DEVICE FOR APPLYING A FLUID

Description

[0001] The present invention relates to a device for applying a fluid having the features of the preamble of claim 1, which can be designed, for example, as a needle-free self-filling syringe with which a liquid medication, a liquid drug, a liquid vaccine or the like can be administered intramuscularly to animals.

[0002] Such a device for applying a fluid (known, for example, from US 3 057 349 A or WO 2018 / 107220 A1) should, on the one hand, be as light as possible and thus be portable for a long time with one hand by a user and, at the same time, enable the desired needle-free intramuscular injection.

[0003] The object of the invention is therefore to provide such a device for applying a fluid.

[0004] The invention is defined in claim 1. Advantageous embodiments are specified in the dependent claims.

[0005] The device according to the invention for applying a fluid comprises a cylinder having an open discharge end, a piston which is displaceable in the cylinder between a front and rear end position, which is connected to a piston rod which projects along a first direction beyond a rear end of the cylinder opposite the open discharge end, a check valve which closes the open discharge end (acting as an outlet valve), and a tensioning device connected to the piston rod. The tensioning device can move the piston rod in a tensioning process along the first direction until the piston is in its rear end position, in order to fill the cylinder with the fluid to be applied and to pre-tension the piston rod towards the open discharge end. For this purpose, the device can have a connection which opens into the cylinder. The connection can be connected, for example, toA hose or container containing the fluid to be applied can be attached and secured for use with the device. Preferably, the connection can have a check valve designed as an inlet valve that opens during the clamping process and closes when the fluid is applied. Accordingly, the outlet valve closes during the clamping process and opens when the fluid is applied.

[0006] Furthermore, when the piston is in its rear end position, the clamping device can release the piston rod in a dispensing process, so that the piston moves counter to the first direction towards the open dispensing end due to the applied preload, and fluid in the cylinder is dispensed via the check valve for application.

[0007] The clamping device can have a ramp that is rotatable by means of a motor and has a ramp path extending along a helical line, wherein the ramp path rises from a first plateau along an incline region to a second plateau and falls from the second plateau via a step flank to the first plateau, wherein the ramp path has a transition region connecting the second plateau and the step flank. The clamping device can further have a roller that contacts the ramp path and is rotatably mounted in a driver that is connected to the piston rod, so that when the ramp rotates along a first direction of rotation, the ramp path passes beneath the roller that is thereby rotating. For the clamping process, the ramp path can be rotated along the first direction of rotation such that the roller runs on the incline region up to the second plateau, thereby moving the piston to its rear end position.For the dispensing process, the tensioning device can rotate the ramp track along the first direction of rotation starting from a contact of the roller with the second plateau until the roller runs over the transition area and accelerates towards the first plateau due to the pre-tension, whereby the piston is moved towards the open dispensing end.

[0008] The device according to the invention is preferably designed as a self-filling syringe for needle-free application (in particular intramuscularly) in animals and / or humans.

[0009] According to the invention, the motor can be connected to the ramp via a coupling, wherein the coupling transmits the torque provided by the motor in the first direction of rotation for rotating the ramp and thereby provides a freewheel opposite to the first direction of rotation, which is designed to cover at least one rotation angle range corresponding to the transition range.

[0010] The clutch can be designed such that the freewheel covers a rotation angle range that is no more than twice the transition range. In particular, the freewheel can cover the rotation angle range that is 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80%, or 90% larger than the transition range.

[0011] The clutch may have a first clutch part connected to the motor and a second clutch part connected to the ramp. One of the two clutch parts may have a protruding engagement element, and the other of the two clutch parts may have a recess into which the engagement element projects. The extent of the engagement element in the first rotational direction may be smaller than the extent of the recess in the first rotational direction by at least the rotational angle range covering the transition region. Thus, the extent of the recess in the first rotational direction is greater than the extent of the engagement element in the first rotational direction, thereby providing the desired freewheel.

