Field of the invention

The invention relates to dosing units for infusion pump devices, and infusion pump devices with such a dosing unit, according to the preamble of the independent claim.

State of the art / Background of the invention

Devices for the automated release of liquid medica ments are normally used with patients who have a continuous and in the course of the day varying need of a liquid medicine which can be administered by infusion. Specific applications are, for example, certain pain therapies, cancer therapies and the treatment of diabetes mellitus, in which computer controlled infusion pump devices are used. Such devices are particularly useful for ambulatory therapy, and are generally carried attached on or near the body of a patient. The medicine reservoir often comprises medicine supply sufficient for one or several days. The liquid medicament is supplied to the patient ^' s body from the medicine reservoir through an infusion cannula or an injection needle.

Ambulatory infusion pump devices are typically of the syringe driver type, where the liquid medicament to be administered to the patient is stored in a cylindrical glass cartridge or ampoule acting as the liquid medicament reservoir, and is conveyed to the body of the patient by displacing a plunger within the cylinder. An example of such an infusion pump device is disclosed for example in WO 01 /83008 A 1 . A cylinder of the dosing unit comprises the complete reservoir of liquid medicament of the infusion pump device. A plunger plug arranged in the cylinder is unidirectionally displaced along the cylinder axis by a drive system via a shaft or threaded spindle.

A number of drawbacks of such a design are known in the art. In particular, such pump devices have a limited precision, because they involve pumping very small volumes, typically in the nanolitre range, out of a cartridge having an overall volume in the range of millilitres, typically e.g. 3 ml. Thus, to achieve a precise dosing of the liquid medicament, it is necessary to very precisely displace the plunger. Already small deviations can lead to over-dosing or underdosing. Furthermore the forces needed to actuate the plunger are comparably high due to the friction between the walls of the glass cartridge and the sealing of the plunger. This leads to demanding requirements for the drive system and the mechanical parts involved, as well as the control unit of the pump. As a consequence such infusion pump devices are expensive.

Another problem is the lower limit of the length of such an infusion pump device. The complete supply of liquid medicament has to be stored in the cartridge acting as the pump cylinder. The cross-sectional area of the plunger has to be below a certain limit, for precision reasons and in order to limit the device thickness, which is known to be a particularly critical dimension with respect to comfort and discreetness during a pplication. The minimum overall length of the device is then essentially given by the resulting minimum length of the cylinder, which is detrimental to the provision of compact infusion pumps. Particularly in self-administration of medicaments, for example insulin, the patients using the medicament in question and administering it themselves by means of an infusion pump are increasingly emphasizing convenience and discretion, which restricts the acceptable size and weight of such devices. Particular the overall length, width and thickness should be as small as possible, in order not be evident through clothing and to be carried as comfortable as possible.

Alternative approaches have been proposed, in which a separate dosing unit is provided downstream from the liquid medicament reservoir. Since the primary reservoir does not have to fulfil additional functions, its dimensions can be optimized in view of the compactness of the infusion pump device. Such a dosing unit can comprise for example a small piston pump, specially designed for precise metering of small volumes. The small piston pump retrieves liquid medicament from the larger primary reservoir, e.g. a collapsible reservoir, and conveys the liquid medicament in a precise manner to the injection site on the body of the patient. When filled, the cylinder of the piston pump acts as a secondary reservoir, holding a restricted amount of liquid medicament. When the cylinder is empty, the piston pump retrieves new liquid medicament from the primary reservoir.

The liquid medicaments that are admin istered by liquid infusion pump devices are generally highly effective. The accuracy of the dosing unit is therefore of utmost importance. Such accuracy can be ensured by using high quality components, as well as an appropriate design of the various parts of an infusion pump device. Particularly it is advantageous to reduce the number of different interacting elements. EP 2 1 63273 A 1 of the applicants, the disclosure of which is hereby included by reference in its entirety, discloses a piston pump based dosing unit for an infusion pump device with a 4/3 or 3/3 way valve system arranged at a front end of the cylinder of the dosing unit. A plunger arranged in the cylinder of the dosing unit can be bidirectionally displaced along the cylinder axis by a spindle drive system. In one state of the valve, an inlet conduit fluidly connected to the primary reservoir is fluidly connected to the cylinder cavity, and an outlet conduit fluidly connected to the infusion tubing is disconnected from the dosing unit. This state of the valve is applied during the refill mode, when the dosing unit retracts the plunger and sucks liquid medicament from the primary reservoir into the pump cylinder / secondary reservoir. In a second state of the valve, the cylinder of the dosing unit is fluidly connected to the outlet conduit, thereby establishing a fluid connection to the body of the patient. The inlet conduit is disconnected from the dosing unit. This valve state is applied during the pump mode, when liquid medicament is conveyed from the secondary reservoir in the cylinder of the dosing unit to the subcutaneous tissue of the patient. The valve thus either allows the dosing unit to retrieve liquid from the primary reservoir, or to convey liquid from the secondary reservoir of the dosing unit toward the patient.

The valve is realized as a rotatable cylinder acting as a valve member, mounted in a fixed valve seat. The cylinder member of the valve is frictionally connected to the plunger. By rotating the plunger along the cylinder axis, the actuating means of the plunger indirectly actuate also the valve member, by rotating the cylinder / valve member within the stationary valve seat. Thus no separate actuator is needed for the valve. Furthermore the valve system and the piston pump are coupled such that in the pump mode, the valve will automatically be in the pump state, and in the refill mode, the valve will automatically be in the retrieving state. Thus also no additional control means is needed for the valve.

In order to rotate the cylinder and to switch the valve, the plunger has to exert a rotational torque on the cylinder member. At the same time the rotational torque exerted on the plunger by a drive unit has to be translated into a linear displacement of the plunger along the cylinder axis. For that purpose the plunger shaft is provided with an outer thread that interacts with an inner thread provided on the cylinder. The dosing u nit is designed such that the static f rictional force between plunger and cylinder member ( including friction between plunger plug and cylinder wall and friction of the thread ) is larger than the static friction between cylinder member and valve seat. When the drive unit rotates the shaft into one direction, the cylinder is frictionally coupled to the rotating plunger and rotates in the valve seat until finally reaching an end position, where its further rotation is mechanically blocked by a stopper. The plunger is now frictionally decoupled from the cylinder member, and any further rotation of the plunger is translated by the threads into a linear d isplacement along the cylinder axis. When the rotation of the plunger is reversed, the cylinder member is no longer rotationally blocked in the valve set, and plunger and cylinder member are frictionally coupled again. The cylinder member thus rotates in the valve seat in the reverse direction, actuated by the drive unit via the plunger, until a second stopper is reached, corresponding to the second valve state. The plunger is decoupled again from the blocked cylinder member, and is now linearly displaced along the cylinder axis in the opposite direction. The design of such a combined piston pump / valve system is named "valve before plunger" design, since the valve is actuated before the plunger is actuated.

In an infusion pump device as discussed above, all parts that come into contact with liquid medicament, as well as parts that are subject to friction, are advantageously arranged in a disposable subunit. Prior to use of the infusion pump device, a fresh disposable subunit is coupled to a reusable subunit, comprising for example the electronics, the drive system, the battery, and all other parts that are not prone to contamination or wear, and can be used over a longer time period.

Since the spindle that actuates the plunger of the pump is typically made from a polymer material, and thus would be subject to wear if used over a long time period, it is advantageously also part of the disposable subunit. However, if a simple threaded rod coupled to the plunger would be used as the spindle of the spindle drive, the length of the disposable subunit would depend on the plunger position. Such a design would complicate the coupling of the disposable subunit to the reusable subunit, namely the coupling of the spindle to the drive motor.

In the dosing unit shown in EP 2 1 63273 A 1 , the length of the disposable subunit is hold constant. The plunger spindle of the dosing unit comprises a plunger shaft attached to the plunger, and a coaxial plunger driving rod arranged in a longitudinal bore along its axis of the plunger shaft. The driving rod can be linearly shifted along the longitudinal bore. The cross- section of the driving rod and the longitudinal bore are chosen such that a rotational torque is effectively transmitted from the driving rod to the plunger shaft. The coupler element can be coupled to a driving unit of a reusable subunit. The linear displacement of the plunger during the spindle actuation is compensated by the two-part spindle. While the plunger shaft is linearly shifted together with the plunger, the driving rod remains on place in regard to the drive unit. The transmission of the rotational torque from the drive unit to the plunger shaft is effected by the rotational coupling between plunger shaft and driving rod.

A spindle drive, as it is also present in such an advantageous prior art dosing unit, unavoidably has a certain thread lash. When spindle rotation is reversed, the flanks of the inner thread and the outer thread are slightly shifted in regard to each other along the longitudinal axis. In a standard single-reservoir syringe-type infusion pump, thread lash is not relevant, since the spindle drive in unidirectional. Thus after priming of the pump system there is no reversal of the spindle rotation direction. Thread lash can be potentially detrimental to metering precision for secondary-reservoir piston pump dosing units, where the rotation direction is repeatedly reversed after priming. After switching the rotational direction of the plunger, for a small rotation angle of the plunger the threads are not coupled, resulting in a rotation of the plunger without linear displacement. Furthermore the linear force exerted on the plunger may have to counteract an opposite force due to a pressure differential in the cylinder cavity. Depending on the circumstances this can lead to a small linear displacement of the plunger within the cylinder, without rotation. As a result, the metering precision of such a dosing unit may be restricted.

This precision reducing effect of the thread lash is particularly relevant when the rotation angle and/or the linear displacement of the plunger a re used to determine the position of the plunger plug within the cavity and/or the volume of retrieved/conveyed liquid volume. Although such a metering measurement method is very precise, and can take into account various effects, it cannot counterbalance thread lash, since thread lash cannot be detected such a method.

Counter spindle drives are used to avoid thread lash in high precision linear motors, for example for machining devices such as lathes. However, such complex drives are not applicable for infusion pump devices, since they are too voluminous and complex.

In one embodiment of a dosing unit as described in EP 2 1 63273 A 1 , thread lash is reduced by realizing the plunger shaft as two elastic longitudinal legs, which are dimensioned such that when the plunger is arranged within the cylinder, the legs are radially deformed toward the cylinder wall. As a result there is a constant biasing between the inner and the outer thread flanks, thereby reducing thread lash. However, the constant mechanical stress of the polymer material of the plunger shaft has certain disadvantages in regard to long-time stability. Creep deformation of the biased polymer during storage reduces the bias force over time, and as a result reduces the possible shelf life time of such a dosing unit.

In the dosing unit described in EP 2 1 63273 A 1 , the f rictional coupling between cylinder valve member and plunger that is necessary for the switching of the valve is the result of the con- stant frictional interaction between cylinder and plunger. Said friction force is always larger than the friction force between cylinder valve member and valve seat. Such an approach is advantageous in regard to reduced complexity of the control and drive system. However, the increased friction force, which has to be set larger than for a comparable piston pump without valve actuation, has to be overcome by the drive unit all the time when the piston pump is activated. This increases energy consumption of the drive motor, thereby reducing battery lifetime of the ambulatory infusion pump device.

There is accordingly a need to further improve the precision of dossing units for infusion pump devices.

