact”. The full contact is defined by the fact that the ejection tip of the plunger comes into operative contact with the nozzle, preferably completely circumferentially. In particular, when there is full contact, the plunger can rest against the sealing seat of the nozzle in such a way that the nozzle opening is closed.

The stroke movement (the distance covered) that the plunger executes during each ejection process up to full contact in relation to the nozzle is called the “(hydraulically) effective stroke” of the plunger. The (hydraulically) effective stroke is therefore a portion of a maximum actuator deflection provided during operation or a portion of a maximum electrical control voltage applied to the piezo actuator during operation, which can be used for ejecting the dosing substance and therefore has an influence on the dosing substance delivery.

On the other hand, the actuator deflection can also be used at least partially to push the plunger further in the direction of the nozzle beyond full contact. This defined portion of the total actuator deflection or the portion of the maximum provided electrical control voltage of the piezo actuator by which the plunger is pushed a certain minimum further in the direction of the nozzle starting from full contact is referred to as the sealing position actuator deflection, as will be explained later. A specific sealing force of the plunger can preferably be built up by means of the sealing position actuator deflection.

With an "ideal" very stiff metering system, a position of the plunger after full contact can remain largely constant with a progressive actuator deflection or with a further increase in the electrical control voltage applied to the piezo actuator (piezo actuator control voltage). That is, the plunger is pressed against the nozzle with an increasing force by means of the sealing position actuator deflection, whereby a certain sealing force of the plunger can be built up.

Depending on the configuration of the dosing system, e.g. B. depending on the nature of the materials used, the sealing position actuator deflection can also lead to a slight elastic deformation of components of the dosing system. For example, the nozzle insert, the plunger, connecting elements of the fluidic unit such as e.g. The lever, or a combination of these or other components, can be elastically deformed. Correspondingly, with an "ideal" one cannot completely stiff dosing system can still slightly change a position of the plunger after full contact due to the progressive actuator deflection or by increasing the piezo actuator control voltage, especially in the nano or micrometer range. However, even with such a non-rigid metering system, a large part of the sealing position actuator deflection can preferably be transferred to the tappet and used to set a sealing force of the tappet.

Regardless of the specific configuration of the dosing system, a maximum deflection of the actuator that is provided during operation, in particular a maximum control voltage applied to the piezo actuator during operation, can be "distributed" proportionally between a (hydraulically) effective stroke of the tappet on the one hand and the build-up of a sealing force of the tappet on the other. are, in particular by means of a corresponding control of the expansion element.

The adjust position of the plunger can advantageously be set by an interaction of the expansion element and (first) actuator in such a way that the plunger exerts a certain sealing force on the nozzle in the adjust position. The following applies: the greater the sealing force of the plunger in the adjust position, the greater the proportion of the sealing position actuator deflection required for this in the maximum actuator deflection provided during operation or in the maximum intended piezo actuator control voltage. The portion of the actuator deflection or the piezo actuator control voltage that can be used for the (hydraulically) effective stroke of the tappet will be reduced accordingly. The (hydraulically) effective stroke of the tappet can therefore be set precisely by setting the adjust position of the tappet, in particular by setting the sealing force. A further improved metering accuracy can advantageously be achieved in this way.

In order to be able to move the ejection element into the adjust position, the dosing system, as mentioned, preferably comprises at least one heating device assigned to the second actuator, in particular the expansion element, and / or at least one cooling device assigned to the second actuator, in particular the expansion element. The dosing system particularly preferably further comprises a control unit for controlling and / or regulating the heating device and / or the cooling device. The heating device can preferably use electrical energy for heating the expansion material or the expansion material element. For example, at least one resistance heating element in the form of a heating film could be arranged on an outer surface (outside) of the expansion element, e.g. B. on a housing of the expansion element. Alternatively or additionally, at least one resistance heating element could be arranged in the expansion material itself. The heating device is preferably designed to uniformly heat all of the expansion material of the expansion element to a specific target temperature.

The cooling device can preferably comprise at least one gaseous and / or liquid fluid for cooling the expansion element or the expansion material. Preferably, the outside of the expansion element can be acted upon at least in some areas with a cooling medium, for. B. in that a housing of the expansion element is directly flown or blown with cooling medium. For this purpose, the cooling device in the metering system can comprise a cavity (cooling area) which surrounds the expansion element and can be flooded with cooling medium. Furthermore, the cooling device can comprise flow-directing elements in order to specifically apply cooling fluid to individual subregions of the expansion element. However, essentially the entire outside of the expansion element can also be actively cooled. The cooling device can furthermore comprise feed and discharge devices in order to introduce the cooling medium into the metering system, in particular into the cooling area, or to remove it again.

The cooling medium is preferably designed in order to be able to cool the expansion element as quickly as possible to a certain temperature value. This temperature value can also be above room temperature and / or above a “parasitic” heating of the expansion element by the piezoelectric actuator. However, such a temperature value is preferably below 45.degree. C., preferably below 30.degree. C., particularly preferably below 18.degree.

At least in those cases in which the temperature value is above room temperature, air, in particular compressed air, can also be used as the cooling medium. Uncooled compressed room air has the advantage that it can be provided comparatively inexpensively and with a sufficiently large volume flow.

Alternatively, cooled air can also be used as the cooling medium, in particular cooled compressed air. For example, the cooling medium by means of one of the Cooling device associated cold source, z. B. a refrigeration machine and / or a vortex tube, can be "actively" cooled to a certain target temperature. The cooling medium could then be designed to cool the expansion element to a temperature below an ambient temperature of the metering system.

The cooling capacity of the cooling device assigned to the expansion element can preferably be controlled and / or regulated separately. A separate controllability is particularly useful when the cooling device of the metering system is also provided for temperature control of other components of the metering system. For example, the cooling device could also be designed to control the temperature of the actuator, in particular the piezo actuator, in order to cool it down to a working temperature during operation. In this case, the cooling device assigned to the expansion element can be designed as a separate partial cooling device of a jointly used overall cooling device of the metering system. A further partial cooling device can accordingly be assigned to the actuator. The overall cooling device can then preferably comprise two separately controllable proportional valves in order to individually supply the expansion element or the actuator with cooling fluid.

The cooling device assigned to the expansion element and the heating device are preferably designed to be separately controllable. As a result, a thermal decoupling of the expansion element from other components of the metering system can be achieved as far as possible. The cooling device and the heating device can particularly preferably also be operated simultaneously. As a result, a certain setpoint temperature of the expansion element can be set in a particularly time-efficient manner, with an overshooting of the temperature being prevented. In addition, a slight, controlled “working against one another” of the heating device and cooling device can contribute to increased “rigidity” or constancy of the temperature of the expansion element, e.g. B. against external interference.

To control and / or regulate the heating device and / or the cooling device, the metering system preferably comprises at least one control or regulation unit. The metering system can on the one hand be coupled to an external control or regulation unit, e.g. B. a central control unit for separate control of a plurality of metering systems. Such a central control or regulating unit could be implemented as software as possible, preferably in the form of a computer unit with a suitable one Software. The computer unit can have, for example, one or more cooperating microprocessors or the like.

However, the dosing system can also be assigned a separate "dosing system-specific" control unit. This can e.g. B. be realized by means of a circuit board inside the housing. The “dosing system's own” control unit can on the one hand be designed to independently control the entire dosing process. A central control or regulation unit could then be dispensed with.

On the other hand, the “dosing system's own” control unit can also be designed to control only individual processes of the dosing process. The “dosing-system-specific” control unit can then preferably be designed as a control unit part of a central control unit and coupled to it for signaling purposes. For example, the “dosing system's own” control unit can be provided for controlling and / or regulating the second actuator, in particular the expansion element, that is to say in particular for carrying out adjustment processes and for thermal and / or mechanical compensation functions. In contrast, the central control unit can control the remaining processes of the dosing process, e.g. B. the electrical wiring of the piezo actuator. In the following, a “dosing-system-specific” control unit according to the second variant is described without being restricted to this. The control unit can also comprise a plurality of sub-control units, which can then jointly form the control unit.

The term control is used in the context of the application as a synonym for control and / or regulation. This means that even when one speaks of a controller, the controller can comprise at least one regulating process. In the case of regulation, a controlled variable (as an actual value) is generally recorded continuously and compared with a reference variable (as a setpoint). The regulation is usually carried out in such a way that the controlled variable is matched to the reference variable. This means that the controlled variable (actual value) continuously influences itself in the action path of the control loop.

In a preferred method for controlling the metering system, a number of operating parameters of the metering system can be taken into account when controlling and / or regulating the second actuator, preferably for controlling and / or regulating the expansion element, preferably for setting the temperature of the expansion element. In particular for setting, ie for determining and / or reaching, the adjust position, at least one of the following operating parameters can be taken into account:

A first operating parameter can be a temperature of the second actuator, in particular a temperature of the expansion material element, particularly preferably a temperature of the expansion material or an expansion body of the expansion material element. The expansion body and the expansion element will be explained in more detail later. A temperature of the (first) actuator and / or a temperature of the housing in one or more different housing areas can also be taken into account as operating parameters.

To determine the temperature and other operating parameters, the metering system can comprise a sensor arrangement coupled to the control unit and having a number of sensors. The measured values of the respective sensors can be fed to the control unit as (measurement) signals.

The sensor arrangement preferably comprises at least one temperature sensor assigned to the second actuator, in particular the expansion material element, preferably for determining the temperature of the expansion material. Preferably, the metering system can additionally comprise at least (each) one temperature sensor assigned to the (first) actuator and / or one temperature sensor assigned to the housing.

Another operating parameter that can be included in the control of the expansion element is the position of the ejection element in the dosing system. The position of the ejection element can preferably be determined via a position of a lever coupled to the ejection element (as part of the movement mechanism).

To detect this operating parameter, the sensor arrangement preferably comprises at least one position sensor for determining a position of the ejection element. Such a position sensor can, for. B. be realized by means of a Hall sensor. A movement of the plunger can preferably also be calculated using the (measurement) signals of the Hall sensor. Alternatively or in addition, the sensor arrangement can comprise at least one movement sensor for determining a movement of the ejection element. A motion sensor can e.g. B. be realized by means of an acceleration sensor. Preferably, by means of the movement and / or position sensor, a Movement or position of the plunger can be determined in relation to the position of the sensor.

At least one thermally compensated Hall sensor can preferably be arranged in an area of the housing in such a way that the sensor can interact with a magnet in the area of the plunger and / or in the area of the lever in order to achieve a lifting movement of the plunger (e.g. a vertical Distance measurement) with a respective ejection process and / or with a respective retraction movement. The Hall sensor can preferably be arranged on an imaginary vertical axis with the plunger (corresponding to its longitudinal extension). Preferably measured data about the (hydraulically) effective stroke of the ram can be obtained by means of the Hall sensor.

Another operating parameter can be an actuator position of the actuator, e.g. B. a respective deflection of the actuator. An electrical control voltage applied to the piezo actuator can preferably be the operating parameter.

A further operating parameter can be an amount and / or a weight of metering substance, which metering substance is to be dispensed or is to be dispensed during a respective ejection process from the nozzle of the dispensing system. Such a measured value representing the amount and / or weight of dispensed dosing substance can be e.g. B. be determined in a weighing process. Alternatively or additionally, a “dosing volume-dependent” signal of the dispensed dosing substance can be determined, e.g. B. via an optical evaluation unit of the sensor arrangement. Preferably, a signal, e.g. B. a measured value of a flow sensor for metering substance can be used as an operating parameter. The measured value can e.g. B. be determined by means of a volume flow meter in the area of the nozzle opening.