[0012] A spring can be arranged between a side surface of the engagement element and a side surface of the recess, which face each other in the first rotational direction. In particular, a spring can be arranged between all opposite side surfaces of the engagement element and the recess. The spring(s) can be attached to the engagement element.

[0013] The spring(s) can be designed as compression springs. In particular, they can be implemented as disc springs.

[0014] The engagement element can be designed as a web.

[0015] The first coupling part may comprise the engagement element. Furthermore, the ramp may comprise a base as the second coupling part, wherein the recess is formed in the base.

[0016] One of the two coupling parts can have a plurality of protruding engagement elements spaced apart from one another in the first direction. The other of the two coupling parts can have a plurality of recesses into which the engagement elements engage. The extent of each engagement element in the first direction of rotation is smaller than the extent of the corresponding recess in the first direction of rotation by at least the rotation angle range covering the transition region.

[0017] According to the invention, the ramp track can run on the end face of a wall extending along a circular path, wherein a cover is provided which overlaps the ramp track, the driver and the roller and has at least one wiper which extends counter to the first direction and which extends within the wall to the inside of the wall and thus wipes off lubricant located in the inside from the inside.

[0018] The cover may have a plurality of wipers extending opposite to the first direction, each of which extends within the wall in the direction of the inside of the wall and thus wipes lubricant located in the inside from the inside, wherein the wipers are spaced apart from one another along the first direction.

[0019] The scrapers can differ in length opposite to the first direction.

[0020] Furthermore, the wipers can differ in their extension towards the inside.

[0021] The wiper(s) may be formed on a frustoconical central portion. In particular, they may extend radially from the frustoconical central portion. The frustoconical central portion may extend opposite to the first direction. In particular, the frustoconical central portion may extend to the bottom of the ramp.

[0022] The middle part can also have any other shape. In particular, it can be cylindrical.

[0023] According to the invention, the piston rod can be connected to the driver via a joint.

[0024] In particular, to form the joint, the end of the piston rod facing away from the piston can be rounded and movably mounted in a bed.

[0025] The bed can be formed on a connecting part that presses against the rounded end of the piston rod by means of a screw screwed into the rounded end. The bed can be formed by a curved side of a washer (or shim).

[0026] Furthermore, the joint can have two washers (or shims) arranged one above the other, the opposing sides of which are curved so that they move against each other when the piston rod rotates. The two washers can be arranged on a side of the connecting part facing away from the rounded end of the piston rod.

[0027] The joint can be designed as a rotary joint and / or as a joint with exactly one degree of freedom.

[0028] The joint can allow a translational movement (preferably exactly a translational movement) transverse to the longitudinal direction of the piston rod.

[0029] According to the invention, the device for application can have exactly one cylinder with exactly one piston and exactly one piston rod, wherein the tensioning device has two helical springs running parallel to each other, both of which contribute to the applied preload when the piston is in its rear end position.

[0030] The two coil springs may be arranged at a distance from each other transversely to their longitudinal direction and / or have the same dimensions.

[0031] In particular, the coil springs can be arranged so that their longitudinal directions are parallel to the longitudinal direction of the piston rod.

[0032] The coil springs can be designed as compression springs.

[0033] The piston rod may be connected to two guide rods via a connecting part, each guide rod extending within one of the coil springs.

[0034] The tensioning device can have at least three coil springs running parallel to each other. In particular, the coil springs can be arranged symmetrically to the engine in a plane perpendicular to the longitudinal direction of the coil springs.

[0035] According to the invention, the device for applying a fluid can comprise a front part having the cylinder and the open discharge end and a rear part having the clamping device, wherein the front part and the rear part are formed from different materials.

[0036] The material of the front part can include titanium, steel or plastic and the material of the rear part can include titanium, aluminum, magnesium or plastic.

[0037] The device may comprise a housing enclosing the front part and the rear part, with a portion of the front part projecting from the housing.