Objects of the Invention It is the overall objective of the present invention to provide dosing units and ambulatory infusion devices comprising dosing units that improve the state of the art with respect to the above-mentioned and other problems.

Particularly such dosing units and ambulatory infusion devices should provide high metering precision, low energy consumption, and long shelf time. They should be reliable and cost effi- cient in large scale manufacture.

For dosing units for which valve and piston pump are realized as a combined structure, both being actuated by the rotating plunger, the valve switching process should be precise.

According to the present invention, these and other objects are achieved through the features of the independent claims. In addition, further advantageous embodiments follow from the dependent claims and the description. Summary of the invention

The present invention may comprise one or more of the features recited in the attached claims, and /or one or more of the following features and combinations thereof.

A dosing unit for an infusion pump device comprises a piston pump with a pump cylinder, a plunger arranged within said cylinder, and a plunger driving part provided for transmitting rotational torque from a driving unit to the plunger without itself being linearly displaced. The cylinder, the plunger and the plunger driving part are coaxially arranged along a longitudinal axis and rotatable around said axis in regard to static parts of the dosing unit. The plunger has a shaft with a thread and the cylinder has a threaded sleeve part with a thread. One of the two threads is an outer thread and the other one is a n inner thread, said two threads engaging with each other in such a way that a rotational movement of the plunger around the longitudinal axis results in an additional linear displacement of the plunger along said longitudinal axis. The plunger driving part has a driving rod that is arranged in a longitudinal bore of the plunger shaft, the driving rod being linearly displaceable within the longitudinal bore along the longitudinal axis, and being rotationally engaged with the plunger shaft. One or more first coupling parts are mounted to or are integral with the cylinder, and one or more second coupling parts are mounted to or are integ ral with the plunger driving part and/or the plunger. The first and second coupling parts interact in such a way that

- the first and second coupling parts are bidirectionally switchable between a first state and a second state, by reversing the rotation direction of the plunger driving part;

- the first and second coupling parts are unidirectionally switchable from the first state to the second state, by mechanically blocking cylinder rotation or actuating the first coupling part; and

- the cylinder is rotationally coupled to the plunger driving part in the first state of the first and second coupling parts; and not rotationally coupled in the second state.

Alternatively or in addition one or more first coupling parts are mounted to or are integral with the cylinder and/or the plunger driving part, and one or more second coupling parts are mounted to or are integral with the plunger driving part and /or the plunger; the first and second coupling parts interacting in such a way that the cylinder is rotationally coupled to the plunger on certain linear positions of the plunger in regard to the cylinder and is not rotation- ally coupled to the plunger on the other positions.

Alternatively or in addition one or more first coupling parts are mounted to or are integral with the cylinder, and one or more second coupling parts are mounted to or are integral with the plunger driving part; the first and second coupling parts interacting in such a way that the cylinder is rotationally decoupled from the plunger driving part on certain angular orientations of the cylinder in regard to static parts of the dosing unit, and is rotationally coupled on the other orientations.

In a dosing unit according to the disclosure the coupling parts are advantageously, at least partly, part of the plunger driving part and do a direct (selective) torque transmission from the plunger driving part to the cylinder. Alternatively the coupling parts are, at least partly, part of the plunger and do an indirect (selective) torque transmission from the plunger driving part to the cylinder, via the plunger. The plunger driving part is distinct from both cylinder and plunger.

A functional principle of the disclosed dosing unit is that the plunger driving part receives a rotational torque from some drive and provides that torque either to the plunger only (decoupled state) or to both plunger and cylinder (coupled state). The plunger driving part accordingly fulfils the functions of transforming a pure rotational drive movement into a screwlike combined rotational and linear movement of the plunger, and selectively rotationally coupling the cylinder to the drive.

Such an embodiment of a dosing unit has reduced energy consumption, since the cylinder can be decoupled from the drive unit, as long as the valve does not have to be switched. Fewer parts are necessary, which reduces costs.

In an advantageous embodiment of such a dosing unit, a first coupling part is mounted to or is integral with the cylinder, and a second coupling part is mounted to or is integral with the plunger driving part . The first and/or the second coupling parts comprise one or more bistable elements that can be in a first configuration where the bistable elements rotationally couple the first and second coupling parts by static friction or positive locking when the plunger driving part rotates clockwise, and do not rotationally couple the first and second coupling parts when the plunger d riving part rotates counter-clockwise. In a second configuration the bistable elements rotationally couple the first and second coupling parts by static friction or positive locking when the plunger driving part rotates counter-clockwise, and do not rotation- ally couple the first and second coupling parts when the plunger driving part rotates clockwise.

In the advantageous embodiment mentioned above, where the first and second coupling parts are unidirectionally switchable from a first state to a second state, by mechanically blocking cylinder rotation, such a change occurs, more generally spoken, if the torque for rotating the cylinder exceeds a maximum torque that can be transmitted via the coupling from the bistable friction elements to the cylinder. The design is advantageously such that this change occurs only in the mechanically blocked state, where the torque for further rotating the cylinder becomes essentially infinite.

In a particularly advantageous embodiment of this previous dosing unit the bistable elements are friction elements that are switchable between two configurations, and that the rotational coupling is a static frictional coupling. More advantageously the bistable friction elements are switchable between the two configurations by reversing the rotation direction of the plunger driving part in case the first and second coupling parts are not rotationally coupled; and by reversing the rotation direction of the plunger driving part and blocking cylinder rotation in case the first and second coupling parts are rotationally coupled. Even more advantageously, cylinder rotation is blocked on certain angular orientations of the cylinder in regard to the static parts of the dosing unit. In another particularly advantageous embodiment of the previous dosing unit, the bistable elements are ratchet mechanisms that are switcha ble between two configurations, and that the rotational coupling is given when the ratchet mechanism is locked. Advantageously the bistable ratchet mechanisms are switchable between the two states by reversing the rotation direction of the plunger driving part in case the ratchet mechanism is locked; and by reversing the rotation direction of the plunger driving part and additionally actuating the ratchet mechanism in case the ratchet mechanism is not locked. In an even more advantageous variant of such a dosing unit, the ratchet mechanism is actuated by switching elements mounted to or being integral with the static parts of the dosing unit.

In a further advantageous embodiment of the dosing unit, the first coupling parts comprise first ramps provided on the plunger driving rod , and the second coupling parts comprise second ramps provided on a structure pivotably mounted on the plunger shaft. The structure car- ries portions of the outer thread. The first and second ramps are arranged such that on certain linear positions of the plunger in regard to the cylinder some of the first ramps abut some of the second ramps, and press the outer thread portions radially outwards onto the inner thread of the cylinder, thereby frictionally coupling the cylinder and the plunger.

In yet a further advantageous embodiment of the dosing unit, the one or more first coupling parts are first friction elements mounted to or being integral with the cylinder, and the one or more second coupling parts are second friction elements mounted to or being integral with the plunger. At certain longitudinal positions of the plunger in regard to the cylinder one of the first friction elements frictionally engages with one of the second friction elements, thereby frictionally coupling the cylinder and the plunger. Advantageously the one or more first friction element is a hollow cylinder, and the one or more second friction element is a friction cylinder, which frictionally engages with the hollow cylinder when the friction cylinder is located in the hollow cylinder.

In even another advantageous embodiment of the previous dosing unit, the one or more first coupling parts are first stopper elements mounted to or being integral with the cylinder, and the one or more second coupling parts are second stopper elements mounted to or being integral with the plunger. At certain longitudinal positions of the plunger in regard to the cylinder one of the first stopper elements abuts with one of the second stopper elements, thereby blocking the further linear displacement of the plunger, and releasably jamming the inner thread of the cylinder and the outer thread of the plunger. Advantageously the stopper elements are disks.

Another variant of an advantageous dosing unit has a cylinder coupling part as the first coupling part and a plunger coupling part as the second coupling part. The cylinder coupling part comprises first locking elements and the plunger coupling part comprises second locking elements, which releasably lock the plunger to the cylinder at certain longitudinal positions of the plunger in regard to the cylinder.

In yet another advantageous embodiment of the dosing unit, a first coupling part is mounted to or is integral with the cylinder, and a second coupling part is mounted to or is integral with the plunger driving part. The two coupling parts are frictionally coupled. The frictional coupling is releasable by switching elements mounted to or being integral with the static parts of the dosing unit. A dosing unit without thread-lash is advantageous for several reasons. The metering precision is increased due to the reduction of metering errors due to uncontrolled plunger displacement. Furthermore the separation in time of the valve switching process and the plunger displacement process is more precise, since the thread friction force, adding to the friction force between cylinder valve member and plunger, remains essentially constant when the plunger rotation direction is reversed.

A self-biasing polymer plunger shaft for thread-lash reduction has the disadvantage that its bias force deteriorates over time in an irreproducible manner, which eventually reduces the acceptable shelf time of a disposable dosing unit prior to first use in an ambulatory infusion pump device. In an advantageous dosing unit according to this disclosure, a separate bias force element is provided, thereby allowing using a plunger without detrimental mechanical stress.

In a particularly advantageous variant of the dosing units discussed so far, a separate bias force element is provided that biases the two threads in regard to each other along the longitudinal axis, such that the threaded engagement of inner thread and outer thread is free of play independent of a direction of a rotational movement and linear displacement of the plunger in regard to the cylinder. Advantageously the plunger thread is an outer thread and the cylinder thread is an inner thread.

In one advantageous embodiment of such dosing units, the bias force element subjects the plunger shaft to a force perpendicular to the longitudinal axis, thereby pressing a portion of the plunger thread onto a portion of the cylinder thread. Advantageously the bias force element comprises a radially biased flat surface that abuts the lateral surface of an outer one of the two threads.

In another advantageous embodiment of such dosing units, one or more portions of the cylinder thread or the plunger thread are pivotably mounted on the cylinder, or on the plunger shaft, respectively. Advantageously a spring element is provided, more advantageously a tension ring, which radially biases the pivotably mounted thread portions toward the other thread .

In yet another advantageous embodiment of such dosing units, the bias force element comprises a tensioned segment of wire that is mounted to the cylinder or the plunger and is ar- ranged in such a way that it is located in a groove segment of the outer thread and exercises a bias force perpendicular to the longitudinal axis.

In a further advantageous embodiment of such dosing units, the bias force element comprises a threaded element, which is coaxially mounted on the first threaded sleeve or on the plunger shaft, and is longitudinally shiftable in regard to the first threaded sleeve or the plunger shaft, respectively. The threaded element has a thread portion engaging with the plunger thread or the cylinder thread, respectively. Further the threaded element has a spring element that subjects the threaded element to an axial bias force in regard to the first threaded sleeve or the plunger shaft, respectively.

In yet a further advantageous embodiment of such dosing units, the bias force element comprises one or more spring elements with inner or outer thread segments, such that said inner or outer thread seg ments are radially biased towa rd the outer or inner thread. The inner or outer thread segments act as the inner or outer thread, respectively.

It is advantageous that in the dosing units as discussed the bias force element is elastic.

The bias force element can be made from a material that is different from the material of the cylinder and/or the plunger.