A sealing force of the ejection element that is present in the closed state of the metering system can also represent a further operating parameter. The corresponding measured values can be obtained by means of a force sensor in the plunger or in the nozzle or, alternatively, by means of a force sensor for determining a bearing force of the first or the second actuator.

Calibration data of the dosing system can be used as further operating parameters, the calibration data preferably being stored in the dosing system and being able to be read out by the respective control unit. The calibration data can in particular normalize the Hall sensor and its signals and normalize a transfer function of an electrical control voltage of the piezo actuator in relation to a respective plunger position at an operating point, ie in an adjusted state of the lever system.

Furthermore, calibration data can relate to different heating zones of the dosing system. For example, a first heating zone can be assigned to a dosing substance cartridge, and a second heating zone can be assigned to the fluidics unit, e.g. B. a feed channel, and a third heating zone of the nozzle to be assigned to the metering substance in the respective heating zone, preferably differently to temperature.

In addition, calibration data can relate to a volume flow of a respective proportional valve in relation to a control voltage of the proportional valve at a given pressure.

The expansion element can advantageously be controlled in such a way that at least the essential, preferably all, operating parameters of the metering system that can have an influence on the tappet position and / or the (hydraulically) effective stroke of the tappet are taken into account. As a result, the expansion element can be controlled in a targeted manner such that the adjust position of the ejection element can be set particularly reliably during operation. By calculating a plurality of operating parameters in the control, a less failure-prone or more robust control can be achieved, and the metering accuracy can be further improved.

In order to be able to determine and / or achieve the adjust position of the plunger as precisely as possible, an adjustment process (adjust process) with a multi-step control algorithm can preferably be run through. The individual steps of the control algorithm can preferably be processed by the control unit at least partially automatically, preferably fully automatically.

In a first step, a maximum deflection of the (first) actuator that is provided during operation of the metering system can be set. A “closed position” of the metering valve can therefore be set, whereby the ejection tip of the plunger is moved in the direction of the nozzle. A regular adjustment process is preferred during the entire adjustment process Dosing substance delivery from the nozzle not possible, e.g. B. by temporarily blocking a trigger to initiate the dispensing process.

In a second step, an “adjustment start temperature” of the second actuator, in particular the expansion element, particularly preferably the expansion material, can be set. This ensures that the ejection tip of the plunger is not (yet) in contact with the nozzle at this point in time, despite the actuator that has already been expanded. For this purpose, the expansion element can preferably be cooled. The adjustment start temperature can for example correspond to an ambient temperature of the dosing system. The adjustment start temperature can preferably be below an expected (defined later) “Adjust temperature”.

In a further step, the second actuator, in particular the expansion element, particularly preferably the expansion material, can be heated starting from the adjustment start temperature until there is full contact between the ejection tip of the plunger and the nozzle. This means that the expansion element is expanded so far over the temperature that the plunger is pushed in the direction of the nozzle and finally contacts it. As mentioned, full contact is achieved when the ejection tip of the plunger rests essentially over the entire circumference of the sealing seat of the nozzle, with the nozzle opening being sealed in a ring.

In order to determine this point of full contact, an (adjustment) ratio between the respective temperature of the expansion element and the corresponding position of the ejection element can preferably be determined during the heating of the expansion element. This change in position of the plunger can preferably be determined in relation to the temperature change by means of the control unit. For this purpose, the control unit can, for. B. access the temperature sensor of the expansion element and the position sensor of the lever, which is coupled to the plunger, and form or save corresponding “temperature-position” value pairs. Corresponding “temperature-position” value pairs can preferably be formed during the entire adjustment process. As previously explained, the position of the plunger can preferably be determined in relation to the Hall sensor, e.g. B. a distance to the Hall sensor can be determined.

Until full contact is achieved, a predominantly linear (first) (adjustment) relationship is preferably established between the temperature of the expansion element and the respective ram position ("ideal" dosing system). The (adjustment) ratio corresponds e.g. B. a slope of a function graph based on the above-mentioned value pairs. After the "full contact point" has been reached, the plunger tip is pressed further against the sealing seat of the nozzle as the expansion element continues to heat up.

In an “ideal” very stiff metering system, a further expansion of the expansion element essentially only leads to a build-up or to an increase in the sealing force of the plunger with respect to the nozzle. Correspondingly, the position of the plunger will no longer change or will no longer change measurably, with the temperature of the expansion material rising further. A new (second) predominantly linear (adjustment) ratio is therefore established, which preferably differs from the first (adjustment) ratio. The second (adjustment) ratio can preferably correspond to a slope which differs from the slope of the first (adjustment) ratio. In the “ideal” very stiff metering system considered here, the slope of the second (adjustment) ratio would be approximately zero. The ram position at which the transition from the first to the second (adjustment) ratio takes place corresponds to a full contact position of the ram.

With an “ideal” non-rigid dosing system, the further expansion of the expansion element after full contact can lead to an elastic deformation of components of the dosing system. Accordingly, the position of the plunger can still change slightly after full contact. However, the change in position of the plunger in relation to the increase in temperature of the expansion element is preferably only very small, in particular less than before full contact. Therefore, even with an "ideal" non-rigid dosing system, a new (second) predominantly linear (adjustment) relationship is established. In such an “ideal” non-rigid metering system, a slope assigned to the second (adjustment) ratio can be significantly smaller or flatter than a slope assigned to the first (adjustment) ratio. In contrast to an "ideal" very stiff metering system, the second slope would of course not be approximately zero here. The ram position at which the transition from the first to the second (adjustment) ratio takes place corresponds to the full contact position of the ram. In the case of a “non-ideal” or “real” metering system, it can happen that the ejection tip of the plunger initially hits a conical sealing seat inside the nozzle on one side or only in certain areas. This can e.g. B. be the case when the plunger is not arranged exactly in the center of the nozzle or not in alignment with the nozzle opening. Such a contact, in which only an area or only part of the plunger tip comes into contact with the nozzle, is referred to as “first contact” or “partial contact”. Correspondingly, in a “real” dosing system, the heating of the expansion element, starting from the adjustment start temperature, can initially lead to a partial contact, which is to be distinguished from a full contact.

A predominantly linear (first) (adjustment) relationship between the temperature of the expansion element and the respective plunger position can be established up to partial contact.

As part of the adjustment process, the expansion element can be heated further until the plunger finally "slips" into the nozzle due to the progressive expansion of the expansion element, with the above-described full contact between plunger and nozzle being achieved. This process of "sliding" the tappet into the nozzle is also known as the "shift process". In addition, “temperature-position” value pairs can preferably be formed, with the respective temperature of the expansion element being assigned the respective corresponding tappet position.

Since the plunger is pressed into the full contact position after the first contact against a certain resistance of the nozzle, the position of the plunger can change more slowly in relation to the temperature increase of the expansion element than before the first contact. A new (second) predominantly linear (adjustment) ratio is therefore established, which preferably differs from the first (adjustment) ratio. The plunger position at which the transition from the first to the second (adjustment) ratio takes place corresponds to a first contact position of the plunger. In an optional step, the first contact position of the ejection element can be determined and possibly saved. Together with the full contact position, this value can provide information about the mechanical quality of the system and can therefore be helpful in the context of a system evaluation. Furthermore, a “first contact temperature” of the expansion element, that is to say the temperature that the expansion element has at the time of the first contact, can be determined and possibly saved. In a "real" dosing system, in a similar way to an "ideal" dosing system, full contact is defined by the fact that there is (again) a change in the (adjustment) ratio. The expansion element can preferably be heated further after the initial contact until a new (third) (adjustment) ratio is established. The ram position at which the change from the second to the third (adjustment) ratio takes place corresponds to the full contact position of the ram in a "real" dosing system.

Depending on the specific design of the "real" dosing system, the position of the plunger after reaching full contact can remain essentially constant (very stiff system) or change very slightly (non-stiff system), as was previously the case for the expansion element respective "ideal" systems was explained accordingly.

In a next step, the full contact position of the ejection element can then be determined and possibly saved. Furthermore, a “full contact temperature” of the expansion element, that is to say the temperature that the expansion element has at the time of full contact, can be determined and possibly saved.

In a further step of the adjustment process, an adjust position of the ejection element can then be determined and, if necessary, stored, preferably on the basis of the previously determined “temperature / plunger position” value pairs. Furthermore, an “adjust temperature” of the expansion element, that is to say the temperature that the expansion element has at the desired adjustment point, can be determined and possibly saved. As mentioned, the adjust position is an empirically determined value at which, for example, a sufficiently high sealing force is built up between the plunger and the nozzle to guarantee a reliable sealing of the system during operation.

The adjustment position and / or the adjust temperature can preferably be determined at least as a function of the full contact position of the ejection element and / or as a function of the full contact temperature of the expansion element.

The adjust position of the ejector element can preferably be determined at least as a function of a full contact position of the plunger and a slope of an (adjustment) ratio, the (adjustment) ratio resulting from a change in position of the plunger in relation to a change in temperature of the expansion element , in particular until a first contact is reached or until a full contact is achieved.

The adjust position of the ejection element can particularly preferably be calculated using the following equation: s (AP) = s (VP) + m-T (DS, FS, m) (1)

Where: s (AP) = position of the ejection element in the adjust position. For this purpose, a corresponding adjust temperature of the expansion element is determined, preferably on the basis of the previously recorded “temperature-position” value pairs. s (VP) = position of the ejection element in full contact and from this determines a corresponding full contact temperature of the expansion unit. m = (Äs / DT) = slope of a function graph based on “ram position-temperature” value pairs until a first contact (“real” system) or until a full contact (“ideal system”) is reached (depending on which Contact is reached first).

T = required temperature difference of the expansion element, based on full contact, in order to achieve a desired sealing force of the plunger. Preferably, a temperature difference value T as a function of a total spring stiffness FS of an actuator system, as a function of a desired sealing force DS, which z. B. can be stored in a firmware of the metering system, and calculated depending on the slope m determined in each case. The total spring stiffness FS is understood to mean a type of mean spring stiffness of a metering system, the spring stiffness z. B. can be measured on several copies of the dosing system and, if necessary, averaged over several copies.

In addition, the adjust position can be dependent on an application-specific parameter that is included in the determination process. For example, when the supply pressure is particularly high, it can be advantageous dosing medium to compensate the forces acting on the plunger by an initially higher sealing force and thus to include the supply pressure as an application-specific parameter.

In the case of a very stiff metering system, the respective position of the plunger should essentially no longer change after full contact. Therefore, s (AP) is essentially equal to s (VP), the difference due to the term m-T not leading to a further change in position, but only to a required build-up of sealing force by the tappet.

The position of the plunger in the adjust position can therefore preferably be essentially the same as the position of the plunger in the full contact position and / or essentially the same as the position of the plunger in an ejection end position, which will be explained in more detail later.

If the metering system is not completely rigid, the specific total spring stiffness FS can be taken into account when determining s (AP) using the term m-T, so that an elastic deformation can be compensated and a desired sealing force can be built up in the adjust position. In the case of a non-rigid metering system, too, the position of the plunger in the adjust position can preferably be essentially the same as the position of the plunger in the ejection end position. The position of the plunger in the adjust position can preferably correspond approximately to the position of the plunger in the full contact position.

In summary, the adjust position of the plunger can be used to set a desired sealing force, preferably at least taking into account a (previously determined) full contact position of the plunger, a (first) slope (above the temperature) of the still freely movable plunger and an overall spring stiffness of the stored in the system Dosing system can be determined. Alternatively, a desired sealing force (adjust force) and thus also an adjust temperature could be regulated directly by means of a force sensor (which will be explained later).