[0038] According to the invention, the device can comprise a dosage adjustment device with a spacer and a movement unit, wherein the movement unit can move the spacer, when the piston is in its rear end position, from a neutral position in which the spacer is not positioned between the driver and the cylinder, into an active position between the driver and the cylinder, so that the driver, after the roller has overrun the transition area, is stopped by the spacer and thus the piston stroke during the movement of the piston to the open discharge end is shorter compared to the case in which the spacer is in its neutral position.

[0039] The spacer may have a threaded bore into which a threaded rod extends, which is rotated to move the spacer between its neutral position and its active position.

[0040] The spacer can be guided in such a way that the spacer can only move in a plane perpendicular to the piston rod.

[0041] The spacer may be designed such that when the driver is stopped by the spacer, the roller is not in contact with the spacer.

[0042] The spacer may have a first stop region and a second stop region for the driver, wherein the extension of the spacer along the first direction is smaller for the first stop region than for the second stop region, so that different piston stroke reductions can be set depending on whether the first or second stop region is moved into the active position of the spacer.

[0043] Of course, the spacer can also have three or more stop areas, wherein the extension of the spacer along the first direction is different for the stop areas, so that different piston stroke shortenings can be set depending on which stop area is moved into the active position of the spacer.

[0044] According to the invention, the device can have a control unit that measures a characteristic value during a clamping and / or dispensing process and, by comparing it with at least one default value, determines whether the clamping and / or dispensing process was carried out as intended. In particular, the measurement of the characteristic value can be performed during the dispensing process and the preceding clamping process, and, by comparing it with the at least one default value, determines whether both the clamping and dispensing processes were carried out as intended.

[0045] The parameters that can be measured are the current consumption of the motor, the acceleration acting on the application device and / or the sound (or noises; e.g. frequency spectrum, frequency(s), pitch, energy and / or volume).

[0046] A temporal target curve of the current consumption with a lower limit and an upper limit can be specified as the at least one default value, wherein the control unit determines the clamping process as intended if the measured current consumption during the entire clamping process is not less than the lower limit and not greater than the upper limit.

[0047] A desired temporal progression of the acceleration with an upper limit can be specified as the at least one preset value, wherein the control unit determines the dispensing process as intended if the measured acceleration during the entire dispensing process is not greater than the upper limit.

[0048] A first upper and a first lower target frequency and / or a first upper and a first lower target amplitude can be specified as the at least one default value, wherein the control unit determines the delivery process as intended if a main frequency of the measured frequency spectrum lies between the first upper and the first lower target frequency and / or the amplitude of the main frequency of the measured frequency spectrum lies between the first upper and the first lower target amplitude.

[0049] The main frequency here refers specifically to the frequency of the measured frequency spectrum that has the largest amplitude. The main frequency is usually the frequency that determines the pitch.

[0050] The first upper target frequency can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% higher than a predefined first target main frequency. Furthermore, the first lower target frequency can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% lower than the predefined first target main frequency.

[0051] The first upper target amplitude can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% greater than a predefined first target main amplitude. Furthermore, the first lower target amplitude can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% smaller than the predefined first target main amplitude.

[0052] Furthermore, a second upper and a second lower target frequency and / or a second upper and a second lower target amplitude can be specified as the at least one default value, wherein the control unit determines the delivery process as intended if a first secondary frequency of the measured frequency spectrum lies between the second upper and the second lower target frequency and / or the amplitude of the first secondary frequency of the measured frequency spectrum lies between the second upper and the second lower target amplitude.

[0053] The first secondary frequency is understood here in particular to be the frequency of the measured frequency spectrum which has the second highest amplitude and thus the largest amplitude after the main frequency.

[0054] The second upper target frequency can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% higher than a predefined first target secondary frequency. Furthermore, the second lower target frequency can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% lower than the predefined first target secondary frequency.