The bias force element can be made from metal, and alternatively or in addition the cylinder and/or the plunger can be made from polymer.

An advantageous infusion pump device according to the disclosure comprises a dosing unit according to the disclosure.

Brief description of the drawings

In order to facilitate a fuller understanding of the present invention, reference is now made to the appended drawings. These references should not be construed as limiting the present invention, but are intended to be exemplary only.

Figure 1 schematically shows a possible embodiment of an advantageous dosing unit according to the disclosure, (a ) in a longitudinal section along the cylinder axis, and ( b) in a cross section through the plunger shaft and the plunger driving rod along plane A-A. schematically shows a detail view of a similar thread lash reducing arrangement as shown in Figure 1 . schematically shows other variants of thread lash reducing arrangements in a dosing unit according to the disclosure. depicts a further embodiment of an advantageous dosing unit without thread lash, with a ring-like metal spring element as a radial bias element, (a ) in a top view, ( b) in a longitudinal section along plane B-B, and in a cross-section along plane A-A,

(c) with the plunger shaft, and (d ) without the plunger shaft. The plunger is shown (e) without the plug sealing element material in top view, (f) in a cross- section along plane C-C, and (g ) in side view with view along the longitudinal axis on the bore. The radial bias force element is shown in ( h ). depicts another embodiment of an advantageous dosing unit, with a ring-like metal spring element as a radial bias element, (a ) in top view, ( b) in a longitudinal section along plane A-A, and (c) in a cross-section along plane B- B. The radial bias force element is shown in (d ). schematically shows a further embodiment of a radial bias force element, (a ) in a longitudinal view on the split end of the plunger shaft, and ( b) in a side view on the end of the plunger shaft. depicts yet another advantageous embodiment of a plunger with thread lash reduction, having three pivotably mounted thread portions, (a ) in a perspective view, ( b) in a longitudinal view, (c) in a longitudina l section along plane A-A, and

(d ) in a cross-section along plane B- B. shows a further variant of a thread lash reduction arrangement, with four threaded claws at the distal end of the cylinder engaging with a threaded plunger shaft, (a ) in a side view with view on the distal end, and ( b) in a longitudinal section along plane A-A.

Figure 9 schematically depicts yet a further embodiment of a dosing unit with thread lash reduction arrangement, in which three biased spring elements act as an radially biased outer thread, with the dosing unit (a ) in a perspective view, and ( b) in a detail view of a longitudinal section, with a distal sleeve (c) in a longitudinal view, and (d ) in a perspective view, and with an axial bias force element with three radially biased spring elements (e) in a longitudinal view, and (f) in a perspective view.

Figure 1 0 shows another advantageous variant of a thread lash reduction arrangement, in which a biased wire is used as a radial bias force element. The interaction of the biased wire, the threaded plunger shaft, and the thread portion on the cylinder surface is schematically depicted in (a ). A distal portion of the cylinder is shown in ( b), and a cross-section along plane A-A in (c).

Figure 1 1 discloses a further variant of a thread lash reduction arrangement, with an axially biased threaded sleeve, (a ) in a longitudinal section through plunger shaft, threaded sleeve and axial bias force element, and (b) in a schematical detail view of the interacting thread portions, (c) discloses yet a further variant of a thread lash reduction arrangement, with an axially biased threaded plunger shaft, a longitudinal section through plunger shaft, threaded sleeve and axial bias force element.

Figure 1 2 schematically shows a longitudinal section of an advantageous embodiment of a dosing unit with controlled friction between plunger and cylinder, (a ) with the plunger in a start position, ( b) with the plunger in a medium position, and (c) with the plunger in a maximum position. A detail of Figure 1 2 (a ) is shown in (d ), explaining how the driving rod controls the friction between plunger and cylinder.

Figure 1 3 schematically shows the plunger of Figure 1 2, (a ) in a longitudinal section along plane A-A, ( b) in a cross-section along plane B - B, and (c) in a cross-section along plane C-C.

Figure 1 4 schematically shows the driving rod of Figure 1 2, (a ) in a side view, ( b) in a top view, and (c) in a cross-section along plane D- D.

Figure 1 5 schematically shows a longitudinal section of a variant of a plunger shaft and driving rod that allows valve switching in intermed iate positions. Figure 1 6 schematically shows another embodiment of a dosing unit with controlled friction between plunger and cylinder, (a ) with the plunger in a start position, and ( b) with the plunger in a maximum position. A detail of Figure 1 6(a ) is shown in (c) , explaining how the driving rod controls the friction between plunger and cylinder.

Figure 1 7 schematically shows yet another embodiment of a dosing unit with controlled friction between plunger and cylinder, (a ) with the plunger in a start position, and

( b) with the plunger in a maximum position. A detail of Figure 1 7 (a ) is shown in

(c) , explaining how the driving rod controls the friction between plunger and cylinder.

Figure 1 8 schematically shows a further variant of the dosing unit with controlled friction between plunger and cylinder, (a ) with the plunger in a start position, and ( b) with the plunger in a maximum position.

Figure 1 9 schematically shows yet another variant of a dosing unit with controlled friction between plunger and cylinder, and thread lash reduction, with the plunger in an intermed iate position.

Figure 20 schematically depicts a longitudinal section of another advantageous embodiment of a dosing unit, in which the cylinder is positively locked to the plunger at certain longitudinal positions, (a ) with the plunger in a start position, ( b) with the plunger in a medium position, and (c) with the plunger in a maximum position.

Figure 2 1 schematically depicts another advantageous variant of a dosing unit: (a ) in a longitudinal section with the plunger in a start position, ( b) in a longitudinal section perpendicular with the plunger in a maximum position, (c) in a detail view of (a ), and (d ) in a detail view of ( b).

Figure 22 schematically depicts a longitudinal section of another advantageous variant of a dosing unit with the plunger in the start position, in which the cylinder can be re- leasably positively locked to the plunger at certain longitudinal positions.

Figure 23 schematically shows an advantageous coupling system that allows switching the valve of a dosing unit at any longitudinal position of the plunger, (a ) in a cross section, and ( b) to (e) in detail views of different steps during the valve switching. Figure 24 schematically shows another advantageous coupling system that allows switching the valve of a dosing unit at any longitudinal position of the plunger, (a ) in a bottom view of the driving rod, ( b) in a side view of the driving rod, and (c) in a detail of a cross-section of the coupling part of the driving rod coupled to the cylinder wall, (d ) to (g ) show detail views of different steps during the valve switching.

Figure 25 schematically shows cross-sections of different embodiments of plunger shafts and driving rods, (a ) without and ( b) to (d ) with rotational play.

Figure 26 shows a perspective view of an advantageous dosing unit with the cylin der/plunger combination with thread lash reduction arrangement as shown in Figure 5, and with a cylinder/driving rod coupling arrangement similar to Figure 24.

Figure 27 shows the different steps during valve switching with the dosing unit of Figure 26.

Figure 28 schematically shows subsequent steps of an advantageous approach to realize a controlled coupling between cylinder and driving rod, based on a bistable ratchet mechanism.

Figure 29 schematically shows another embodiment of a controlled coupling between cylinder and driving rod, (a ) in a perspective view on the interacting coupling parts, and ( b) in a perspective view of the cylinder coupling part alone.

Description of embodiments of the invention

An advantageous embodiment of a dosing unit 1 according to the invention is schematically depicted in Figure 1 . A cylinder valve member 2 is rotatably mounted in a stationary valve seat 1 2. A plunger 3 with a plug 3 1 and a shaft 32 is arranged in the cylinder 2. The plunger plug 3 1 sealingly closes the cylinder, thereby defining a metering cavity 1 1 between the cylinder head 2 1 and the plug. In the figure, the valve formed by the valve seat 1 2 and the cylinder valve member 2 is in one of its two operational valve states, where an inlet 1 2 1 is f luidly connected to the metering cavity 1 1 through an opening 2 1 1 in the cylinder head. The inlet 1 2 1 is fluidly connected to a primary reservoir of an infusion pump device ( not shown ). A downstream outlet 1 22 toward an infusion set ( not shown ) is disconnected from the metering cavity 1 1 . The plunger plug 3 1 is attached to a plunger shaft 32, which is provided with an outer thread 33 that interacts with an inner thread 23 arranged on the cylinder. The plunger shaft 32 is provided with a longitudinal bore 322 along its axis, having a square cross-section, in which a rod 41 of a plunger driving part 4 is arranged. The plunger driving rod 41 has a square cross- section corresponding to the longitudinal bore 322 of the plunger shaft. Thus the rod 41 can be shifted with only minimum friction in the longitudinal bore 322, while at the same time efficiently transmitting a rotational torque around the axis 20 from the plunger coupler 4 to the plunger 3. Plunger shaft and plunger driving rod are designed such that the bore 322 is vented toward atmosphere.

The plunger shaft 32 and the plunger driving rod 41 together form the plunger spindle of the dosing unit. The plunger driving part 4 is rotationally coupled to a driving unit of the infusion pump device ( not shown ). In case the dosing unit is designed as a disposable element, which is intended to be replaced in regular intervals, the plunger driving part is advantageously provided with a drive unit coupling 42 for releasably coupling the plunger coupler to the drive unit. During operation, the drive unit ( not shown ) exerts a rotational force on the plunger coupler 4 via the drive unit coupling 42, and the plunger coupler transmits this rotational torque to the plunger 3. While the plunger driving rod remains stationary along the longitudinal axis, the plunger is linearly displaced along the axis.

Since the f rictional coupling between plunger and cylinder is larger than between cylinder and valve seat, the plunger is frictionally coupled to the cylinder member, as long as the cylinder has not yet rotated to a blocking position, corresponding to an operational valve state. In the blocking position of the valve, the now decoupled rotational movement of the plunger is translated into a linear movement of the plunger, by the spindle drive realized by the outer thread 33 of the plunger and the inner thread 23 of the cylinder.

In the embodiment shown in Figure 1 , the thread lash is minimized by an advantageous thread lash reduction arrangement. The inner thread of the cylinder is realized as a single thread segment 23 having a segment angle of 1 80° or less. A separate radial bias force element 5 is provided on the cylinder wall, on the side opposite to the inner thread segment 23. Said bias force element 5 is realized in the given embodiment with a radially biased flat surface element 56 pressing on the outer thread 33 of the shaft 32, thereby pressing the outer thread 33 on the opposite side of the shaft radially onto the thread segment 23. A defined bias force is generated by a spring element 52 or other suitable resilient element, which in the figure is shown only schematically.

The principle of the applied thread lash reduction arrangement is shown in more detail in Figures 2 (a ) and ( b), schematically depicting a longitudinal section through a portion of a plunger shaft 32 with outer trapezoid thread 33 , interacting with a trapezoid thread seg ment 23 on the cylinder wall 22. On the opposite side of the thread seg ment 23 , a radial bias force element 5 is arranged, exerting a radial bias force F _bias perpendicular to the cylinder axis 20. The radial bias force element 5 is here realized as a flat element 56, abutting the outer surface 33 1 of the spindle 32, 33 , and biased by a helical spring 52. The bias element exerts a radial force on the outer thread 33 surface and the shaft 32, without directly interacting with the thread 33. As a result, there is a radial force F _bias between thread 33 and thread segment 23 , resulting to which the two threads closely abut each other, without a thread lash. Thus with such an arrangement there will be no undefined plunger motion upon reversal of the rotation direction, or pressure differentials in the metering chamber.