The adjust position s (AP) of the ejection element can preferably be set via the expansion element. An adjust temperature can particularly preferably be set in the expansion element in order to bring the ejection element into the adjust position. Therefore, in a final optional step of the adjustment process, the ejection element preferably brought into the adjust position by correspondingly tempering the expansion element to the temperature determined for the adjust point. For this purpose, the expansion element can preferably be heated further beyond the full contact temperature until the adjust position of the ejection element is reached.

Reaching or setting the respective adjust position depends on the specific configuration of the dosing system, as will be explained below.

With an "ideal" very stiff dosing system, the full contact can already correspond to the adjust position of the ram. As explained above, if the expansion element is heated above the full contact temperature, the main result is that a sealing force is built up in the plunger. The position of the ram remains essentially constant. Therefore, the full contact position of the tappet can preferably correspond to the adjust position of the tappet.

In the case of an "ideal" non-rigid, i.e. H. At least partially elastic dosing systems can, as mentioned, change the position of the plunger due to an elastic deformation of components of the dosing system after full contact. A (second) predominantly linear (adjustment) ratio can therefore be established from full contact, which preferably has only a very slight slope. The adjust position is reached when the desired sealing force is achieved.

For a “real” dosing system, a change from a second to a third (adjustment) ratio only defines the full contact position of the plunger. Correspondingly, in a very rigid “real” dosing system, the ram position at which the transition from the second to the third (adjustment) ratio takes place can correspond to the adjust position of the ram. A slope assigned to the third (adjustment) ratio can then be approximately zero.

In contrast, in a non-rigid “real” metering system, the plunger can be moved slightly into the adjust position according to a third (adjustment) ratio or according to an associated third slope, with no further change in position after the adjust position has been reached takes place because the expansion element is not expanded any further. As already explained, in a non-rigid metering system the plunger can still be moved slightly after full contact, whereby a large part of the further expansion of the expansion element can be used to set a sealing force of the plunger after full contact.

As an alternative or in addition, it can also be provided in the adjustment process that the second actuator, in particular the expansion element, is heated beyond the full contact temperature until a maximum “system deflection” is reached during operation. The maximum “system deflection” corresponds to a maximum deflection of the (first) actuator provided during operation and a maximum planned expansion of the expansion element during operation.

Correspondingly, a “system end contact position of the ejector element can then be determined and, if necessary, saved in the adjustment process, that is to say the position that the ejector element has when the system is deflected at its maximum during operation. Furthermore, a “system end contact temperature of the expansion element can be determined and, if necessary, stored, that is to say the temperature that the expansion element has during the maximum system deflection provided during operation. The “system end contact position” or the “system end contact temperature” can preferably also be determined on the basis of “temperature plunger position” value pairs.

The so determined "system end contact position of the ejection element and / or the" system end contact temperature of the expansion element can be used as an alternative or in addition to the full contact position or the full contact temperature when determining the adjust position and / or the adjust Temperature must be taken into account.

In order to bring the ejection element from the “system end contact position into the specific adjust position, the expansion element can optionally also be brought to the adjust temperature assigned to the adjust position, preferably by means of cooling.

Furthermore, the “system end contact position” defined in this way also represents a measure of a maximum control range during operation. In the “system end contact position, the greatest possible sealing force can be achieved during operation. Information about a control reserve and thus possibly also about the existing wear of the metering system can advantageously be obtained via a difference between a specific adjust position and the “system end contact position. The adjustment process described above can be carried out on the one hand before the first start-up of the dosing system, e.g. B. to determine an initial adjust position. However, the adjustment process can also be carried out (again) after a temporary interruption of the dosing operation, e.g. B. after replacing a plunger. Routine adjustment of the dosing system is also conceivable.

A particularly precise and at the same time uncomplicated setting of the adjust position of the plunger can advantageously be carried out by means of the expansion element in the adjustment process. This process is also referred to as "thermal adjust" by the expansion element. Since the adjust position can be determined separately for each metering system, any manufacturing tolerances of each individual metering system can be compensated for by the control unit itself. As a result, a substantially identical (hydraulically) effective stroke can be set in dosing applications with a large number of dosing systems, i.e. H. the dosing systems can dose in a particularly comparable manner.

The adjustment process can also advantageously be carried out in a comparatively uncomplicated manner. The dosing system can, for. B. preferably be designed so that the adjustment process is started by means of an input to the control unit by a user, the entire adjustment then running automatically. In this way, on the one hand, the operating costs of the dosing system can be reduced, since the adjustment can now also be carried out by the user himself, in particular also by untrained personnel. At the same time, however, the adjustment process is also highly reliable, since human intervention - and corresponding sources of error - can be largely avoided. The dosing accuracy of a respective dosing system and, above all, the comparability of the dosing of several dosing systems can thus be further improved.

In order to be able to profitably use the previously explained advantages of the adjustment process during the dosing, the second actuator, in particular the expansion element, is preferably controlled and / or regulated in such a way that just an ejection end position of the ejection element during operation of the dosing system, in particular during each ejection process, corresponds to an adjust position determined in a previously carried out adjustment process. The control and / or regulation of the expansion element can preferably be performed as a function of an actual ejection end position of the plunger during a respective ejection process and taking into account a change in the piezo actuator control voltage during the same ejection process. The “ejection end position” is understood to mean the position of the tappet that the tappet actually has at the end of a respective ejection process, that is, when the (first) actuator is deflected to the maximum extent during operation. Preferably, the position of the plunger in the ejection end position can be essentially the same as the position of the plunger in the adjust position.

A control process can preferably take place in such a way that the ejection end position is controlled to a constant value during operation, in particular to the adjust position. For this purpose, the expansion element can be regulated in such a way that an adjust temperature, which, as mentioned, is assigned to the adjust position determined previously, is reached and / or kept constant in the expansion element. A PID controller or fuzzy controller coupled to the control unit can preferably control the heating device and / or the cooling device of the expansion element in such a way as to set the adjust temperature.

Advantageously, the control process can also be used to ensure that a desired (hydraulically) effective stroke of the tappet is reliably achieved during operation and can also be maintained constant over a longer period of time.

However, setting or keeping the adjust temperature constant in the expansion element can also be useful if there is temporarily no dosing, e.g. B. when the dosing system is temporarily in a standby mode (hold mode). The adjust temperature in the expansion element can preferably be kept constant by means of the PID controller even when the dosing system is at a standstill. As a result, a high level of dosing accuracy can be guaranteed immediately even if the dosing process is restarted at short notice.

In order to ensure particularly stable operation of the metering system, the metering system can include at least one force sensor, which is preferably coupled to the control unit for signaling purposes. Measured values of the force sensor can preferably be taken into account when regulating the expansion element.

The force sensor is preferably designed to determine a force exerted by the second actuator, in particular the expansion element, on the (first) (piezo) actuator. In particular, the force sensor can also be designed to determine a sealing force of the plunger relative to the nozzle on the basis of the measured values of the force sensor, for example with the aid of an evaluation unit (which can also be part of the control unit). The force sensor can preferably be arranged in a “line of force” with the expansion element and the piezo actuator. For example, the force sensor can be arranged in a support point or contact point of the expansion element opposite the piezo actuator.

The force sensor can advantageously be used to regulate directly to a constant force. In particular, a sealing force of the plunger can be adjusted to be constant via the force sensor. Since the spring stiffness of the overall system should not change during operation, seamless control is then possible in all operating modes, e.g. B. also in hold mode.

In order to further improve the dosing accuracy, especially under fluctuating operating or environmental conditions, a multi-step control algorithm can be run through in a preferred control method of the dosing system in order to adjust the ejection end position of the plunger particularly precisely to the desired, for example previously determined as described above, Adjust -To regulate position or indirectly to a certain sealing force. The individual steps of the control algorithm can preferably be processed by the control unit, in particular fully automatically. This correction algorithm can preferably be run through in the ongoing (regular) metering operation.

The control algorithm can basically be run through during a respective “closing” flank and / or during a respective “opening” flank, that is to say during an ejection process of dosing substance or during a retraction movement of the plunger. Depending on the dosing requirement, the "opening" flanks can be run at slightly slower speeds than the "closing" flanks, so that more value pairs can be recorded at a given sampling rate for each "opening" flank, with the evaluation being even more precise. The use of the “opening” edge can therefore even be preferred. For a better clarification of the control process, unless otherwise mentioned, the individual steps are described below using a “closing” edge without being restricted to them. In a first step, an ejection start position of the ejection element can be set. The ejection start position is characterized in that the (first) actuator is not deflected, ie the (first) actuator is in a rest position. Accordingly, the ejection tip of the plunger is spaced as far from the nozzle as is possible during operation. The control algorithm therefore preferably starts as soon as a retraction movement of the plunger is completely completed or immediately before a new ejection movement starts. The ejection start position can e.g. B. can be determined via the Hall sensor and / or the electrical control voltage of the (first) actuator, in particular the piezo actuator.

In a second step, a deflection of the (first) actuator and / or a change in the electrical control voltage of the (first) actuator as a function of time can be detected during a single ejection process. A deflection speed of the (first) actuator can preferably be determined in this way, to be precise starting from the rest position of the actuator up to the maximum deflection of the actuator (provided during operation). The change in the electrical control voltage applied to the (first) actuator, in particular to the piezo actuator, can preferably be recorded over time (rate of change of the control voltage).

The ram position can preferably also be recorded as a function of time during the same ejection process. A plunger speed can preferably be determined in this way, to be precise starting from the ejection start position up to reaching the ejection end position of the plunger. As mentioned, the ram position can be detected via the Hall sensor.

The rate of change of the control voltage of the piezo actuator and the corresponding tappet speed are preferably determined repeatedly at essentially the same points in time. Preferably, pairs of values (“control voltage / ram position” value pairs) over the time of the ejection process can therefore preferably be recorded by means of the control unit, the value pairs including the respective actuator control voltage (first actuator) and the corresponding (assigned) ram position.

In a further step of the control algorithm, an actual value of a value representing a sealing position actuator deflection can then be determined. As mentioned, the sealing position actuator deflection can be a proportion of the maximum during operation intended deflection of the first actuator. The sealing position actuator deflection can preferably be a portion of a maximum electrical control voltage applied to the piezo actuator (as the first actuator) during operation. The sealing position actuator deflection is defined by the fact that the ejection element is pressed into the sealing seat of the nozzle by a certain minimum beyond the full contact between the ejection element and the nozzle. The sealing position actuator deflection is therefore specifically that portion of the actuator deflection which brings the plunger into the sealing area and thus builds up a desired sealing force.

A value that represents the sealing position actuator deflection can preferably be a component (a partial voltage) of the maximum electrical control voltage applied to the piezo actuator (as the first actuator) during operation in order to set a specific sealing force of the plunger. In a pneumatic actuator could, for. B. a gradual pressure build-up in relation to the respective corresponding slide position can be detected. The sealing position actuator deflection could then correspond to a specific increase in pressure which, based on full contact, is still required to build up the sealing force.

This means that by determining the sealing position actuator deflection, in particular its extent, it can be determined whether the plunger is moved into a desired adjust position, or whether the ejection movement ends at another ejection end position, e.g. B. at an “earlier” or “later” point.

The determination of the value that represents the sealing position actuator deflection can preferably take place on the basis of the previously determined “control voltage-tappet position” value pairs. The rate of change of the control voltage of the piezo actuator (as the first actuator) can preferably be compared with the corresponding tappet speed, in particular over the entire ejection process. A ratio between the rate of change of the control voltage and the ram speed can preferably be determined.