[0055] The second upper target amplitude can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% greater than a predefined first target secondary amplitude. Furthermore, the second lower target amplitude can be 0.5%, 1%, 1.5%, 2%, 2.5%, 3%, 3.5%, 4%, 4.5%, 5%, 6%, 7%, 8%, 9%, 10%, 12%, 14%, or 15% smaller than the predefined first target secondary amplitude.

[0056] Of course, a second, third, fourth, fifth and / or further secondary frequencies (whose amplitudes are each smaller) can be measured and taken into account in the same way to evaluate the delivery process.

[0057] The delivery process is determined to be as intended if the main frequency of the measured frequency spectrum is lower than the target frequency and / or the amplitude of the main frequency of the measured frequency spectrum is greater than the target amplitude. The main frequency is understood here in particular to be the frequency of the measured frequency spectrum with the largest amplitude. The main frequency is usually the frequency that determines the pitch.

[0058] The duration of the clamping process can be measured as a parameter.

[0059] A first target time period can be specified as a default value, whereby the control unit determines the clamping process as intended if the measured time period is greater than the first target time period.

[0060] A second target time period can be specified as a default value, whereby the control unit determines the clamping process as intended if the measured time period is less than the second target time period.

[0061] Furthermore, the angle of rotation swept along the first direction of rotation during the clamping process can be measured as a characteristic value.

[0062] A target angle of rotation can be specified as a default value, whereby the control unit determines the clamping process as intended if the measured swept angle of rotation is greater than the target angle of rotation.

[0063] It is understood that the features mentioned above and those to be explained below can be used not only in the combinations indicated, but also in other combinations or in isolation, without departing from the scope of the present invention.

[0064] The invention is explained in more detail below using exemplary embodiments with reference to the accompanying drawings, which also disclose features essential to the invention. These exemplary embodiments are for illustrative purposes only and are not to be interpreted as restrictive. For example, a description of an embodiment with a large number of elements or components should not be interpreted to mean that all of these elements or components are necessary for implementation. Rather, other embodiments may also contain alternative elements and components, fewer elements or components, or additional elements or components. Elements or components of different exemplary embodiments may be combined with one another unless otherwise stated. Modifications and variations described for one of the exemplary embodiments may also be applicable to other exemplary embodiments.To avoid repetition, identical or corresponding elements in different figures are designated by the same reference numerals and are not explained more than once. The figures show: . Fig. 1 is a perspective view of an embodiment of the application device 1 according to the invention; Fig. 2 is a front view of the cylinder-piston arrangement 10 of the application device 1; Fig. 3 is a sectional view of the cylinder-piston arrangement 10 along the section line AA in Fig. 2 ; Fig. 4 a sectional view of the cylinder-piston arrangement 10 along the section line BB in Fig. 3 ; Fig. 5 a sectional view of the cylinder-piston arrangement 10 according to the section line CC in Fig. 4 ; Fig. 6 is an isometric view of the cylinder-piston arrangement 10, wherein the device is tensioned and the piston is in its rear end position; Fig. 7 is an isometric view of the cylinder-piston arrangement 10, wherein the piston is in its front end position; Fig. 8 is a diagram illustrating the course of the ramp path 41, wherein the angle of rotation α is plotted along the x-axis and the stroke along the longitudinal axis of the piston rod 25 is plotted along the y-axis; Fig. 9 is a sectional view of the piston-cylinder arrangement 10 in the tensioned state according to Fig. 6 ; Fig. 10 a front view of the piston-cylinder arrangement 10, in which the piston is in its front end position; Fig. 11 a sectional view of the piston-cylinder arrangement 10 according to the section line DD in Fig. 10 ; Fig. 12A-12C representations to explain the forces when the roller 40 runs over the transition area 46 towards the jump flank 47; Fig. 13 a front view of the base 60 of the ramp 42; Fig. 14 an isometric view of the coupling part 66 connected to the motor 51 in a rotationally fixed manner; Fig. 15 a side view of the coupling part 66; Fig. 16 a front view of the coupling part 66; Fig. 17 a front view of the coupling part 66 inserted into the recess 61 in the base 60; Figs. 18 and 19 representations according to Fig. 17 to explain the freewheel provided by the clutch 50; Fig. 20 is a schematic front view of the spatial arrangement of the springs 32 and 33 and the motor 51; Fig. 21 is a comparative view of the arrangement of a spring and the motor of a conventional application device; Figs. 22 and 23 are further views of further exemplary embodiments for the spatial arrangement of spring and motor in the application device 1 according to the invention; Fig. 24 is a view of the front part 11 and rear part 12 in the connected state; Fig. 25 is a view of the front part 11 and the rear part 12 in the unconnected state; Fig. 26 is an enlarged detailed section of the dosage setting device 36; Fig. 27A is a perspective view of the spacer 70; Fig. 27B is a schematic representation of a further embodiment of a spacer 70; Fig. 28 is a perspective representation of the cover 35; Fig. 29 a front view of the cover 35; Fig.30a sectional view along section line BB in . Fig. 29 ; Fig. 31 a sectional view along the section line AA in Fig. 29 ; Fig. 32 a front view of the cover 31; Fig. 33 a sectional view of the cover 35 along the section line CC in Fig. 32 ; Fig. 34 an enlarged sectional view of the front part 11 including piston 26 and part of the piston rod 25; Fig. 35 a schematic sectional view of an insert 96 for the nozzle 16; Fig. 36 a schematic sectional view of piston rod 25, plate 28 as well as guide rods 29 and 30 and springs 32 and 33; Fig. 37 an enlarged view of detail A of Fig. 36 ; Fig. 38 and 39 diagrams with measured values ​​of acceleration values ​​during the clamping and release process; Fig. 40 and 41 diagrams with measured values ​​of the measured current consumption of the motor 51 during a clamping and release process.