The parameters of the thread as such, namely thread form, flank angle, and helical angle are mainly defined by the intended application, namely a self-locking spindle drive. With a thread having a flank angle a, and neglecting the comparably small helix angle of the thread, an axial force F _ax acting on the plunger shaft 32 will have a force component F _a = cos(a) F _ax parallel to the surface of the thread flank. Similarly there acts a force component F _b = sin (a) F _bias parallel to the flank surface, in the opposite direction. Thus as long as biasing force component F _b is larger than an axial force component F _a exerted on the plunger, or sin (a) F _bias > cos(a) F _ax , the axial force cannot overcome the bias force, and the outer thread flank cannot slide along the flank of the thread segment 23 , which would lead to a axial shift of the plunger.

In order not to increase thread friction unnecessarily, which would be detrimental for energy consumption of the drive unit, and thus for the battery life time of a corresponding infusion pump device, the biasing force has to be properly adjusted.

The maximum axial force F _{ax max} that may occur on the plunger during normal operation can be estimated. Based on that upper limit an appropriate minimum radial force of the bias force element is determined, as F _{bias min} = cot(a) F _ax . The smaller the flank angle the smaller is thread friction during operation, which is advantageous in regard to energy consumption. On the other hand it considerably increases the necessary bias force. An advantageous compromise in a dosing unit according to the disclosure is for example a trapezoid thread with flank angle 60° (cot 60° = 0.58) and helical angle 3.4°.

In the discussed embodiment, the bias force is generated by a spring element, for example a metal helical spring. Other types of resilient elements are possible. The material of the resilient element is chosen such that it does not deteriorate over time in regard to the spring force, thereby allowing a long shelf time prior first use.

The plunger shaft and the cylinder wall including thread segment 23 are advantageously manufactured from a thermoplastic polymer material compatible for medicinal applications. It should furthermore provide elasticity parameters suitable for application in self-locking spindle drives. Suitable materials are for example polyamide ( PA) , polypropylene ( PP), methyl methacrylate butadiene styrene terpolymer ( M BS), and polybutylene terephthalate ( PBT).

Another variant of a thread lash reducing arrangement is shown in Figure 3 (a ), where the bias force element 5 is realized as a biased thread segment 5 1 , interacting with the outer thread 33. A further embodiment is shown in Figure 3 ( b) , where three parallel thread segments 23 are provided. Such a variant with more than one thread flank interacting is less advantageous than the variants discussed before, since the actual forces acting on the thread can be determined less precisely due to manufacturing tolerances.

Another embodiment of an advantageous dosing unit is disclosed in Figure 4. The pump cylinder/valve member 2 comprises two parts 28, 26, and is rotatably arranged in the valve seat 1 2. The plunger plug 3 1 is arranged in a proximal ( proximal meaning "toward the valve") cavity part 28 of the cylinder, together defining the variable metering cavity. The plug 3 1 comprises a plug sealing element 3 1 1 , sealingly closing the metering cavity. The sealing element 3 1 1 is advantageously made from an elastic thermoplastic polymer. The plunger can be manufactured e.g. by two component injection moulding of plunger sealing element and plunger rod. In the longitudinal section given in Figure 4( b) , in which the valve seat 1 2 is shown, the radial opening 2 1 1 in the cylinder head wall 2 1 is f luidly connected to inlet 1 2 1 , while the outlet 1 22 is disconnected from the metering cavity.

The threaded 33 plunger shaft 32 is arranged in a distal (distal meaning "away from the valve, toward the drive unit") threaded sleeve part 26 of the cylinder, where the outer thread 33 interacts with two inner thread segments 23 of the threaded sleeve 26. The proximal cylinder part 22 and the distal part/threaded sleeve 26 of the cylinder are attached together with a suitable locking mechanism, for example by ultrasonic welding. Assembling the cylinder from two separate parts has the advantage that the single pieces are easier to manufacture. Furthermore it allows optimising of the materials used. The material of the proximal cylinder part 22 can be chosen in regard to compatibility with medical liquids and the interaction with the material of the plug sealing element 3 1 1 . The material of the distal threaded sleeve 26 can be chosen in regard to a reliable thread interaction with the plunger shaft 32.

The plunger shaft 32 is provided with a longitudinal bore 322 along its axis, in which a rod of a plunger driving part ( not shown ) can be arranged. Four longitudinal cams or rips 34 are arranged along the bore 322 of the plunger shaft, intended to interact with corresponding slots on the plunger driving rod. The cams 34 allow to efficiently transmitting a rotational torque from the plunger coupler to the plunger. At the same time there is only low friction along the longitudinal axis 20.

The necessary bias force to remove tread lash is provided by a radial bias force element 5 in the form of a half-ring-like metal spring 52 , having a flat portion 56 at one end of the spring 52, and a locking structure 53 on the other end. When mounted to the cylinder, the locking structure is arranged in a corresponding recession on the outer cylinder wall. The flat element 56 is arranged in an opening 22 1 in the threaded sleeve 26, and abuts the thread 33 of the plunger shaft 32.

During assembly the spring element 52 is slightly deformed. When the locking structure 53 and the flat portion 56 snap into the corresponding recessions and openings, the spring element is positively locked to the distal cylinder element, with a spring force due to the remaining radial deformation. Due to this remaining spring force the radial bias force element 5 generates a radial biasing force between the two inner thread segments 23 of the threaded sleeve 26 and the outer thread 33.

The embodiment shown in Figure 4 is particularly advantageous. Since the bias spring element 52 has a very simple structure and can be easily mounted to the cylinder, the dosing unit can be manufactured and assembled very efficiently. At the same time the spring element provides a reliable and constant radial bias force F _bias . The spring element 52 is advantageously made from spring band steel, for example spring band steel 1 .43 1 0. The use of two inner thread segments 23 in combination with a single biased flat surface element 56 is particularly advantageous, compared to a single threaded seg ment as described for Figure 1 . Since said two inner thread segments and the flat surface element provide a three-point mounting ( instead of two mounting points), the outer thread of the plunger shaft 32 is more stably mounted.

Another advantageous embodiment of a dosing unit is depicted in Figures 5 and 26, having another variant of a radial bias force element 5. Here the spring element 52 is a metal spring having the basic shape of an open ring, with two locking structures 53 at the two ends of the open ring, and a straight segment 56 in the middle. When mounted to the cylinder, the locking structures 53 are located in corresponding recessions. The straight segment 56 is located in an opening 22 1 of the cylinder wall, through which the flat portion 56 abuts the thread 33 of the plunger shaft 32. The two arms of the spring element 52 between the locking structures 53 and the central flat portion 56 remain slightly deformed when mounted to the cylinder, providing a constant radial bias force F _bias .

In the embodiments discussed so far, the plunger shaft 32 has been provided with a continuous outer thread, while the inner thread has been reduced to a single segment ( Figure 2 ) or two segments ( Figure 5 ). Such a configuration is advantageous in regard to reproducibility of thread lash reduction (see also discussion of Figures 2 and 3 ). Alternatively it is also be possible to provide the shaft 32 with a single outer thread segment 22 , and the inner surface of the cylinder with a continuous inner thread 23 , as for example shown in Figure 6. The distal end of the plunger shaft 32 is split into two shaft arms 32 1 , 32 1 ^' . On one shaft arm 32 1 a single outer thread segment 33 is arranged, interacting with the inner thread 23 of the cylinder. On the other shaft arm 32 1 ^' of the plunger shaft, a flat cylinder segment 56 is arranged, abutting the surface of the inner thread 23. A spring element 52 in the form of a single metal leaf spring is arranged between the two shaft arms 32 1 , 32 1 ^' , providing a radial force directed outwards. As a result the outer thread segment 23 is constantly biased against the inner thread 23 , thereby removing the thread lash. The two shaft arms 32 1 , 32 1 ^' of the plunger as such are not biased, since the corresponding force is provided by the spring element 52. Thus such an embodiment does not suffer from creep deformation as in the state of the art.

Another advantageous embodiment of a plunger with thread lash reduction is given in Figure 7. The outer thread 33 of the plunger shaft is divided into three rectangular portions 33a, 33a', 33a", equally distributed on the shaft 32. The threads are provided such that the outer thread is stably arranged and runs smoothly in a continuous inner thread of the cylinder. The thread portions are arranged in corresponding rectangular openings on the shaft, connected to the shaft only by a longitudinal hinge structure 323 , e.g. a film hinge or a longitudinal area with reduced wall thickness. The thread portions thus are pivotable along the axis of said hinges, about a small angle. The three outer thread portions are radially biased toward the inner thread, thereby efficiently removing thread lash.

The necessary bias force can be obtained by one or more suitable spring elements, e.g. a slotted metal ring spring ( not shown ) arranged in a circular groove in the bore 322 of the shaft. A suitable way to manufacture such a plunger is insert injection moulding, where the ring spring is over-moulded with the thermoplastic polymer material of the plunger shaft.

In an alternative embodiment the dimensions of the shaft are chosen such that the pivotably mounted thread portions are slightly compressed inwards when introduced into the inner thread. In that case the spring force is generated by the shaft/thread structure itself. However, a separate radial bias force element as discussed above is more advantageous, since there is no creep deformation of the shaft.

A similar approach is shown in Figure 8, where a plunger 3 having a shaft 32 with continuous outer thread 33 is arranged in a threaded sleeve 26 with four threaded claws 25, 25', 25", 25"', separated by slots 25 1 . In the given embodiment a slotted tension ring 27 is arranged as a radial bias force element 5 around the distal end of the claws 26, Said tension ring is dimensioned such that the claws are slightly biased inwards, toward the outer thread 33 of the plunger shaft, the inner and outer thread thereby engaging without thread lash.

Yet another advantageous embodiment of a thread lash reducing arrangement with radial bias force is shown in Figure 9. A sleeve element 263 is mounted to the distal end of the cylinder 2. A radial bias force is provided by radial bias force element 5 with three spring biased inner thread segments 59a. The radial bias force element is mounted to the distal end of the sleeve element 263 , and comprises a mounting sleeve 57 with three openings 58, and three spring elements 59. Together the sleeve element 263 and the radial bias force element 5 form a threaded sleeve 26, the inner thread seg ments acting as the inner thread 23 of the threaded sleeve. For assembling the threaded sleeve 26, the mounting sleeve 57 is put over the sleeve element 263 , such that three protrusions 262 lock into the openings 58, thereby positively locking the mounting sleeve 57 on the sleeve element 263. The three spring elements 59 are located in three longitudinal slots 261 of the sleeve element 263.

Sleeve element 263 and bias force element 5 are designed such that the thread segments 59a of the three spring elements 59 engage with the outer thread 33 of a plunger shaft 32 that is engaged with the threaded sleeve 26. The thread segments 59a thus act as short thread segments 23 of the threaded sleeve 26. In the assembled state, the thread seg ments 59a are radially biased, with a spring force F _bias acting radially inwards. The three spring elements are symmetrically arranged around the longitudinal axis. As a result the radial force components acting on the plunger shaft sum to zero.