The rate of change of the electrical control voltage of the piezo actuator can be essentially constant during the entire ejection process. However, more complex control voltage functions are also possible, ie the control voltage can vary during the ejection process. In the case of a constant The rate of change of the electrical control voltage of the piezo actuator can vary the rate of deflection of the piezo actuator during different phases of the ejection process. Due to the coupling between the (piezo) actuator and the ejection element, e.g. B. by means of a lever, the two components form a "movement unit". Correspondingly, the slide speed can also be different during a respective ejection process, as will be explained below.

At the beginning of a respective ejection process, the deflection of the (piezo) actuator can initially move the plunger at a first, predominantly constant speed in the direction of the nozzle. A first (speed) ratio can therefore be established between the rate of change of the piezo actuator control voltage and the ram speed.

In the case of an "ideal" very stiff dosing system, the ram speed can slow down considerably after full contact, in particular go to zero, with the ram being pressed further into the nozzle. For a piezo actuator, this means that the electrical control voltage increases essentially constantly, with the plunger no longer moving in a measurable manner. Due to the coupling of the piezo actuator and the plunger, the longitudinal extension of the piezo actuator hardly changes. This means that the increase in the electrical control voltage leads to a predominantly constant increase in pressure or to a (mechanical) build-up of tension in the piezo actuator, via which the sealing force of the plunger can then be built up.

After full contact, a second (speed) ratio can therefore set between the rate of change of the control voltage and the ram speed, which ratio preferably differs from the first ratio. At the moment or at the ram position at which the change from the first to the second (speed) ratio takes place, the full contact position of the ram is reached. As already explained, in an “ideal” very stiff metering system, the full contact position of the plunger can preferably be essentially the same as the ejection end position of the plunger, with a maximum control voltage provided during operation being applied to the piezo actuator.

With an “ideal” non-rigid dosing system, the ram speed can also slow down significantly after full contact, with a second (speed) ratio also being established here. The slide position at which the change from the first to the second (speed) ratio corresponds to the full contact position of the plunger. The second (speed) ratio corresponds to a slight change in position of the plunger due to elastic deformation of components of the dosing system. The plunger can be moved slightly further until a maximum control voltage provided during operation is applied to the piezo actuator, the ejection end position of the plunger being reached. This means that in the case of a non-rigid system, unlike a rigid system, after full contact, a small part of the electrical voltage change of the piezo actuator can still be converted into a change in travel of the plunger, with the majority flowing into the change in force.

With a “real” dosing system, a first (speed) ratio can be established up to the first contact, whereby the ram speed can slow down after the first contact due to the “shift process”. The ram position at which a change from the first to a second (speed) ratio takes place corresponds to the first contact position of the ram. As soon as the plunger has "slipped" into the full contact position due to the actuator deflection, the plunger speed can slow down significantly, with a third (speed) ratio being established. The ram position at which a change from the second to the third (speed) ratio takes place then corresponds to the full contact position of the ram.

Depending on the configuration of the dosing system, the full contact position can correspond to the ejection end position (rigid system). Otherwise, according to the third (speed) ratio, the ram can still be moved into the ejection end position defined above.

Ideally, the ejection end position can correspond to the intended adjust position. As mentioned, the adjust position can preferably be set taking into account the desired sealing force and the spring stiffness of the metering system. During the operation of the dosing system, however, it can also happen that an actual ejection end position of the plunger deviates from a previously determined adjust position. This can e.g. B. be caused by a thermally induced change in length of the piezo actuator and / or wear of moving components and / or a change in a temperature of a housing of the dosing system and / or a change in the ambient temperature of the dosing system. The actual Sealing position actuator deflection (as actual value) deviate from a "setpoint" of the sealing position actuator deflection (to reach the adjust position).

To determine the actual value that represents the sealing position actuator deflection, the actual portion of the actuator deflection (of the first actuator) can be determined, which presses the plunger into the nozzle from the full contact position to the ejection end position. The actual value of the value representing the sealing position actuator deflection can result from a difference between the maximum actuator deflection during operation and the actuator deflection until full contact is reached. Preferably, the actual value of the current sealing position actuator deflection can be a voltage difference between a maximum electrical control voltage applied to the piezo actuator (as the first actuator) during operation and the electrical control voltage that is necessary to bring the plunger into the full contact position.

In order to regulate the discharge end position during operation to a specific adjust position, a difference between the actual value of the value representing the sealing position actuator deflection and a setpoint value of a value representing the sealing position actuator deflection can be determined in a further step of the control algorithm. Particularly preferably, the expansion element can be regulated as a function of the determined difference such that the setpoint value of the value representing the sealing position actuator deflection is reached during operation.

This setpoint value of the value representing the sealing position actuator deflection is preferably assigned to a specific adjust position. This means that the plunger can be moved into the desired adjust position by regulating it to this setpoint ("setpoint sealing position actuator deflection"). The setpoint value can preferably be a voltage difference between the control voltage for reaching the full contact position and the maximum electrical control voltage applied to the (first) actuator during operation. The target value of the sealing position actuator deflection can be preset at the factory and is preferably stored in the control unit, e.g. B. in an EEPROM. As an alternative or in addition, the target value of the sealing position actuator deflection can also be stored in a separate memory, preferably an EEPROM, of the metering system and ready for retrieval. The setpoint can e.g. B. be a percentage value of a maximum possible stroke movement of the (first) actuator or a change in length of a calibrated (first) actuator during operation. Furthermore, the setpoint could also be implemented by means of a force value. The setpoint value of the value representing the sealing position actuator deflection can preferably be set via the temperature of the expansion element. Particularly preferably, the temperature of the expansion element can be controlled to be constant to a specific voltage difference of the piezo actuator control voltage (as a setpoint value).

The second actuator, in particular the expansion element, can preferably be controlled in such a way that, in the event of a negative deviation of the actual value from the setpoint value of the value representing the sealing position actuator deflection, a temperature of the second actuator, in particular the expansion element, is increased by the setpoint value of the sealing position actuator deflection adjust. Correspondingly, in the event of a positive deviation of the actual value from the target value of the value representing the sealing position actuator deflection, the temperature of the second actuator, in particular the expansion element, can be reduced in order to set the target value of the sealing position actuator deflection.

The currently required temperature of the expansion element can preferably be determined by means of equation (1) introduced above.

As already explained, the control process can also be run through during a respective "opening" edge. Correspondingly, an ejection end position of the ejection element can then be set in a first step in order to regulate the ejection end position. In a next step, a position of the ejector element can be determined as a function of a deflection of the first actuator during a retraction movement of the ejector element. The position of the ejection element can particularly preferably be determined as a function of an electrical control voltage applied to the first actuator or to the piezo actuator. For this purpose, “control voltage / ram position” value pairs can again be recorded, as described above.

In a further step, an actual value of a value representing the sealing position actuator deflection can then be determined. The actual value and the setpoint of a value representing the sealing position actuator deflection (of the first actuator) are defined accordingly, as was previously explained for the "closing" edge. In a subsequent step, the second actuator, preferably the expansion element, can be controlled and / or regulated, in particular as a function of a difference between the actual value of the value representing the sealing position actuator deflection and a target value of the value representing the sealing position actuator deflection, that a target value of the value representing the sealing position actuator deflection is set. The control and / or regulation of the second actuator is preferably carried out as was described above for a “closing” edge.

Preferably, the control process described (the control of the target sealing position actuator deflection) can be run through at regular intervals during operation of the metering system, e.g. B. during each ejection of the plunger. However, it is preferred to first “filter” the actual values of the sealing position actuator deflection recorded for each ejection process, e.g. B. to compensate for any measurement inaccuracies. A mean value and / or a median value from a number of individual measured values, e.g. B. 10 individual measurements can be formed, this median or mean value can then be fed back to the control process as the current reference variable (setpoint of the sealing position actuator deflection).

A difference between the actual value and the setpoint value of the value representing the sealing position actuator deflection can preferably be determined in a first ejection process, a “new” adjust temperature being determined as a function of the difference in order to set the adjust position under the current operating conditions.

The “new” adjust temperature determined during the (first) ejection process can preferably be taken into account for regulating the expansion element during a subsequent (second) ejection process. This means that the adjust temperature can be continuously redefined during operation.

Particularly preferably, the adjust temperature can be continuously redetermined as a function of a number of actual values of the sealing position actuator deflection determined immediately beforehand, in particular after “filtering” the individual values.

A particularly dynamic control of the expansion element can advantageously take place by determining the current sealing position actuator deflection. In particular, the expansion element can be regulated in such a way that the ejection element is brought into the adjust position with each ejection movement. This can advantageously result in various disturbance variables, such as B. thermal expansion effects of the piezo actuator, wear of the plunger and / or the nozzle, etc., can be compensated. In particular, the expansion element can on the one hand be regulated in such a way that leaks can be avoided during the dispensing of the dosing substance. On the other hand, the continuous readjustment of the target sealing position actuator deflection or the adjust temperature can further improve the metering accuracy even in continuous operation, in particular with varying metering requirements and / or under strongly fluctuating ambient conditions.

In order to be able to set the adjust position of the plunger particularly efficiently, the second actuator, in particular the expansion element, as mentioned, comprises an expansion body and preferably a slidably mounted transmitter coupled therewith, e.g. B. a movable piston.

The expansion body, which forms the expansion material of the expansion element, can preferably be a solid. In particular, the expansion body can be present as a solid body at the adjust temperatures that usually occur during operation of the metering system. For example, the expansion body can be present as a solid at temperatures up to 250 ° C., preferably up to 260 ° C., preferably up to 350 ° C. The expansion body preferably has a thermally induced high coefficient of expansion, in particular a higher coefficient of expansion than a metal or a ceramic of a housing of the expansion element. For example, the expansion coefficient of the expansion body can be at least 23-10 ⁶ / K, preferably at least 45-10 ⁶ / K, preferably at least 100-10 ⁶ / K. A suitable material of the expansion body can be a polymer, e.g. B. PEEK, PFA or polytetrafluoroethylene.

The expansion body can preferably be arranged in a housing or a chamber of the expansion element, for. B. in a stainless steel case. The housing can preferably be designed in the manner of a hermetically sealable chamber. This offers the advantage that the expansion material can be introduced into the chamber in liquid form and can harden into a solid there, in particular without bubbles.

The second actuator, in particular the expansion element, can preferably be in an axial direction, for. B. be coupled to the (first) actuator in accordance with a longitudinal extension of the piezo actuator in order to position the (first) actuator in the housing. Preferably can the expansion element in the housing of the dosing system can be mechanically connected in series with the piezo actuator. The expansion element can preferably be supported on the housing of the metering system with at least one side, preferably one side facing away from the (first) actuator.

The expansion element is preferably designed and arranged in the housing in such a way that only one pressure side of the expansion element pointing in the direction of the actuator is designed to be displaceable. The pressure side can preferably be shifted in the direction of a longitudinal axis of the actuator, in particular of the piezo actuator. This means that when the volume of the expansion body changes, the dimensions of the expansion element change essentially only in the direction of the longitudinal axis of the actuator, with the lateral dimensions of the expansion element remaining predominantly constant (“forced expansion direction”). The change in volume of the expansion material can therefore be converted into a directed stroke movement in order to move the actuator, in particular the piezo actuator, preferably in accordance with its longitudinal extension.