[0065] In the Fig. 1 In the exemplary embodiment shown, the device 1 according to the invention for applying a fluid (e.g. a liquid) comprises a housing 2 with a main section 3 and a handle section 4. The handle section 4 is designed such that a user can hold the device 1 by grasping the handle section. Furthermore, the handle section 4 has a trigger 5 for actuating the device. A dispensing area 6 is formed at the front end of the main section 3. Furthermore, the device 1 has a connection 7 at the upper area of ​​the main section 3, to which a hose or a container, for example, can be connected. The fluid to be applied can be supplied via the hose. The fluid to be applied can similarly be contained in the container.

[0066] The handle section 4 merges at its end pointing away from the main section 3 into a foot 8, in which, for example, a power supply (for example a battery) for the device 1 can be contained.

[0067] The device 1 according to the invention, which can also be referred to as an application device 1, is designed in the embodiment described here for the needleless application of the fluid to an animal. The application preferably involves an intramuscular injection of the fluid, which may be, for example, a medicament, a vaccine, or the like.

[0068] The application device 1 has a cylinder-piston arrangement 10 ( Fig. 3 and 4) and is designed as a self-filling type in such a way that a piston movement towards the dispensing area 6 causes the fluid to be ejected and an opposite movement of the piston causes the cylinder to be filled with the fluid for the next ejection process.

[0069] In Fig. 2 bis 5 The entire cylinder-piston assembly 10 is shown without the housing 2. The cylinder-piston assembly 10 comprises a front part 11 and a rear part 12 connected thereto. The front part 11 comprises a cylinder 13 for receiving the fluid, which has an open discharge end 14 in which a check valve 15 is seated, which is in fluid communication with a nozzle 16. The check valve 15 is also clearly visible in the illustration according to Fig. 34 and is designed to allow the fluid to be discharged from the cylinder 13 via the check valve 15 and the nozzle 16. Suction of air or liquid via the nozzle and the check valve 15 is not possible. In this direction, the check valve 15 closes.