The flanks of the thread segments 59a of the spring elements 59 of the radial bias force element 5 abut the flanks of the plunger shaft thread 33. Thread lash is removed, similar to Figure 2, as long as the relation F _{bias min} = cot(a) F _ax applies for the minimum radial bias force f _b i _as .min and the external axial force F _ax .

In an alternative embodiment, a similar radial bias force element 5 is mounted to the plunger shaft, its spring biased outer thread seg ments 59b acting as the outer thread 33 of the plunger shaft, engaging with the inner thread 23 of the cylinder without thread lash.

Yet another advantageous variant of a thread lash reduction arrangement is depicted in Figure 1 0. In contrast to the embodiment shown in Figure 3 (a ), where a radially biased inner thread segment provides the radial bias force, a short wire segment 55 is used as the radial bias force element 5.

The wire segment 55 is mounted on a threaded sleeve, parallel to the other threads 33 of the plunger. Two inner thread segments 23 are arranged on the sleeve 26 opposite to the wire 55. During operation the bias wire 55 is arranged in a groove of the outer thread 33. The wire is attached on its two ends to the sleeve in such a way that it is strained when the plunger shaft thread 33 is introduced into the threaded sleeve 26. The strained wire exerts a radial bias force on the plunger shaft, resulting in a radial bias force between outer thread 33 and thread segments 23. In the variant as shown in Figure 1 0(a ), the wire abuts the groove of the thread 33 , which is particularly advantageous, since a jamming of the wire between the two thread flanks is not possible.

In the embodiments discussed so far the bias force providing the thread lash free engagement of plunger thread and cylinder thread was directed radially. Inner thread and outer thread were subject to a force perpendicular to the longitudinal axis.

In an alternative approach to avoid thread lash, the bias force is directed axially, along the longitudinal axis 20, as for example in Figure 1 1 . A continuously threaded 33 plunger shaft 32 is arranged in a threaded sleeve 26 at the distal end of a cylinder. A separate threaded element 64 with an inner thread 65 is coaxially mounted behind the threaded sleeve 26, connected to the latter via a helical spring 62.

Together the threaded element 64 and the helical spring 62 act as a spring biased axial bias force element 6. The helical spring 62 , arranged coaxially to the plunger 32, provides an axial force F _bias , pushing the threaded element 64 away from the threaded sleeve 26 along the longitudinal axis 20. As a result, during normal operation the distal flanks of the threaded portion 65 of the threaded element 64 abut the proximal flanks of the plunger shaft thread 33 , and the proximal flanks of the static threaded sleeve 26 abut the distal flanks of the plunger shaft thread. Independently from any reversal of the rotation direction of the plunger, or any external axial force due to a pressure differential in the metering chamber, the plunger 3 will be positively locked in the cylinder thread, without thread lash. At the same time there is no unnecessary increase of thread friction, which would be disadvantageous in regard to energy consumption.

In yet another variant, the roles of the inner 23 and outer 33 threads are exchanged, as shown in Figure 1 1 (c). A threaded sleeve 26 comprises a continuous inner thread 23. A plunger shaft 32 is provided with an outer thread 33. A threaded element 64 ^' with an outer thread 66 is shiftably arranged on the plunger shaft 32. A spring element in the form of a helical spring 62 is coaxially arranged between the end of the outer thread portion 33 and the threaded element 64 ^' . Together the threaded element 64' and the helical spring 62 form a spring biased axial bias force element 6. The helical spring 62 provides an axial force F _bias , pushing the threaded sleeve 64 ^' away from the outer thread portion 33 along the longitudinal axis 20. As a result, during normal operation the proximal flanks of the outer thread portion 66 of the threaded element 64 ^' abut the distal flanks of the cylinder thread 23 , and the distal flanks of the outer thread 33 abut the proximal flanks of the cylinder thread 23. Independently from any reversal of the rotation direction of the plunger, or any external axial force, the plunger 3 will be positively locked in the cylinder thread 23 , without thread lash.

One particular advantage of these embodiments is the possibility to use continuous threads for both the inner thread and the outer thread, thereby providing a stable mounting of the plunger shaft in the cylinder.

In the dosing unit as known from prior art EP 2 1 63273 A 1 , the friction force between cylinder valve member and plunger, which is necessary for reliably switch ing the valve before the plunger is linearly displaced, is constant. As a result the corresponding rotational torque that is necessary for actuating the plunger is also constant.

To reduce energy consumption of the drive unit actuating the plunger, it is advantageous to reduce the friction force between cylinder valve element and plunger during linear plunger displacement, where the valve is in one of its operational states. One advantageous embodiment of a dosing unit that allows controlling the friction between cylinder valve member 2 and plunger 3 is shown in Figures 1 2, 1 3 , and 1 4. The valve seat of the dosing unit 1 is not shown for simplicity. The threads 33 , 23 are only schematically indicated. The plunger 3 is coaxially arranged in the cylinder valve member2, defining a metering cavity 1 1 . The plunger 3 comprises a plunger plug 3 1 and a plunger shaft 32. Said plunger shaft is longitudinally split into two shaft arms 32 1 , 32 1 ^' , pivotably connected to the plunger plug 3 1 by a hinge region 323. A coupler element 4, releasably coupled to a drive unit ( not shown ) of an infusion pump device, has a driving rod 41 , essentially comprising a distal part stem 41 2, to be connected to the drive unit, and a proximal part 41 1 that is arranged in a longitudinal bore 322 of the plunger shaft. The proximal part 41 1 comprises two cams 43 , 43 ^' , slidably arranged in the slot 37 that divides the shaft 32 into the two shaft arms 32 1 , 32 1 ^' . Rotational torque is primarily transferred from the driving rod 41 to the plunger shaft 32 via said cams 43 , 43 ^' . Two other cams 44, 44 ^' are arranged perpendicular to the first cams 43 , 43 ^' , each having a long cut-out 441 that leaves a proximal ramp 7 1 and a distal ramp 7 1 ^' .

Along each of the two shaft arms 32 1 , 32 1 ^' a longitudinal slot 38 is arranged, on the proximal side limited by the hinge region 323 of the shaft 32, and on the other side by a bridge structure 39 bearing an outer thread element 33a , 33a'. The two bridge structures 39 com- prise a proximal ramp 72 and a distal ramp 72 ^' . When assembled the bridge structures are arranged in the cut-out 441 of the coupling rid 41 , between the two ramps 7 1 , 7 1 ^' . During operation the linear orientation of the driving rod 41 in regard to the cylinder valve member 2 , as well as the rotational orientation of the driving rod 41 in regard to the plunger 3 , remain constant.

As will be shown, the elements of the plunger shaft 32 and the driving rod 41 engage in such an advantageous way that friction between plunger and cylinder valve element is increased to a high value when the plunger shaft and the driving rod are in certain positions to each other, thereby frictionally coupling cylinder and plunger. In the other positions friction is on a lower level. This functional principle is explained in more detail in Figure 1 2, and Table 1 .

Table 1

Plunger rotaValve State Metering cavity Frictional couFigure

tion direction pling between

Cylinder valve

member and

plunger

Pump direction Pump state Partially filled None 1 2 ( b)

Pump direction Pump state Empty Yes 1 2 (a )

Refill direction U ndefined, Empty Yes 1 2 (a )

valve rotates

until the other

stopper is reached.

Refill direction Refill state Partially filled None 1 2 ( b)

Refill direction Refill state Maximum caYes 1 2 (c)

pacity

Pump direction U ndefined, Maximum caYes 1 2 (a )

valve rotates pacity

until the other

stopper is reached.

Pump direction Pump state Partially filled None 1 2 ( b) Assuming that the valve of the dosing unit is in the pump state, the valve member abutting a corresponding stopper of the valve seat, and the outlet being connected to an infusion set, and that the metering cavity is partially filled (see the situation in Figure 1 2 ( b) ) , the drive unit will rotate the plunger such that it is linearly shifted to the left, thereby conveying liquid medicament toward the infusion set. The friction between plunger 3 and cylinder 2, namely thread friction and friction between plunger plug and cylinder wall, is chosen such that is as small as possible, in order to minimize energy consumption of the drive.

When the plunger reaches the cylinder head, and the metering cavity is completely emptied (see Figure 1 2 (a ) ), the proximal ramp 72 of the bridge structure 39 of the plunger shaft 32 , shifting to the left, engages with the proximal ramp 7 1 of the driving rod 41 and forces the bridge structure 39 radially outward toward the cylinder wall. As a result the thread segment 33a on the bridge structure is radially pressed onto the inner thread 23 , which increases thread friction until finally the outer thread is jammed in the inner thread.

To continue the administration of liquid medicament it will be necessary to retrieve new liquid medicament from the primary reservoir of the infusion pump. For that the valve has to be switched from the pump state to the refill state, wh ich requires a reversal of the rotation direction of the plunger and a frictional coupling between cylinder valve member and plunger. Since the inner and outer threads are jammed, friction between cylinder and plunger is considerably larger than friction between cylinder and valve seat. The rotating plunger grips and rotates the cylinder in the valve seat until it reaches the stopper that defines the valve's refill state, where the inlet conduit is connected to the primary reservoir. Since cylinder rotation is now mechanically blocked, the drive unit can overcome the thread jamming. The proximal ramp 72 of the bridge structure 39, now shifting to the right, disengages from the proxima l ramp 7 1 of the driving rod, until thread friction and thus energy consumption is minimal again.

During the following refill mode, the plunger is displaced to the right and the metering cavity is refilled (see Figure 1 2 ( b) ) , until finally maximum filling capacity is reached (see Figure 1 2 (c) ). When the plunger reaches this maximum position at the right, the distal ramp 72 ^' of the bridge structure 39 engages with the distal ramp 7 1 ^' of the driving rod, forcing the bridge structure and the outer thread segment radially outwards toward the inner thread 23 , until the thread is jammed. The valve has now to be switched back to the pump position , discon - necting the primary reservoir and connecting the infusion set. Since cylinder and plunger are again temporarily frictionally coupled, rotating the plunger in the reversed direction ( pump direction ) will rotate the cylinder in the valve seat until the stopper is reached that defines the pump state of the valve. Further rotation of the plunger disengages the ramps 7 1 ^' , 72 ^' and removes the thread jam, and the plunger can be moved again to the left at minimum friction.

As can be seen, an advantageous dosing unit as discussed above allows controlling the friction between plunger and cylinder valve member. The interaction between the ramps 72, 72 ^' of the bridge structures 39 and the ramps 7 1 , 7 1 ^' of the driving rod 41 provides the possibility of temporarily radially biasing the outer thread segments toward the inner thread 23 , thereby increasing thread friction. Thus a dosing unit optimizes energy consumption by restricting friction to a minimum level during pumping and refilling. Although this increase may go up to an actual temporary jamming of the thread, it is also possible just to increase friction to a value that is sufficient for the valve switching.