In order to position the actuator, the expansion element, in particular its pressure side, can be coupled to the actuator by means of a carrier. A stroke movement of the expansion element can preferably be transmitted predominantly completely to the actuator by means of the carrier in order to move it in the housing. As mentioned at the beginning, the coupling between the expansion element (transmitter) and the (first) actuator does not have to be a fixed connection. The coupling can preferably take place in such a way that an active unit composed of expansion element and actuator is kept under constant pretension during operation, in particular also when the (first) actuator is in a non-deflected state. For example, a side of the expansion element facing away from the actuator could be mounted so as to be adjustable by means of an adjustable spherical cap relative to the housing of the metering system.

The invention is explained in more detail below with reference to the accompanying figures on the basis of exemplary embodiments. The same components are provided with identical reference numbers in the various figures. The figures are usually not to scale. They show schematically:

Figure 1 is a sectional view of a metering system according to an embodiment of the invention, Figures 2 and 3 parts of the dosing system from Figure 1 in an enlarged view,

Figures 4 to 6 parts of the dosing system from Figure 1 in a once again enlarged and greatly simplified view,

FIGS. 7a to 7c are flow charts of sections of a method for controlling the metering system according to an embodiment of the invention,

FIGS. 8 to 12 representations of function graphs to clarify subsections of the method according to FIGS. 7a to 7c for controlling the metering system.

A specific exemplary embodiment of a metering system 1 according to the invention will now be described with reference to FIG. The metering system 1 is shown here in the usual intended position, for. B during the operation of the metering system 1. A nozzle 60 is located in the lower area of the metering system 1, so that the drops of the medium are ejected in an ejection direction R through the nozzle 60 downwards. As far as the terms below and above are used in the following, this information always relates to such a, usually usual position of the dosing system 1. This does not rule out that the dosing system 1 can also be used in a different position in special applications and the drops z. B. be ejected laterally. Depending on the medium, pressure and exact construction as well as control of the entire ejection system, this is basically also possible. Since the basic structure of metering systems is known, for the sake of clarity, predominantly those components are shown here which relate at least indirectly to the invention.

The dosing system 1 comprises, as essential components, an actuator unit 10 and a fluidics unit 50 coupled to it. The dosing system 1 shown here also comprises a dosing substance cartridge 66 which is coupled to the fluidics unit 50.

In the exemplary embodiment shown here, the actuator unit 10 and the fluidics unit 50 are implemented in the manner of plug-in coupling parts that can be coupled to one another to form a quick-release coupling. Advantageously, the actuator unit 10 and the fluidic unit 50 can thus be coupled to one another without tools in order to form the metering system 1. The quick coupling includes a coupling mechanism 70 a clutch spring 71 which keeps a ball 72 under constant tension. The coupling spring 71 and the ball 72 are here enclosed by a (first) housing block 11a and form a first plug-in coupling part. The first plug-in coupling part furthermore comprises a heating device 75 for heating the metering substance in the nozzle 60.

The coupling mechanism 70 has a number of spherical caps 74 (only one shown here) into which the ball 72 can engage for coupling. The spherical caps 74 are arranged in a second plug-in coupling part 73 of the fluidic unit 50, the fluidic unit 50 being encompassed by a (second) housing block 11b. For coupling, the first plug-in coupling part and the second plug-in coupling part can be plugged into one another along a (virtual or imaginary) plug-in axis and thereby coupled to one another. For example, the fluidics unit 50 can be plugged into the actuator unit 10 against a direction R and coupled to the actuator unit 10 in a suitable rotational position.

The spherical caps 74 are arranged in the second plug-in coupling part 73 of the fluidic unit 50 in such a way that different latching positions are possible, i. H. different rotational positions of the fluidics unit 50 about the plug-in axis are possible. Due to the resiliently pretensioned ball 72, the plug-in coupling part 73 engages in one of the several possible locking positions, in order to form the metering system 1. It should be noted, however, that the respective assemblies 10, 50 can also be firmly connected to one another, e.g. B. by means of a fixing screw, so as to form the housing 11 with the two housing blocks 11a, 11b.

In the exemplary embodiment shown here, the actuator unit 10 comprises two internal chambers, namely on the one hand an actuator chamber 12 with a piezo actuator 20 located therein and on the other hand an action chamber 13 into which a movable ejection element 51, here a plunger 51, of the fluidic unit 50 protrudes. Via a movement mechanism 14 with a lever 16, which protrudes from the actuator chamber 12 into the action chamber 13, the tappet 51 is actuated by the piezo actuator 20 so that the fluidic unit 50 ejects the medium to be dosed in the desired amount at the desired time.

To control the piezo actuator 20, it is connected electrically or in terms of signaling to an external control unit (not shown). The piezo actuator 20 here comprises an actuator housing 22 and a piezo stack hermetically encapsulated therein with respect to the environment 21. The piezo actuator 20 can expand (expand) and contract again in the longitudinal direction of the actuator chamber 12 in accordance with a circuit by means of the control unit. Since the basic function and control of piezo actuators is known, this will not be discussed further.

At the upper end of the piezo actuator 20 (pointing away from the nozzle 60), the piezo actuator 20 (as the first actuator 20) is indirectly in operative contact with an expansion element 30 (as the second actuator 30). The expansion element 30 here comprises a housing 31 which encloses a cylindrical expansion body 32 from five sides (in cross section from three sides). The housing 31 is designed so that a thermal expansion movement of the expansion body 32 is directed predominantly in the direction of the piezo actuator 20.

On the side on which the expansion body 32 is not limited by the chamber 31, the expansion body 32 adjoins a carrier 35. The carrier 35 is movably mounted in the housing 31 of the expansion element 30 and can be displaced in the direction of a longitudinal extension of the piezo actuator 20. On a side of the transfer piston 35, which is lower here, this adjoins the piezo actuator 20 or rests directly on an outside of the actuator housing 22. This means that the expansion body 32, the transmitter 35 and the piezo actuator 20 are in operative contact with one another in such a way that a stroke of the expansion body 32 can predominantly be used completely for positioning the piezo actuator 20. The piezo actuator 20 can therefore be moved “up” or “down” by means of the expansion element 30, which essentially corresponds to an ejection direction R of the metering substance from the nozzle.

A nominal stroke of such an arrangement, i.e. the extent of a possible displacement of the piezo actuator 20, depends in particular on the diameter used of the expansion element 30 and the volume of expansion material enclosed therein, as well as the usable temperature range and the respective expansion coefficient of the surrounding housing 31, which z. B. can be made of metal or ceramic, and the expansion element 30 from. For thermal compensation measures, a design for a nominal stroke in the range of a piezo actuator nominal stroke or less is useful, which can correspond to a few micrometers up to a few hundredths of a millimeter. For the combination of thermal adjust and thermal compensation described here, a nominal stroke of the expansion element 30 of at least 10 pm, preferably of at least 50 pm and particularly preferably of at least 100 pm.

To control the expansion length of the expansion body 32, the expansion element 30 comprises a heating device 33. This is particularly clear in FIG. The heating device 33 is here a heating film 33 which rests on an outside of the housing 31 of the expansion element 30. A temperature sensor 83 for determining a temperature of the expansion element 30 is also arranged on the outside of the housing 31. For control, the expansion element 30, in particular the heating device 33, is connected by means of connecting cables 81 to a “dosing system-specific” control unit 80 (FIG. 1).

The “dosing system-specific” control unit 80 is implemented here (FIG. 1) as a sub-control unit of a central external control unit (not shown) and is coupled to it for signaling purposes by means of connecting cables 81. The sub-control unit 80 can e.g. B. be implemented by means of a circuit board 80 in the housing 11 of the metering system 1. The “dosing system-specific” control unit 80 is designed to control the expansion element 30 during operation, that is to say in particular to apply corresponding control signals to the heating device 33 and a cooling device 40 in order to set a desired expansion of the expansion body 32.

The dosing system 1 from FIG. 1 further comprises a cooling device 40, the cooling device 40 being designed to cool the expansion element 30 and the piezo actuator 20 separately. The cooling device 40 here includes some components that are used jointly for cooling the expansion element 30 and the piezo actuator 20. This includes, among others. a coupling point 41, e.g. B. a connection for an external cooling medium supply, an adjoining inflow channel 42 for cooling medium and a cooling medium discharge 46.

However, the cooling device 40 comprises two separate proportional valves 43, 44 which can be controlled separately by the control unit 80. The proportional valve 43 assigned to the expansion element 30 is connected to a cooling area 34 by means of a separate bore 42 ′. The cooling region 34 here surrounds the expansion element 30 in a ring shape and is provided exclusively for cooling the expansion element 30. The cooling area 34 can be supplied with a cooling medium, for example via the proportional valve 43 and the bore 42 '. B. compressed and / or cooled air, are flooded in order to cool the expansion element 30 as required.

The cooling of the piezo actuator 20 can be controlled separately by means of the second proportional valve 44, wherein the actuator chamber 12 can be supplied with cooling medium via an inflow channel 42 ″. The cooling of the expansion element 30 and the piezo actuator 20 is therefore largely thermally decoupled here. The cooling medium can be discharged from the cooling area 34 or from the actuator chamber 12 via a separate outflow channel (not shown here) and then flow out of the metering system 1 again via a shared outflow channel 45 and a coupling point 46 for a cooling medium discharge.

In order to be able to position the piezo actuator 20 in the desired manner by means of the expansion element 30 during operation, an active unit composed of expansion element 30 and piezo actuator 20 is kept under constant prestress for coupling. For this purpose, the expansion element 30 comprises a centering element 36, which is superimposed on the expansion element 30 here (FIG. 1). The centering element 36 is supported with respect to the housing 11 of the metering system 1 and is designed to exert a certain pressure on the expansion element 30 and thus also on the piezo actuator 20. The piezo actuator 20 is supported at its lower end via a pressure piece 23 on a lever 16 of the movement mechanism 14.

The lever 16 of the movement mechanism 14, which serves to transfer the actuator movement to the ejector element 51, rests on a lever bearing 18 at the lower end of the actuator chamber 12 and can be tilted about a tilting axis K via this lever bearing 18. A lever arm of the lever 16 protrudes through an opening 15 into the action chamber 13. The opening 15 thus connects the action chamber 13 to the actuator chamber 12.

In the action chamber 13, the lever arm has a contact surface 17 pointing in the direction of the plunger 51, which presses on a contact surface 54 of a plunger head 53 (FIG. 3). In Figure 1 it becomes clear that the contact between piezo actuator 20 and lever 16 takes place in an area between the lever bearing 18 and the contact surface 17 of the lever 16 facing the plunger 51, this contact point being closer to the lever bearing 18 than the contact surface 17 To achieve the desired transmission ratio, in which a small movement of the actuator 20 causes a larger movement of the ejection element 51. In the exemplary embodiment shown in FIG. 3, it is provided that the contact surface 17 of the lever 16 is permanently in contact with the contact surface 54 of the plunger head 53 in that a plunger spring 55 presses the plunger head 53 against the lever 16 from below. The plunger spring 55 is supported here downward on a plunger centering piece 56.

The lever 16 rests on the plunger 51. However, there is no fixed connection between the two components 16, 51. In principle, however, it would also be possible for the tappet spring 55 to be at a distance between the tappet 51 and the lever 16 in an initial or rest position. In order to enable an almost constant preload of the drive system (lever-piezo actuator movement system), the lever 16 is pressed upwards by an actuator spring 19 at the end at which it comes into contact with the plunger 51 (FIG. 3).