The example discussed above provides opportunities to switch the valve at two distinct positions, namely when the metering cavity is either completely empty or completely full. An advantageous variant that allows the switching of the valve also in intermediate positions is explained in Figure 1 5. In addition to the two ramps 7 1 , 7 1 ^' at the proximal and distal end of the driving rod 41 , two elevations 7 1 a arranged on the driving rod between the ramps provide two other positions where bridge structures 39 a nd thread segments 33a, 33a ^' are radially biased (see position I ). The height of the elevations is chosen such that although friction is increased, no jamming takes place. Thus the dosing unit may continue in the mode it currently is in, for example pumping. The only effect will be a temporary increase of energy consumption until the end of the elevation is reached, due to the temporary increase of thread friction. If on the other hand the valve should be switched at this intermediate position, the dosing unit may do so by reversing the plunger rotation and rotating the frictionally coupled cylinder in the valve seat until the stopper is reached, and frictional coupling is released. Between the elevations and/or ramps, the bridge structure is not biased (see position I I ). When the bridge structure reaches one of the outer ramps (see position I I I ), the friction can be increased up to thread jamming, although this is not actually necessary.

The dosing units discussed in Figures 1 2 to 1 5 may also be combined with thread lash reduction. For example may the two shaft arms of the plunger shaft be pre-biased , due to radial dimensions that are slightly larger than the dimensions of the inner thread, or a radial bias force element as shown for example in the embodiments in Figures 6 or 7 can be applied.

Another possible embodiment of a dosing unit 1 with controlled friction is shown in Figure 1 6, with the valve seat not shown for simplicity. The cylinder valve member comprises a cavity part 28 and a threaded sleeve part 26, mounted together. The threaded sleeve part 26 has an inner thread 23 , which may be some few windings, or even only a thread segment, particularly if one of the thread-lash reduction schemes is applied that have been discussed further above.

The plunger 3 with plunger plug 3 1 and plunger shaft 32 is coaxially arranged in the cylinder 2. The plunger shaft 32 comprises a continuous outer thread 33 , engaging with the inner thread 23 of the threaded sleeve 26. In the figure the threads are only schematically indicated for simplicity. The plunger shaft comprises a longitudinal bore 322, in which a driving rod 41 of a plunger driving part 4 is shiftably arranged.

The plunger and the cylinder are realized in such a way that friction is minimal during the pump mode and refill mode, in order to restrict energy consumption by the drive unit ( not shown ). In order to temporarily increase friction and thereby enabling the valve switching functionality by the drive unit, two friction cylinders 74, 74 ^' are arranged on the proximal and the distal end of the plunger shaft 32. Said two friction cylinders are intended to frictionally engage with two corresponding hollow friction cylinders 74a, 74a ^' that are arranged on the proximal and the distal side of the inner thread 23 of the threaded sleeve 26. When the plunger is in the position where the metering cavity 1 1 is completely empty ( Figure 1 6(a ) ) or completely filled ( Figure 1 6( b) ) , the abutting cylinder surfaces of the engaging friction cylinders cause increased friction. This provides the necessary additional friction between plunger and cylinder to reliably actuating the valve and rotating the cylinder valve member in the valve seat upon reversal of the plunger rotation direction. This can be seen in more detail in Figure 1 6(c). When the spindle drive rotates the plunger toward the maximum distal position, the friction cylinder 74 continuously shifts to the right into the cavity of the hollow friction cylinder 74a, thereby linearly increasing friction. The dimensions of the interacting elements and the materials used are chosen such that latest when the plunger is in the maximum filling position , the friction between cylinder valve member and plunger, namely between the friction between the engaging friction cylinders and the constant friction due to the thread and the plunger plug, are sufficiently large to actuate the cylinder valve member in the valve seat when the plunger rotation direction is reversed. When the plunger rotation direction is reversed, the plunger grips the cylinder and rotates it in the valve seat, until the cylinder abuts the stopper of the valve set. The static friction force is overcome, and the plunger starts again to rotate a nd to displace in the cylinder. The overlapping area of the friction cylinders, and thus the additional friction force, decreases linearly to zero.

As in the example discussed before, the friction between cylinder and plunger is mechanically controlled, depending on the relative position of the plunger in the cylinder. However, the element controlling the additional friction (the hollow friction cylinders 74a, 74a ^' ) are in this case located on the cylinder, while in Figure 1 2 the cams as the controlling element are located on the driving rod. In both cases the relative position of the linearly static elements (cylinder and driving rod ) in regard to the displaceable element (the plunger) is the parameter used to control the amount of friction between plu nger and cylinder.

Another advantageous variant of a dosing unit 1 , using a similar principle for controlling the friction, is described in Figure 1 7. Again the valve seat is not shown for simplicity. Two stopper disks 73 , 73 ^' are mounted on the plunger shaft 32, on a proximal and a distal end of the continuous outer thread 33. The threaded sleeve 26 comprising the inner thread 23 is also realized as a stopper disk 73a.

The additional friction that is necessary for switching the valve in the end positions of the plunger is generated when one of the two stopper disks, e.g. the proximal stopper disk 73 as shown in Figures 1 7 (a ) and (c), abuts the stopper disk 73a mounted to the cylinder. Since the plunger is actually mechanically blocked from a further linear displacement, the thread friction force exponentially increases with any further rotation, immediately jamming the plunger thread 33 in the cylinder thread 23 and frictionally coupling the plunger and the cylinder. When now the plunger rotation direction is reversed, the static friction between cylinder and plunger is large enough to actuate and rotate the cylinder in the valve seat ( not shown ) of the dosing unit. When the cylinder abuts the stopper of the valve seat, the thread jamming is removed and f rictional coupling is released. Thread friction is back to a minimum level. A dosing unit embodiment as discussed in the example above is very robust and reliable.

A further variant of such a dosing unit is shown in Figure 1 8, having two stopper disks 73a, 73a ^' mounted in the cylinder 2, while one stopper disk 73 is mounted on the plunger shaft 32 on a distal end of the continuous outer thread 33 , and located between the two other stopper disks 73a, 73a ^' . The inner thread 23 of the cylinder is arranged on the proximal stopper disk 73a. Similar to the example above, the spindle thread 23 , 33 jams when the central stopper disk 73 reaches one of the peripheral stopper disks 73a, 73a ^' . The resulting frictional coupling between plunger and cylinder then allows rotating the cylinder and switching the valve when the rotation direction is reversed.

The inner thread 23 of the cylinder may also be arranged on the distal stopper disk 73a ^' , when the outer thread 33 is arranged on the other side of the central stopper disk 73. In such a case, however, the necessary length of the plunger shaft and the driving rod, and thus the overall length of the dosing unit, is increased.

Such a dosing unit can be further modified by arranging an outer thread 33 , 33 ^' on both sides of the central stopper disk, each engaging with an inner thread 23 , 23 ^' on a stopper disk 73a, 73a ^' , as disclosed in Figure 1 9. The linear and angular orientation of the engaging threads is advantageously realized in such a way that the two thread sets longitudinally bias each other, thereby effectively removing thread lash.

Instead of achieving the temporary locking of cylinder and plunger via jamming the spindle threads, as discussed above, it is also possible to positively lock the plunger and the cylinder at certain longitudinal positions, as for example shown in the dosing unit in Figure 20. The cylinder 2 of the depicted embodiment comprises a cylinder part 28 and a threaded sleeve 26. The valve seat of the dosing unit, in which the cylinder valve member 2 is rotatably arranged, is not shown.

The threaded sleeve comprises a cylinder coupling part 75 in the form of a circumferential ring with a multitude of locking holes 75 1 . Attached to a distal end of the plunger shaft 32, a plunger coupling part 76 is provided, having locking elements 761 , 761 ^' in the form of spring biased balls, arranged on both sides of the cylinder locking element 75. The plunger locking element 76 can be realized as a cylinder-like element, having a multitude of circumferentially distributed locking elements 761 , 76 1 ^' , or as two or more arms bearing the locking elements.

During pumping and refilling the position of the cylinder coupling part with the multitude of locking holes 75 1 remains in a fixed position, since the cylinder remains in a fixed position. The plunger coupling part 76 rotates and linearly shifts together with the plunger 3 , to which it is attached. When the plunger 3 arrives at one of its two terminal positions, the spring- biased balls of one end of the plunger locking structure start to slide and roll over the ring 75 surface, with minimum friction. However, when they finally arrive at their corresponding locking holes 75 1 , the balls 761 , 761 ^' snap into the holes and positively lock the cylinder to the plunger. When now the plunger rotation direction is reversed, the plunger 3 actuates and rotates the cylinder valve member 2 in the valve seat, until the cylinder abuts the stopper of the valve seat. The valve has switched. Due to continuing rotation, the ball overcomes the spring force and slides under the ring 65, and the temporary locking of cylinder and plunger is released.

Figure 2 1 discloses another advantageous variant of a dosing unit 1 , in which a cylinder coupling part in the form of a cylindrical sleeve 75 is coaxially arranged on the cylinder part 28 and attached to the threaded sleeve 26. Alternatively said cylinder coupling part may also be realized as an integral part of the cylinder 28, or as a separate part. A plunger locking structure 76 that is attached to a distal end of the plunger shaft 32 comprises cams 762 that are pivotably mounted on the locking structure 76, by pivot arms 763. Two sets of depressions 75 1 , 75 1 ^' are located on a proximal and a distal end of the cylinder coupling part 75. The two coupling parts 75, 76 are realized in such a way that the cams 762 slide on the surface of the cylinder coupling part 75 when the cams are located between the two depressions 75 1 , 75 1 ^' , and snap into the depressions when the plunger arrives at a terminal position , corresponding to an empty metering cavity 1 1 ( Figure 2 1 (a ) ) or a completely filled metering cavity ( Figure 2 1 ( b) ). The cams are radially biased inwards, since the pivot arms 763 are deformed outwards when the cams slide on the surface during operation.

The depressions 75 1 , 75 1 ^' are formed such that a perpendicular wall on the outer side (toward the end of the dosing unit) provides a clearly defined stopping position for the cam 762, thereby mechanically blocking the further linear displacement of the cam and the attached plunger, which as a results leads to a thread jam. Plunger and cylinder are now coupled by static friction. U pon reversal of the plunger rotation direction, the plunger rotates the cylinder and switches the valve. When the valve has been switched and the further rotation of the cylinder valve member is blocked by a stopper of the valve seat, the thread jam is released, and plunger and cylinder are decoupled. A ramp on the opposite side of the stopper wall of the depression forces the pivotably mounted cam outwards, until it slides on the surface again. The plunger can now move to the other terminal position, with minimal friction. Yet another advantageous embodiment of a dosing unit is given in Figure 22, where the pivo- tably mounted cam is replaced by a spring-biased ball as the locking element 761 , mounted on the plunger locking structure 76. A number of locking holes 75 1 are distributed on the cylinder coupling part 75 in the form of a sleeve attached to the threaded part 26 of the cylinder.

During normal operation, in the pump mode or the refill mode, the plunger is linearly displaced along the axis, at the same time rotating about the axis. The spring-biased ball rolls and slides on the surface of the sleeve 75, providing minimum friction. At certain positions, the spring ball 761 snaps into a locking hole 751 , positively locking plunger and cylinder. However, since the valve is in a switched state, the cylinder being mechanically blocked from further rotation, the ball is immed iately forced out of the hole upon further rotation of the plunger, and rolls and slides on the surface of the sleeve 75, providing minimum friction.