To measure the position and / or movement of the plunger 51, a magnet 85 is arranged here on an upper side of the lever 16 facing away from the plunger 51 and interacts with a Hall sensor 84 in the housing of the metering system (FIG. 3). The Hall sensor 84 and the magnet 85 are arranged here on an imaginary vertical axis corresponding to the longitudinal extension of the plunger 51. A predominantly vertical lifting movement of the lever 16 can be detected by means of this arrangement 84, 85, with a position or movement of the plunger 51 also being able to be determined.

In FIG. 1 it becomes clear that the tappet spring 55 is supported on a tappet bearing 57, to which a tappet seal 58 adjoins at the bottom. The tappet spring 55 pushes the tappet head 53 away from the tappet bearing 57 in the axial direction upwards. A plunger tip 52 is thus also pushed away from a sealing seat 63 of the nozzle 60. I.e. Without external pressure from above on the contact surface 54 of the plunger head 53, the plunger tip 52 is in the rest position of the plunger spring 55 at a distance from the sealing seat 63 of the nozzle 60. Thus, in the rest state (non-expanded state) of the piezo actuator 20, a nozzle opening 61 is also not closed .

The dosing substance is fed to the nozzle 60 via a nozzle chamber 62 to which a feed channel 64 leads. At its other end, the supply channel 64 opens into the dosing substance cartridge 66, the cartridge 66 being fastened directly to the housing 11 via a coupling point 65, here on the second housing part 11b. The dosing substance cartridge 66 is releasably fixed to the dosing system 1 by means of a cartridge holder 67 and has a compressed air supply 68 at the upper end here, e.g. B. in order to set a certain pressure of the dosing substance in the dosing substance cartridge 66. The fluidic unit 50 also has a connecting cable 69 in order to control a heating device (not shown) of the fluidic unit 50. In addition, the metering substance can be temperature controlled separately in the fluidics unit 50, e.g. B. differently than in the nozzle 60. The dosing system 1 can preferably comprise several differently temperature-controllable heating zones for the dosing substance, a first heating zone of the nozzle 60, a second heating zone of the fluidics unit 50 and a third heating zone of the cartridge 66 being assigned.

In FIGS. 4 to 6, the essential steps of an adjustment process for setting an adjust position of the plunger are shown schematically. The parts of the dosing system shown correspond to those from FIG. 1, but are shown greatly simplified and enlarged. The dosing system shown here is a "real" system, the distances between the individual components of the dosing system and their movements during adjustment being shown greatly enlarged for clarity.

A start of the adjustment process is shown in FIG. First of all, the piezo actuator 20 (as the first actuator 20) is controlled in such a way that a maximum electrical control voltage provided during operation of the dosing system is applied to the piezo actuator 20; H. the piezo actuator 20 is fully expanded. As already explained, the piezo actuator 20 rests on the lever 16, which in turn is in contact at its other end with the plunger 51. In a next step, an adjustment start temperature is set in the expansion element 30 (as the second actuator 30). For this purpose, the expansion element 30 can be cooled to a certain temperature, so that the expansion element 30 contracts at least slightly if it is in a heated state. The piezo actuator 20, however, is still expanded. Since the piezo actuator 20 and the plunger 51 form a movement unit, the plunger 51 can be moved slightly away from the nozzle 60 as a result of the contraction of the expansion element 30 in an upward direction RS ', this process being shown here, as already mentioned, greatly enlarged for clarity is. Correspondingly, a distance a is established between the plunger tip 52 and the sealing seat 63.

In a subsequent step (FIG. 5), the expansion element 30 is heated starting from the adjustment starting temperature. The thermally induced expansion of the expansion element 30 is transmitted to the tappet 51 via the piezo actuator 20 and the lever 16, the tappet 51 being moved in a downward direction RS in the direction of the nozzle 60. The moment of initial contact is specifically shown in FIG. 5, with only a left area of the plunger tip 52 making contact with the sealing seat 63 of the nozzle 60 for the first time. The nozzle opening 61 is not yet closed by the plunger 51. Therefore, the plunger position shown here corresponds to a first contact position of the plunger 51 and not a full contact. It should be pointed out again that a “real” metering system is shown in FIGS. In contrast to this, in the case of an “ideal” metering system, the first contact (FIG. 5) can be omitted, the plunger 51 being moved directly into the full contact position (FIG. 6). In other words, the first contact then already corresponds to the full contact.

Finally, in FIG. 6, the plunger 51 is arranged in a full contact position. For this purpose, the expansion element 30 is heated further after the initial contact until the plunger 51 “slides” into the nozzle 60 essentially in the downward direction RS, with full contact being achieved. Starting from the first contact (FIG. 5), the tappet tip 52 “slides” along a left part of the conical sealing seat 63 until the tappet tip 52 finally seals the nozzle opening 61 in a ring (full contact). The piezo actuator 20 is still expanded. The full contact position of the plunger 51 shown here can - depending on the configuration of the dosing system - correspond to the adjust position of the plunger 51, with a certain sealing force additionally being exerted by the plunger on the sealing seat 63 in the adjust position.

Further details of the adjustment process can also be found in FIGS. 7a-c to 9.

FIG. 7a shows a first section of a control method for controlling a metering system according to an embodiment of the invention. The method section 7 shown here can be used to set the adjust position of the plunger in an adjustment process or adjust process. Preferably, the adjustment process can run fully automatically after an initial initiation, e.g. B. by the individual process steps being processed by the "dosing system's" control unit. The adjust process is described below (FIGS. 7 to 9) using an “ideal” non-rigid dosing system. This means that full contact between the plunger and nozzle is achieved without prior initial contact.

In a first step 7-I. of the process section 7, the adjustment process is started, e.g. B. by means of an input to the "dosing system's" control unit or to a central one Control unit. In step 7-II. a maximum deflection of the piezo actuator during operation is first set or a maximum electrical control voltage provided during operation is applied to the piezo actuator. At the same time, a trigger for dispensing the dosing substance is blocked for the duration of the adjust process. In step 7-III. an adjustment start temperature is set in the expansion element, e.g. B. by means of cooling. In step 7-IV. the expansion element is then continuously heated starting from the adjustment start temperature.

During the heating of the expansion element, the tappet position is measured in relation to the temperature of the expansion element (step 7-V.). "Temperature-plunger position" value pairs are continuously formed and saved (step 7-VI.). On the basis of the value pairs, a check is carried out at regular intervals to determine whether full contact between the plunger and nozzle has already been detected (step 7-VI I.). If full contact has not yet been detected, according to iterative step 7-i. continues to record value pairs. The iterative step 7-i. is run through until a full contact is detected.

The determination of the full contact takes place in the procedure subsection 7-D. For this purpose, a function graph of the change in the tappet position S (in pm) in relation to the increase in temperature T (in ° C.) of the expansion element is shown schematically in FIG. The ram position S can, for. B. can be determined via a distance between the plunger head and Hall sensor. It can be seen that, based on the adjustment start temperature (here at the origin of the coordinate system), a predominantly linear (adjustment) relationship is initially established between the ram position S and the temperature T of the expansion element. The relationship is shown here as a straight line with an incline m1, the straight line resulting from the previously recorded “temperature / plunger position” value pairs.

As soon as there is full contact between the plunger and nozzle and the plunger is pressed into the nozzle, the plunger position S changes more slowly than before full contact, despite the continuous temperature rise T. A new relationship is therefore established between the ram position S and temperature T, which is shown here as a straight line with a flatter slope m2. The ram position Si, at which the slope of the straight line changes from m1 to m2, corresponds to the full contact position Si of the ram. The flat slope m2 results from a slight slide movement due to elastic deformation of components of the dosing system, the slope m2 being a measure of the spring stiffness of the system can be. The full contact position Si is assigned a full contact temperature Ti here.

The duration until full contact is reached can be, for. B. be in about 1 minute. It is also conceivable to heat the expansion element dynamically in order to achieve full contact more quickly. For example, the expansion element can be heated to different degrees in different phases, with a mean slope m1 then being able to be recorded. This calibration could also be carried out by the manufacturer and stored in the dosing system.

As soon as the full contact in step 7-VII. is detected, the full contact position Si of the plunger in step 7-VIII. stored (Figure 7a).

In step 7-IX. the slope m1 (Figure 8) can then be determined until full contact is reached, preferably as a function of the previously determined “temperature-position” value pairs. In step 7-X. the spring stiffness of the metering system can then be determined, e.g. B. by reading out the calibration data stored in the dispensing system at the factory. In step 7-XI. Finally, the adjust position of the plunger can be calculated, especially taking into account the full contact position (Si), the slope m1 (both in FIG. 8) and the spring stiffness of the overall system. The calculation of the adjust position is z. B. possible with the previously introduced equation (1). Furthermore, in step 7-XI. an adjust temperature assigned to the adjust position can be determined.

The determination of the adjust position in method subsection 7-E is shown schematically in FIG. 9 using a function graph of the change in the ram position S (in pm) in relation to the increase in temperature T (in ° C.) of the expansion element. The adjust position (S2) of the ram deviates slightly from the full contact position (Si) of the ram. The reason is that the adjust position (S2) is shown here for a non-rigid dosing system, whereby after full contact (Si) there is still a slight slide movement according to the slope m2. In order to build up a certain sealing force in spite of the slight slide movement in the adjust position (S2), the spring stiffness of the dosing system can be taken into account when calculating the adjust position (S2). The adjust position (S2) is assigned an adjust temperature (T2) of the expansion element. The adjust position (S2) here also corresponds to an ejection end position (S ₃ ) of the plunger. Contrary to what is shown here, the adjust position S2 of the ram in a very rigid "ideal" dosing system can essentially correspond to the full contact position S1, i.e. the full contact position (S1), the adjust position (S2) and the ejection End positions (S ₃ ) then essentially coincide.

In step 7-XII. the adjust position and the assigned adjust temperature are saved (FIG. 7a). It is then reported to the control unit that the adjustment process has ended (step 7-XIII.). This can be used to unblock the trigger for dispensing of the dosing substance. In step 7-XIV. Finally, the operating mode of the dosing system is queried, d. H. It is decided whether the dosing system should switch to a standby mode (jump label A.) or switch to the dosing process (jump label B.).

FIG. 7b shows a further section of the control method for controlling the metering system according to an embodiment of the invention. The process section 8 shown here follows directly from the jump label A. from FIG. 7a. Method section 8 is therefore carried out if the query of the operating mode in step 7-XIV. (Figure 7a) has resulted in a change of the dosing system into the hold mode.

In the first step 8-I. (FIG. 7b) the adjust temperature determined in a previously performed adjustment process is called up. The adjust temperature is transmitted to a PID controller or fuzzy controller of the dosing system (step 8-II.). The expansion element can be cooled (step 8-III.) Or heated (step 8-IV.) By means of the PID controller in order to set the adjust temperature in the expansion element (step 8-V.). In step 8- VI. the desired actuator position or plunger position is set in the dosing system via the expansion element. The method section 8 ends at the jump label C. This is followed again by the query of the operating mode in FIG. 7a (step 7-XIV.).

A further section of the control method for controlling the metering system is shown in FIG. 7c. The method section 9 shown here directly follows the jump label B. from FIG. 7a. The method section 9 is therefore carried out if the query of the operating mode in step 7-XIV. (Figure 7a) has resulted in a change of the dosing system to the "active" dosing mode. In a first step 9-1. (FIG. 7c) the electrical control voltage currently applied to the piezo actuator is determined. In step 9-11. it is determined whether the current control voltage corresponds to an idle voltage of the piezo actuator, the piezo actuator being in a rest position, that is to say is not expanded. If the current control voltage does not correspond to the no-load voltage, ie the piezo actuator is at least partially expanded, the iterative process step 9-iii. the current operating voltage of the piezo actuator is measured again. The iterative process step 9-iii. is run through until the current control voltage corresponds to the no-load voltage of the piezo actuator (step 9-11.), ie until the plunger is in the initial ejection position.

In step 9-1 II., Starting from the initial ejection position, the change in the electrical actuator voltage over time and the tappet position corresponding to the respective actuator voltage are measured during a single ejection process. For this purpose, “control voltage-plunger position” value pairs are preferably formed over time. In step 9-IV. the electrical control voltage currently applied to the piezo actuator is determined. If the control voltage does not yet correspond to a maximum control voltage (expansion voltage) provided during operation, according to the iterative step 9-iv. value pairs continue to be formed. The iterative step 9-iv. is run through until the current control voltage corresponds to the expansion voltage of the piezo actuator (step 9-IV.), d. H. the ram is in the ejection end position. In step 9-V. the sealing position actuator deflection is determined, e.g. B. on the basis of the generated "control voltage-plunger position" value pairs. Further details on this or on method subsection 9-G are explained below with reference to FIGS. 10 to 12.

As an alternative or in addition, it is also possible to carry out the process described above, in particular the acquisition of “control voltage-plunger position” value pairs over time, with an opening edge. This can have the advantage that the opening edge runs more slowly than the closing edge, whereby an even higher measurement accuracy can be achieved. In this variant, the iterative substep 9- iii. be run through until a maximum control voltage (expansion voltage) provided during operation is applied to the piezo actuator, the piezo actuator reaching its greatest possible deflection during operation (step 9-II.). In step 9-III. Then, starting from the ejection end position of the tappet, the change in the electrical actuator voltage over time and the tappet position corresponding to the respective actuator voltage are measured during a single retraction movement of the tappet. For this purpose, “control voltage-plunger position” value pairs are preferably formed over time. In step 9-IV. the electrical control voltage currently applied to the piezo actuator is determined. If the control voltage does not yet correspond to the rest voltage of the piezo actuator, according to the iterative step 9-iv. value pairs continue to be formed. The iterative step 9-iv. is run through until the current control voltage corresponds to the no-load voltage of the piezo actuator (step 9-IV.), ie the plunger is in the initial ejection position. In step 9-V. the sealing position actuator deflection is determined, e.g. B. on the basis of the “control voltage / ram position” value pairs.

Process subsection 9-G is described separately below for the different types of dosing systems. In FIG. 10, the method subsection 9-G is shown for an “ideal” very rigid dosing system. The upper part here schematically shows a function graph of the time profile of the electrical control voltage U (in V) applied to the piezo actuator over time t (in arbitrary units). In the lower part of FIG. 10 here, the plunger position S (in pm) corresponding to the control voltage (U) is shown for the same period.

At the beginning of the recording, a voltage Ui is applied to the piezo actuator, which corresponds to the expansion voltage of the piezo actuator, i. H. the piezo actuator is initially expanded. Correspondingly, the plunger is arranged in the ejection end position S3 during the same period, which here simultaneously corresponds to the full contact position Sr and the adjust position Sx. As a result of a reduction in the control voltage U, the tappet moves away from the nozzle at time to and thus releases the nozzle opening. At the time ti, the control voltage U2 corresponds to the no-load voltage of the piezo actuator, i.e. H. the piezo actuator is no longer expanded. Accordingly, the ram is temporarily in the ejection start position S5. The control algorithm for adjusting the discharge end position S3 to the adjust position S2 · can, as stated, take place during a respective opening and / or closing edge. The control process during a closing edge is described below, that is, starting at time t2.

At time t2, ie at the beginning of the ejection process, an electrical control voltage U is applied to the piezo actuator. The control voltage U is continuously increased, with a predominantly linear relationship between control voltage U and time t being established (upper part of FIG. 10; time t2 to t4). With the application of the control voltage U at time t2, the plunger is expanded by the Piezo actuator deflected again in the direction of the nozzle. In the period tz to tz, a first, predominantly constant ram speed is initially established (corresponds to m1 '). Accordingly, a first (speed) ratio is formed between the change in the control voltage U of the piezo actuator and the ram speed resulting therefrom.

At the point in time tz, the ram speed suddenly slows down, a new ram speed (corresponding to m4 ') being set. In this case the ram speed approaches zero after tz. At time tz, an electrical voltage II _{3 is applied to} the piezo actuator. However, since the control voltage of the piezo actuator continues to increase continuously after time tz or beyond II ₃ , a new (speed) relationship is established between the change in the control voltage and the ram speed. The point in time tz or the ram position Sr, S ₂ ·, S ₃ at which the change in the (speed) ratio takes place corresponds here to the full contact position Sr of the ram. Since this is an “ideal” and very rigid metering system, the full contact position Sr already corresponds to the ejection end position S ₃ and also the adjust position S ₂ · of the ram.

The electrical control voltage U of the piezo actuator is further increased beyond II ₃ until the expansion voltage Ui is finally applied again to the piezo actuator at time U.

Based on the thus determined full contact position S ₁ and the electrical control voltage II _{3 of} the piezo actuator assigned to this position S ₁ , an actual value of a value representing the sealing position actuator deflection can then be determined. In this case, the value representing the sealing position actuator deflection corresponds to a voltage difference DII ₁ between the maximum electrical control voltage Ui applied to the piezo actuator during operation and the control voltage II _3, which is necessary to move the plunger into the full contact position S ₁ bring to. The sealing position actuator deflection DII ₁ determined in this way, that is to say here the voltage difference DII _{1 of} the control voltage applied to the piezo actuator, has the effect that a sealing force of the plunger against the nozzle is built up from time tz. In other words, the voltage difference DII ₁ is here essentially completely converted into a sealing force of the plunger. In contrast, the remaining portion of the control voltage applied to the piezo actuator, i.e. the difference between II ₃ and U ₂ , is converted into a movement of the plunger, with a (hydraulically) effective stroke Hi being effected here. FIG. 11 shows the method subsection 9-G for an “ideal” non-rigid metering system. Analogous to FIG. 10, a function graph of the time curve of the electrical control voltage U applied to the piezo actuator (in V) over time t (in arbitrary units) is shown schematically in the upper part here, with the control voltage in the lower part for the same period (U) Corresponding ram position S (in pm) is shown.

In FIG. 11, the determination of the sealing position actuator deflection is described on the basis of an opening flank. At the beginning of the recording, an expansion voltage Ui is again applied to the piezo actuator. At the point in time to · the electrical control voltage is reduced, with a pressure built up in the piezo actuator as a result of the expansion slowly starting to decrease. This means that in this period (to · to tr), initially only the sealing force that the plunger exerts against the nozzle is mainly reduced. The electrical control voltage U is reduced from Ui to II3 during this period (to · to tr), the difference between Ui and II3 here corresponding to the sealing position actuator deflection DII2.

In the period to · to tr, in addition to the reduction in the sealing force, there is also a slight plunger movement, the plunger slowly being moved from the ejection end position S ₃ or the adjust position S2 · into the full contact position Sr. This slight slide movement corresponding to the slope m2 'is caused by an elastic (reversible) deformation of components of the dosing system. The continuously decreasing actuator pressure leads to the fact that the components compressed during a previous ejection process, e.g. B. the fluidics unit, can "relax" or "reshape" and align again according to a non-compressed (target) arrangement. Correspondingly, the plunger can return from the ejection end position S ₃ to the full contact position Sr during this period, the control voltage U of Ui and II _{3 being} reduced.

The difference DII2 between these two voltage values Ui, II3 (sealing position-actuator deflection) can therefore also be largely used in such a non-rigid metering system to build up sealing force, with a small proportion of the sealing position-actuator deflection being converted into an elastic deformation of components of the metering system (different from the completely rigid dosing system from FIG. 10).

In order to still achieve a certain sealing force, the spring stiffness of the overall system can be taken into account when calculating the adjust position S2 or compensated (e.g. according to equation 1). For this purpose, for example, the sealing position actuator deflection DII2 can be increased accordingly, with the (hydraulically) effective stroke H2 in turn being able to be reduced.

In the time period tr to tx, the ram position then changes faster than before according to a gradient m1 '. Due to the decreasing actuator voltage U and a spring system of the metering system, the longitudinal extension of the piezo actuator is contracted, the plunger being moved from the full contact position Sr back to the initial ejection position S ₅ . At time t _ß · the control voltage U of the piezo actuator is increased again, the plunger is deflected again in the direction of the nozzle and at time W first the full contact position Sr and with a certain sealing force and a slight movement of the plunger finally at time ts the ejection end position S _{3 is} reached, which corresponds to the adjust position S2 · of the plunger in the regulated state of the dosing system.

In FIG. 12, the method subsection 9-G is now shown for clarification for a “real”, non-rigid metering system on the basis of a closing edge, the basic structure of FIG. 12 corresponding to that of FIGS. 10 and 11 (time profile of the electrical control voltage U above; with the control voltage U corresponding plunger position S below). Starting from the initial ejection position S _{5 of} the plunger, a continuous increase in the electrical control voltage U applied to the piezo actuator results in the plunger being moved at a first speed (corresponds to m1 ') in the direction of the nozzle (period t to ts-) At the point in time ts- the ram speed slows down (corresponding to m3 '), the control voltage being continuously increased. Correspondingly, at ts- a new (speed) ratio arises between the change in the control voltage U of the piezo actuator and the resulting ram speed. The reason for the deceleration of the plunger at time ts- is an initial contact between the plunger and the nozzle, where S ₄ corresponds to the first contact position.

The plunger is deflected beyond S4 against a certain resistance of the nozzle further in the direction of the nozzle until the plunger has "slipped" completely into the nozzle at time te- and thus full contact is achieved (Sr). The slope m3 'thus represents the "sliding in" of the plunger into this nozzle, in particular into the full contact position Sr. To move the plunger from the initial ejection position S ₅ to the full contact position To move position Sr, an electrical control voltage D14 is required, which results from a difference between II ₃ and U ₂ (open circuit voltage) of the piezo actuator.

The control voltage difference ÄlU is part of the maximum control voltage Ui applied to the piezo actuator during operation, with D14 being predominantly fully converted into the (hydraulically) effective stroke H3 of the plunger (and therefore essentially does not lead to the build-up of sealing force). The (hydraulically) effective stroke H3 here also corresponds to the slide movement from the initial ejection position S ₅ to the full contact position Sr.

At full contact (time te-) the (speed) ratio changes again and the plunger is only moved very slightly (corresponding to m2 ') to an ejection end position S ₃ (time tr). As explained with reference to FIG. 11, the slope m2 'is caused by a slight elastic deformation of components of the metering system. In addition, a sealing force of the plunger is predominantly built up in the time period te to tr via the sealing position actuator deflection DII ₃ .

On the basis of the respectively determined actual sealing position actuator deflection (actual value DII ₁ , DII ₂ , DII ₃ , hereinafter only AU) can then in a step 9-VI. (FIG. 7c) it can be determined via a comparison with a nominal value of the value representing the sealing position actuator deflection whether the current sealing position actuator deflection (here the voltage difference DII of the control voltage) is less than the nominal value. If the query shows that the target value is not reached, then according to step 9-VII. a temperature of the expansion element increases, so that the target value of the sealing position actuator deflection (here a certain target voltage difference) is reached.

If the target value is not fallen below (step 9-VI.), In step 9-VIII. checked whether the current sealing position actuator deflection (here the voltage difference DII of the control voltage) exceeds the setpoint. If necessary, then in step 9-IX. the temperature of the expansion element is reduced in order to set the target value of the sealing position actuator deflection. If no deviation of the actual value (DII) of the sealing position actuator deflection from the setpoint is detected, a change is made directly to jump label C without regulating the expansion element. The query of the operating mode follows the jump label C. again (FIG. 7a; step 7-XIV.).