If on the other hand in such a position the rotation direction is reversed, the positive locking of cylinder and plunger is strong enough to rotate the cylinder valve member in the valve seat, until the other stopper is reached and further cylinder rotation is mechanically blocked. Again the ball is forced out of the hole upon further rotation of the plunger, and rolls and slides on the surface of the sleeve.

A particular advantage of such a design is the possibility to define intermediate positions on which the friction between plunger and cylinder is increased, and the valve can be switched. At these positions of positive locking , the drive unit may or may not reverse the plunger rotation direction and thereby switching the valve.

In the embodiments of dosing units discussed so far the friction between plunger and cylinder valve member is controlled based on the linear position of the plunger. Thus valve switching is enabled at certain relative linear positions of the plunger within the cylinder.

In contrast to these previous examples, the advantageous dosing unit embodiments that will be discussed in the following achieves cylinder valve member actuation by temporary f rictional coupling between the cylinder and the driving rod, upon each reversal of the rotation direction of the driving rod. The coupling friction is not controlled by the position of the plunger in the cylinder, but by the change of the driving rod rotation direction and the relative angular orien- tation of cylinder and static valve seat. This particularly advantageous variant allows switching the valve at any longitudinal position of the plunger.

An example of such an embodiment is given by the dosing unit schematically disclosed in Figure 23. As can be seen in the schematic cross-section, a cylindrically shaped driving rod coupling part 77 is arranged coaxially to a cylindrically shaped cylinder coupling part 79. The driving rod coupling part 77 is attached to the driving rod ( not shown ) of the dosing unit, while the cylinder coupling part 79 is attached to the cylinder of the dosing unit ( not shown ). Thus during operation of the dosing unit, the two coupling parts 79, 77 rotate in regard to each other, while at the same time being fixed in regard to each other in the longitudinal direction.

The coupling parts 79, 77 are coupled to each other by three friction elements 770 attached to the driving rod coupling part 77, symmetrically distributed along its circumference. The friction elements 770 have an O-like cross-section and are made from a flexible, elastic material. The materials of the friction elements 770 and the cylinder coupling elements 79 are advantageously chosen such that they provide a large static friction force.

The functional principle of the disclosed embodiment is that during normal operation of the dosing unit, where the plunger is either advanced or retreated within the cylinder, the inner driving rod coupling part 77 (attached to the rotating driving rod ) rotates counter-clockwise in regard to the cylinder coupling part 79 (attached to the cylinder valve member), as shown in Figure 23 (a ) and ( b). The cylinder valve member is mechanically blocked from counterclockwise rotation in the static valve seat, which is schematically shown by a cam 29 of the cylinder abutting a stopper 1 23 of the valve seat. The elastic friction elements 770 are deformed and are dragged along by the inner coupling part 77, sliding on the inner surface 792 of the outer cylinder coupling part 79, which results in a minimum sliding friction force.

For switching the valve, the rotation direction of the driving rod is reversed to clockwise. The deformed friction elements 770 are now oriented opposite in regard to the rotation d irection ( Figure 23 (c) ). The cylinder coupling part 79 is not mechanically blocked from clockwise rota tion. The rotating driving rod coupling part 77 presses the friction elements into the surface 792 of the coupling part 79 and jams them in regard to the coupling part 79. The resulting static friction force between surface 792 and frictions elements 770 allows the inner coupling part 77 gripping the outer coupling part 79 and rotating it clockwise in the valve seat, until the cam 29 reaches the other stopper 1 23 ^' of the valve seat, and is mechanically blocked again. Since the cylinder coupling part cannot rotate any longer, the still frictionally coupled friction elements 770 of the inner coupling part 77 are deformed, and flip via an intermediate state ( Figure 23 (d ) ) to an opposite conformation ( Figure 23 (e) ). In this conformation the friction elements again slide over the surface 792, with minimum sliding friction.

To achieve high static friction, the materials of the friction elements 770 and the surface 792 are chosen accordingly. For example may at least one of said two elements be made or covered by a rubber-like material. Furthermore the elastic friction element is realized such that the force necessary to deform and flip the friction element is larger than the force due to the torque between the inner and outer coupling parts 77, 79. To adjust the friction forces in the given setup, the different elements may be further modified. For example may the outer cylinder 79 be provided with a roughened or teethed surface. The friction elements can also be arranged on the cylinder coupling part 79 instead of the driving rod coupling part 77, or on both parts.

A further variant of a dosing unit with dynamic friction control is disclosed in Figure 24. Shown is the plunger driving part 4 of the dosing unit, having a driving rod 41 with four longitudinal cams 43. On a distal end of the driving rod, opposite to the end that is to be located in the longitudinal bore of a plunger shaft ( not shown ) of the dosing unit, a driving rod coupling part 77 is arranged, having the form of a disk. On the circumference of said disk 77, three mounting arms 776 are provided, for attaching the plunger driving part 4 to a cylinder in such a way that it is remains freely rotatable along the longitudinal axis 20. The mounting arms 776 are provided with two distance rips 775 and a cam 774.

During assembly the driving rod 41 is inserted into the plunger shaft bore. Forced by the ramp of the cam 774, the three mounting arms 776 are forced outwards, until a distal rim 222 of the cylinder wall snaps into the gap provided between the cam 774 and the two distance rips 775. The dimensions of the gap are chosen such that the rim and thus also the cylinder 2 is positively locked in regard to the plunger driving part 4 with minimum play, but can be rotated around axis 20 with minimum friction. The distal surface 792 of the cylinder rim also acts as the cylinder coupling part 79.

On the surface of disk 77 facing the cylinder, three friction elements 770 are arranged, comprising a pivoting arm 77 1 that is connected to the driving rod coupling part 77 by a hinge 772, and that has a tip 775 facing the cylinder. The length of the friction element 770 is cho- sen such that in the assembled state, during normal operation of the dosing unit, the arm 77 1 is tilted to one side away from the direction of rotation, as shown in Figure 24(d ). The disk 77 rotates together with the driving rod 41 , symbolized by the arrow to the left. The cylinder 79 is mechanically blocked in the valve seat, symbolized by the crossed-out arrow to the left. During rotation of the driving rod, the tip 775 of the friction element 770 is dragged along and slides on the distal surface 792 of the cylinder coupling part 79 with minimum friction.

In order to turn the cylinder valve member 2 in the valve seat and to switch the valve, the rotation direction of the driving rod 41 is reversed. In this direction the cylinder 2 is not mechanically blocked in the valve seat. The friction element is now tilted toward the direction of rotation (arrow to the right). U pon rotation of the driving rod 41 , the tip 775 of the friction element is pressed into the surface 792 of the cylinder coupling part 79, jamming the frictiona l element 770 ( high static friction, gripping the cylinder and pushing it in the same rotation direction ( Figure 24(e) ).

When the cylinder has rotated in the static valve seat for a certain rotation angle to the second stopper that corresponds to the other valve state, further rotation of the cylinder is mechan ically blocked. Forced by the continuingly rotating driving rod 41 and disk 77, the hinge region 772 of the friction element 77 is compressed ( Figure 24(f) ), allowing the pivoting arm to flip to the other side ( Figure 24(g ) ). The friction element 770 is now again dragged along by the driving rod coupling part, with minimum sliding friction.

Also in this embodiment of a dosing unit, the friction elements can be arranged on the cylinder coupling part 79 instead on the driving rod coupling part 77, or on both parts. To increase friction, the interacting elements 770, 792 may be modified. For example can the surface 792 be provided with teeth that allow a stronger grip of the tip 773 of the friction element 770, or the surface 792 can be provided with an adhesive or compressible coating. The use of teeth makes the coupling parts unsusceptible to contamination of the surfaces by oil or similar substances. At the same time the teeth define discrete steps of the rotation angle.

In the embodiments shown in Figures 23 and 24, the driving rod, and not the plunger, actuates the cylinder valve member in the valve seat. To avoid that the plunger already gets linearly displaced during the valve switching process, the coupling between plunger shaft and driving rod is advantageously temporarily released during valve switching. This is achieved by realizing the longitudinal bore 322 and the driving rod 41 with a certain predefined play. A further advantage of such an embodiment is the reduction of friction between driving rod and plunger shaft during linear displacement.

Figure 25 depicts in a cross-sectional view different variants of interacting plunger shafts 32 and driving rods 41 . In Figure 25 (a ), the longitudinal bore of the plunger shaft 32 has essentially the shape of the driving rod 41 , the four longitudinal cams 43 of the driving rod being slidably arranged in corresponding slots of the longitudinal bore. Such an embodiment provides essentially no rotational play between driving rod and plunger shaft, and is advantageously used for dosing units as for example shown in Figures 1 4 to 22.

In Figure 25 ( b), the longitudinal bore of the plunger shaft 32 provides rotational play. The slots between the cams 34 of the plunger shaft are designed such that upon reversal of the rotation direction of the driving rod, in the given Figure from clockwise to counter-clockwise, for a certain predefined rotation play angle a, the cams 43 do not rotationally engage with the cams 34 of the plunger rod, until the cams 43 have reached the cams 34 on the other side of the slot ( Figure 25 (c) ). The angle a is chosen such that the friction elements 770 of Figures 23 or 24 can completely switch before the driving rod 41 and the plunger shaft 32 rotation- ally engage again. This ensures that in a dosing unit as for example shown in Figures 23 and 24, the friction element does not remain for a longer time in an intermed iate state ( Figures 23 (d ), 24(f) ), which could lead to irreversible deformation.

In an even more advantageous embodiment, as shown in Figure 25 (d ), the predefined rotation angle β is chosen larger than the angle that is necessary for switching the valve. This ensures that it is geometrically impossible to resume plunger displacement before the valve has been switched.

A particularly advantageous embodiment of a dosing unit 1 is disclosed in Figure 26. The cylinder 2 and the plunger ( not visible) are identical to the embodiment shown in Figure 5. Visible is the threaded sleeve part 26 of the cylinder 2, with the radial bias force element 5 mounted to the threaded sleeve part. A plunger driving part 4 similar to the one shown in Figure 5 is attached to the distal end of the threaded sleeve part 26 with three mounting arms 776. The driving rod coupling part 77, to which the driving rod ( not visible) and the friction elements 77 are mounted, provides additional functionality. The friction elements 770/pivoting arms 77 1 are attached to the driving rod coupling part 77 by hinge structures 772, which are mounted to spring element structures 777. Said spring element structures 777 provide certain elasticity and flexibility n the longitudinal and radial direction.

The distal end of the coupling part 77, opposite to the driving rod and facing toward the driving unit ( not shown ), is realized as a concave, self-centering drive unit coupling 42, with three protruding cams 42 1 that are intended to engage with corresponding elements of the drive unit.

In Figure 26 the friction elements 770 are shown in the intermediate state, as shown in Figure 24(f). Figure 27 shows the different steps during valve switching. Only the most distal end of the cylinder 2 is shown. The depicted different steps are as follows:

I: The valve is in a first valve state. The driving rod coupling part 77 with the piston rod ( not visible) is in the counter-clockwise freewheel mode, and the friction elements 770 are dragged along the surface 792of the rim 222. The plunger ( not shown ) is linearly displaced, driven by the rotating driving rod.