Finally, it is pointed out once again that the dosing systems and control methods for dosing systems described in detail above it is merely a matter of exemplary embodiments which can be modified in a wide variety of ways by the person skilled in the art without departing from the scope of the invention. So z. For example, in the case of the control method explained, it is not always necessary to run through all process steps or the process steps could also be processed in a different order. Furthermore, the control algorithm can also be run through during the other “opening” or “closing” flank not described in the registration. Furthermore, the use of the indefinite article “a” or “an” does not exclude the possibility that the relevant characteristics can also be present several times.

List of reference symbols

I Dosing system 10 actuator unit

I I housing

11a, 11b housing block / components of the housing

12 actuator chamber

13 Chamber of Action

14 Movement Mechanism

15 breakthrough

16 levers

17 Lever contact surface

18 lever bearings

19 actuator spring

20 first actuator / piezo actuator

21 Piezostack

22 Piezo Actuator Housing

23 pressure piece

30 second actuator / expansion element

31 housing (expansion element)

32 expansion body

33 heating device (expansion element)

34 Cooling area / cooling chamber (expansion element)

35 pistons

36 centering element

40 cooling device

41 Coupling point for cooling medium supply 42, 42 ‘, 42" inflow duct (cooling medium)

43 proportional valve (expansion element)

44 proportional valve (piezo actuator)

45 outflow channel (cooling medium)

46 Coupling point for cooling medium discharge

50 fluidic unit

51 Ejection element / ram 52 ram tip

53 ram head

54 Plunger contact surface

55 tappet spring

56 Ram centering piece

57 tappet bearings

58 Tappet seal

60 nozzle

61 outlet opening

62 nozzle chamber

63 tight fit

64 feed channel

65 Reservoir Interface

66 medium cartridge

67 Cartridge holder

68 Compressed air supply cartridge

69 Connection cables

70 clutch mechanism

71 clutch spring

72 bullet

73 plug-in coupling part

74 spherical cap

75 heater (nozzle)

80 control unit (dosing system)

81 Control unit connection cable

82 temperature sensor (medium)

83 temperature sensor (expansion element)

84 Hall sensor

85 magnet

7 First stage of the procedure

7-I. to 7-XIV. Process steps (first process stage)

7-i. Iterative process step (first process step)

7-D, 7-E procedural sub-sections (first procedural section)

8 Second stage of the procedure

8-I. to 8-VI. Process steps (second process stage) 9 Third stage of the procedure

9-1. to 9-IX. Process steps (third process stage)

9-iii., 9-iv. Iterative process steps (third process section) 9-G process subsection (third process section) a Distance (ram tip: nozzle) m1, m2 ratio (ram position: temperature) mT, 2 ‘, 3‘, m4 ‘ratio (ram position: time)

K Tilting axis Hi, H2 _, H3 (hydraulic) effective stroke R Ejection direction RS, RS 'Direction of movement of ram Si, Sr, S2, S2', S3, S4, S5 ram position to- 14 points in time to · - 15 · points in time to · - tr points in time

T 1, T2 temperature (expansion element)

Ui, U ₂ , U ₃ voltage (piezo actuator)

DII, ÄUi, DII2, DII ₃ , DII ₄ voltage difference / actual value

Claims

1. Dosing system (1) for a dosing substance, which dosing system (1) has a housing (11) with a nozzle (60) and a feed channel (64) for dosing substance, an ejection element (51) arranged in the housing (11) for ejecting dosing substance from the nozzle (60), at least one first actuator (20) coupled to the ejection element (51) and / or the nozzle (60), preferably a piezo actuator (20), and at least one second actuator coupled to the first actuator (20) (30), preferably an expansion element (30), wherein the second actuator (30) is designed to adjust a position of the at least one first actuator (20) relative to the housing (11), in particular with respect to the ejector element (51) and / or the nozzle (60) to adjust.

2. Dosing system according to claim 1, wherein the second actuator (30), in particular the expansion element (30), designed and arranged in the housing (11) to a position of the ejection element (51) in relation to the nozzle (60) of the Set the metering system (1), in particular a distance (a) between an ejection tip (52) of the ejection element (51) and a nozzle opening (61) of the nozzle (60).

3. Dosing system according to claim 1 or 2, with at least one heating device (33) assigned to the second actuator (30), in particular the expansion element (30), and / or at least one of the second actuator (30), in particular the expansion element (30), associated cooling device (40) and with a control unit (80) for controlling and / or regulating the heating device (33) and / or the cooling device (40).

4. Dosing system according to one of the preceding claims, wherein the dosing system (1) comprises a sensor arrangement (83, 84) with at least one of the following sensors:

- A temperature sensor (83) assigned to the second actuator (30), in particular the expansion element (30),

- A temperature sensor assigned to the first actuator (20),

- A temperature sensor assigned to the housing (11),

- A movement sensor (84) for determining a movement of the ejection element (51),

- A position sensor (84) for determining a position of the ejection element (51).

5. Dosing system according to one of the preceding claims, wherein the second actuator (30), in particular the expansion element (30), comprises an expansion body (32) and preferably a carrier (35) coupled therewith and / or wherein the second actuator (30) for a positioning of the first actuator (20), preferably by means of the transmitter (35), is coupled to the first actuator (20) in an axial direction.

6. Dosing system according to one of the preceding claims, wherein the dosing system (1) comprises at least one force sensor to a force exerted on the first actuator (20), in particular by means of the second actuator (30), particularly preferably by means of the expansion element (30) to determine, preferably in order to detect a sealing force of the ejection element (51) based thereon.

7. A method for controlling a metering system (1) for a metering substance, which metering system (1) has a housing (11) with a nozzle (60) and a feed channel (64) for metering substance, an ejection element (51) arranged in the housing (11) for ejecting dosing substance from the nozzle (60), at least one first actuator (20) coupled to the ejection element (51) and / or the nozzle (60), preferably a piezo actuator (20), and at least one to the first actuator (20) ) coupled second actuator (30), preferably an expansion element (30), wherein the second actuator (30) is controlled and / or regulated in such a way that a position of the at least one first actuator (20) relative to the housing (11), in particular with respect to the ejection element (51) and / or the nozzle (60).

8. The method for controlling a dosing system according to claim 7, wherein for controlling and / or regulating the second actuator (30), in particular the expansion element (30), a temperature of the second actuator (30), in particular a temperature of the expansion element (30), is preferably controlled and / or regulated by means of at least one heating device (33) assigned to the second actuator (30) and / or by means of at least one cooling device (40) assigned to the second actuator (30).

9. The method for controlling a dosing system according to claim 7 or 8, wherein the second actuator (30), in particular the expansion element (30), is controlled and / or regulated in such a way that the ejector element (51) is in an Adjust- Position (S2, S2) of the ejection element (51) is brought, in which preferably the ejection tip (52) of the ejection element (51) has a certain pressing force into the nozzle (60).

10. A method for controlling a dosing system according to one of the preceding claims 7 to 9, wherein for controlling and / or regulating the second actuator (30), preferably for controlling and / or regulating the expansion element (30), in particular for setting an adjust position (S2, S2), at least one of the following operating parameters of the dosing system (1) is taken into account:

- a temperature of the second actuator (30), in particular a temperature of the expansion element (30), particularly preferably a temperature of an expansion body (32),

- a position of the ejection element (51) in the metering system (1), in particular a position of a lever (16) coupled to the ejection element (51),

- a deflection of the first actuator (20), preferably a control signal of the actuator (20),

- a temperature of the first actuator (20),

- a temperature of the housing (11),

- an amount and / or a weight of the dosing substance to be dispensed from the dosing system (1) during a respective ejection process,

- a signal from a flow sensor for dosing substance,

- calibration data of the dosing system (1),

- a sealing force.

11. A method for controlling a dosing system according to one of the preceding claims 9 or 10, wherein the second actuator (30), in particular the expansion element (30), is controlled and / or regulated in such a way that an ejection end position (S ₃ ) of the ejection element (51) corresponds to an adjust position (S2, S2) determined in a previously performed adjustment process during operation of the metering system (1).

12. The method for controlling a dosing system according to claim 11, wherein in an adjustment process for setting the adjust position (S2, S2) of the ejector element (51), a control algorithm with at least the following steps is run through:

- Setting a maximum deflection of the first actuator (20),

- Setting an adjustment start temperature of the second actuator, in particular an adjustment start temperature of the expansion element (30), preferably by means of cooling the expansion element (30),

- Heating of the second actuator (30), in particular heating of the expansion element (30), until full contact is detected between the ejection element (51) and the nozzle (60) and determining a full contact position (Si, Sr) of the ejection element (51) and / or a full contact temperature (Ti) which is assigned to the full contact position (Si, Sr), and / or heating the second actuator (30), in particular heating the expansion element (30), until a maximum system deflection of the first actuator (20) and the second actuator (30) is reached and a system end contact position of the ejection element (51) and / or a system End contact temperature assigned to the system end contact position

- Determination of an adjust position (S2, S2) of the ejection element and / or an adjust temperature (T2), which is assigned to the adjust position (S2, S2), wherein to determine the adjust position (S2, S2) and / or the adjust temperature (T2), the full contact position (Si, Sr) of the ejection element (51) and / or the full contact temperature (Ti) or the system end contact position of the ejection element (51) and / or the system -End contact temperature and optionally at least one adjust parameter are taken into account,

- optionally transferring the ejection element (51) to the adjust position (S2, S2).

13. A method for controlling a dosing system according to claim 11 or 12, wherein for

Regulating the discharge end position (S ₃ ) during operation, a control algorithm with at least the following steps is run through:

- Setting an ejection end position (S ₃ ) of the ejection element (51),

- Determination of a position of the ejection element (51) as a function of a deflection of the first actuator (20) during a retraction movement of the ejection element (51), in particular as a function of an electrical control voltage (U) applied to the first actuator (20),

Determination of an actual value (DII) of a value representing a sealing position actuator deflection, the ejection element (51) in the sealing position actuator deflection by a certain minimum beyond the full contact between the ejection element (51) and the nozzle (60) into a sealing seat (63) ) the nozzle (60) is pressed,

- Control and / or regulation of the second actuator (30), preferably control and / or regulation of the expansion element (30), in particular as a function of a difference between the actual value (DII) of the value representing the sealing position actuator deflection and a target value of the sealing position Actuator deflection representing value, for setting the setpoint value of the value representing the sealing position actuator deflection, the setpoint value of the sealing position actuator deflection representing value of the adjust position (S2, S2) of the ejection element (51) is assigned.

14. A method for controlling a metering system according to claim 13, wherein a temperature of the second actuator (30), in particular a temperature of the

Expansion element (30), in the event of a positive deviation of the actual value (DII) of the value representing the sealing position actuator deflection from the setpoint value of the value representing the sealing position actuator deflection is reduced and / or the temperature of the second actuator (30), in particular the temperature of the expansion element (30), with a negative deviation of the actual value (DII) of the sealing position

The value representing the actuator deflection is increased from the setpoint value of the value representing the sealing position actuator deflection.

15. A method for controlling a dosing system according to claim 13 or 14, wherein the operation of the dosing system (1) at regular intervals, preferably at each

Ejection process of the ejection element (51), a difference between the actual value (DII) of the value representing the sealing position actuator deflection and the setpoint value of the value representing the sealing position actuator deflection is determined.