I I: The plunger ( not visible) has reached a stop position (completely empty or completely full), or the control system of the dosing unit decides to switch the valve for another reason.

I l l: The valve switching process begins. The rotation direction is reversed from counterclockwise to clockwise. The friction elements jam with the surface of the rim of the cylinder , and actuate the cylinder clockwise in the valve seat.

IV : The cylinder valve member, rotating in the valve seat ( not shown ) reaches the stopper ( not shown ) that defines the second valve position. The valve has been switched to its second state.

V: The cylinder valve member is blocked from further rotation.

VI: U pon further rotation of the driving rod, the friction elements flips over, and the jamming between driving rod and cylinder valve member is released. VI I: The valve is in the second valve state. The driving rod coupling part with the piston rod ( not visible) is in the clockwise freewheel mode. The friction elements are dragged along the surface of the rim. The plunger ( not shown ) is linearly displaced upon rotation of the driving rod.

VI I I: The plunger ( not visible) has reached the other stop position (completely full or completely empty), or the control system of the dosing unit decides to switch the valve for another reason.

IX: The valve switching process begins. The rotation direction is reversed from clockwise to counter-clockwise. The friction elements jam with the surface of the rim of the cylinder, and actuate the cylinder clockwise in the valve seat.

X: The cylinder valve member, rotating in the valve seat ( not shown ) reaches the stopper ( not shown ) that defines the first valve position. The valve has been switched to its first state.

XI: The cylinder valve member is blocked from further rotation.

XI I: U pon further rotation of the driving rod, the friction elements flips over, and the jamming between driving rod and cylinder valve member is released.

XI I I: The valve is in the first valve state again. The driving rod coupling part with the piston rod ( not visible) is in the counter-clockwise freewheel mode. The friction elements are dragged along the surface of the rim. The plunger ( not shown ) is linearly displaced upon rotation of the driving rod. Step XI I I is essentially identical to step I , except for the angular orientation of the driving rod.

Yet another approach to realize a dosing unit is schematically depicted in Figure 28, where a controlled coupling between cylinder 2 and driving rod 41 is realized with a bistable ratchet mechanism 78. All figures are shown with the cylinder valve member remaining static, and the driving rod 41 and valve seat moving in relation to the cylinder valve member.

A cog wheel 781 is mounted on the driving rod 41 at a distal end. A double pawl element 785 with two opposite pawls 787, 787 ^' is pivotably mounted on an axis bearing 784, which itself is mounted on the cylinder valve member 2. The double pawl element 785 is provided with an arm 788. A tension spring 786 is arranged between a first suspension point at the end of the arm and a second suspension point 783. To provide symmetrical operational conditions, said second suspension point 783 has to be located somewhere on a straight line through the driving rod's rotation axis and the pivotal axis 784 of the double pawl element 785. In Figure 28(a ) the driving rod 41 is in the counter-clockwise freewheel mode (symbolized by an arrow). The plunger can be linearly displaced in the corresponding direction. The bistable ratchet mechanism is in one of its stable states, driven by the spring force of the tension spring 786. The teeth 782 of the cog wheel 781 , rotating counter-clockwise together with the driving rod, can pass the pawl 787 ^' without switching the ratchet mechanism. For switching the valve, the rotation direction of the driving rod 41 is reversed, in the given case from counter-clockwise to clockwise ( Figure 28( b). The tooth right of the pawl 787' abuts the pawl, and the ratchet is jammed. The driving rod 41 and the cylinder valve member 2 are now rotationally coupled via the pawl 787 and the bearing axis 784, and the rotating driving rod rotates the cylinder valve member clockwise (dashed arrow). The rotation of the cylinder is stopped when a first switching element 1 24 mounted to the valve seat (dotted arrow) reaches the bistable ratchet mechanism, as shown Figure 28(c). The switching element 1 24 pushes the first pawl 787 toward the cogwheel. The double pawl element 785 pivots around the axis bearing 784, the tension spring 786 is expanded, and when the arm 788 passes the line defined by suspension point 783 and axis bearing 784, the bista- ble ratchet switches to the other state. The cylinder valve member 2 is now rotationally decoupled from the driving rod 41 . The driving rod 41 is in the clockwise freewheel mode again. The teeth of the cogwheel can pass the ratchet mechanism without engaging, and the plunger is linearly displaced in the opposite direction.

To switch the valve back to the first state, the process is repeated ( Figure 28(d ) ), by reversing the rotation direction from clockwise to counter-clockwise. The ratchet and the cogwheel jam, rotationally coupling the cylinder valve member a nd the driving rod. The driving rod rotates the cylinder valve member counter-clockwise, until the second switching element 1 24 ^' mounted to the valve seat reaches the ratchet mechanism, and flips over the double pawl element to its first state, as shown in Figure 28(a ), thereby decoupling again the cylinder valve member and the driving rod. The angular position of the switching elements 1 24, 1 24 ^' is chosen such that the ratchet switching positions correspond to the two valve positions. Thus no additional stopper elements are necessary, delimiting the rotation of the cylinder valve member in the valve seat. Advantageously they are nevertheless provided, to define clear valve end positions.

Instead of using a separate cogwheel the driving rod itself may be used as the cogwheel, with its cams 43 acting as the teeth, if a sufficient number of cams 43 are provided to realize the ratchet mechanism.

Yet another advantageous embodiment of a controllable coupling between driving rod 41 and cylinder valve member 2 is disclosed in Figure 29. A driving rod 41 is arranged within the cylinder 2, operationally engaging with the plunger shaft ( not visible). Only the distal end 41 2 of the driving rod is visible in Figure 29 (a ). The driving rod is provided with a driving rod coupling part 77, in the form of a hollow cylinder 778. The distal end of the cylinder is provided with a cylinder coupling part 79, intended to be arranged in the hollow cylinder 778. The cylinder coupling part 79 comprises two clamp arms 793 , 793 ^' that are pivotably connected to the cylinder 2 via hinges 794, 794 ^' . One clamp arm 793 has one clamp finger 795, having a radial protrusion on the outside toward the inner side of the hollow cylinder 778. The other clamp arm 794 ^' has two clamp fingers 795 ^' with a radial protrusion. Alternatively both clamp arms may be provided with an equal number of clamp fingers.

The dimensions of the two coupling parts 79, 77 are chosen such that in the assembled state of the dosing unit the clamp fingers 795, 795 ^' are radially biased against the inner surface of the hollow cylinder 778. As a result the driving rod 41 and the cylinder valve member 2 are f rictionally coupled, the rotating driving rod being able to actuate the cylinder valve member.

To minimize friction during the linear displacement of the plunger within the cylinder, the cylinder coupling part 79 is provided with means 796, 796 ^' to rotationally decouple the two coupling parts 79, 77. Each of the two clamp arms is provided with a release element arranged 796, 796 ^' outside of the hollow cylinder 778. Two switching elements ( not visible) mounted on the valve seat are arranged on such angular positions that in each of the two valve states, one of the switching elements engages with one of the decoupling elements 796, 796 ^' . The resulting force presses the corresponding clamp arm 793 , 793 ^' inwards, thereby decoupling the two coupling parts 79 , 77, and thus the driving rod 41 and the cylinder valve member 2. U pon further rotation of the driving rod in the same direction, friction is minimal, and the cylinder valve member remains on place.

To switch the valve, the rotation direction of the driving rod is reversed. The switching element disengages the release element, and the clamp arms engage again with the hollow cylinder. The frictionally coupled cylinder valve member rotates together with the driving rod, until the second switching element reaches the second release element, and coupling element and driving rod are decoupled again.

Instead of coupling arms engaging with a hollow cylinder, another embodiment of such a controllable coupling can be realised with a coiled spring, connected to the cylinder. The coil spring is looped around a cylindrical portion of the driving rod, and frictionally couples the cylinder and the driving rod. Switching elements of the valve seat can engage with the ends of the coil spring , increasing the radius of the coil spring and temporarily decoupling cylinder and driving rod.

The present invention is not to be limited in scope by the specific embodiments described herein. Indeed , various modifications of the present invention, in addition to those described herein, will be apparent to those skilled in the art from the foregoing description and accompanying drawings. Thus, such modifications are intended to fall within the scope of the appended claims. Additionally, various references are cited throughout the specification, the disclosures of which are each incorporated herein by reference in their entirety.

List of Reference Numerals

1 dosing unit

1 1 metering cavity

1 2 valve seat

1 2 1 inlet

1 22 outlet

1 23 , 1 23 ^' stopper elements

1 24, 1 24 ^' switching element

2 pump cylinder / cylinder valve member

20 cylinder axis

2 1 cylinder head

2 1 1 opening 2 guide ring

cylinder wall

1 opening in the cylinder wall

2 rim

, 23 ^' threaded portion of the cylinder, cylinder thread, 25', 25 ^" , 25 ^'" threaded claw

1 slot

threaded sleeve part

1 slot

2 protrusion

3 sleeve element

tension ring

1 slot

cavity part

cam

plunger

plunger plug

1 plug sealing element

2 plug protrusion

plunger shaft

1 , 32 1 ^' shaft arm, split portion of plunger shaft3 hinge

2 longitudinal bore

, 33 ^' threaded portion of the plunger, plunger threada, 33a', 33a" portions of the thread

1 lateral surface of the thread

cam

plunger coupling element

slot

slot

bridge structure

plunger driving part

plunger driving rod

1 proximal part 41 2 distal part

42 drive unit coupling

42 1 cam

43 , 43 ^' cam

44, 44 ^' cam

441 cut-out

5 radial bias force element

5 1 threaded element

52 spring element

53 locking structure

55 wire

56 flat surface element

57 mounting sleeve

58 opening

59 spring element

59a inner thread segment

59b outer thread segment

6 axial bias force element

62 spring element

64, 64 ^' threaded element

65 inner thread portion of threaded element

66 outer thread portion of threaded element

7 friction control element

7 1 , 7 1 ^' ramp

7 1 a elevation

72, 72 ^' ramp

73 , 73 ^' stopper disk

73a, 73a ^' stopper disk

74, 74 ^' friction cylinder

74a, 74a ^' friction cylinder

75 cylinder coupling part

75 1 locking hole

76 plunger coupling part

761 , 761 ^' spring-biased ball, locking element 762 cam, locking element

763 pivot arm

77 driving rod coupling part

770 friction element

77 1 pivoting arm

772 hinge

773 tip

774 snap lock cam

775 distance rip

776 mounting arm

777 spring element

778 hollow cylinder

78 bistable ratchet mechanism

781 cog wheel

782 tooth

783 suspension point

784 axis bearing

785 double pawl element

787, 787 ^' pawl

786 tension spring

788 arm

79 cylinder coupling part

792 surface

793 , 793 ^' clamp arm

794, 794 ^' hinge

795, 795 ^' clamp finger

796, 796 ^' release element

F oias bias force

^ ^~ bias,ax axial component of the bias force

Fax axial force acting on the plunger