[0070] The front part 11 also has a connection 7 in which a further check valve 20 ( Fig. 3 ) that allows fluid communication from port 7 to cylinder 13 and blocks fluid communication in the opposite direction. Port 7 has a channel 21 that opens into cylinder 13 via several radial bores 22.

[0071] The further check valve 20 can thus be referred to as an inlet valve and the check valve 15 can be referred to as an outlet valve.

[0072] In the cylinder 13, a piston rod 25 is guided with a piston 26 formed at its end pointing towards the open discharge end 14, wherein the piston 26 in the sectional views of Fig. 3 and 4 is in its rear end position. In this position, cylinder 13 is filled with the fluid to be dispensed.

[0073] The rear end 27 pointing away from the open discharge end 14 (well in Fig. 37 can be seen) of the piston rod 25 is connected via a plate 28 to a first guide rod 29 and a second guide rod 30, which extend parallel to each other and parallel to the piston rod 25 and which are guided in the rear part 12 ( Fig. 4 ). The ends of the guide rods 29 and 30 pointing away from the plate 28 are connected to a driver 31.

[0074] Furthermore, for each guide rod 29 and 30, a compression spring 32, 33 (e.g. coil spring) is arranged, the front ends of which each rest on the plate 28 and the rear ends of which each rest on a stop 34 of the rear part 12. In the Fig. 3 and 4 In the position of the piston 26 shown, the springs 32, 33 are tensioned.

[0075] At the rear end of the rear part 12, a cover 35 and a metering adjustment device 36 are provided, which in the isometric view of the cylinder-piston arrangement 10 according to Fig. 6 are not shown, so that the driver 31 is clearly visible. The driver 31 has a rotatably mounted roller 40, wherein the axis of rotation of the roller 40 extends substantially perpendicular to the longitudinal axis of the piston rod 25.

[0076] The roller 40 runs on a ramp track 41 of a ramp 42 rotating beneath the roller 40, wherein the ramp track 41 has a single turn, as in particular Fig. 6 bis 8 can be seen.

[0077] In Fig. 8 the angle of rotation α is plotted against the pitch difference z parallel to the longitudinal direction of the piston rod 25, whereby it is assumed that at a rotation angle of α0 = 0° the smallest pitch z0 is present and the piston 26 is thus in a front end position in which its distance to the open discharge end 14 is minimal. This position of the piston 26 is shown, for example, in the sectional view according to Fig. 11 shown.

[0078] The ramp track 41 has a lower plateau 43, followed by a gradient area 44 that extends to the upper plateau 45. The upper plateau 45 is followed by a transition area 46, which leads into a jump flank 47 (angle of rotation α1), which leads back to the first plateau 43. Thus, the angle of rotation range from α0 to α2 is equal to 360°.

[0079] The jump flank 47 is characterized by its quasi-vertical nature, extending from height z1 to height z0 at a rotation angle (here α2). The transition region 46 is thus the rotation angle range in which the height z1 continuously decreases, starting from the upper plateau 45, until the rotation angle α2 (= jump flank 47) is reached. Thus, the rotation angle range from α1 to α2 covers the transition region 46.

[0080] The ramp 42 is connected to a motor 51 via a coupling 50 ( Fig. 3 ), which rotates the ramp 42 in a first direction of rotation 52 ( Figuren 6 and 7 ). If the motor 51 now follows the ramp 42 starting from the Fig. 6 shown position, in which the cylinder-piston arrangement 10 is tensioned, continues to rotate in the first rotational direction 52 (because a user has actuated the trigger 5), the roller 40 runs over the transition area 46 and then falls along the jump flank 47 towards the lower plateau 43, since the tensioned compression springs 32 and 33 accelerate the plate 28 towards the open discharge end 14, whereby the piston rod 25 connected to the plate 28 is also moved towards the front discharge end 14 and the fluid contained in the cylinder 13 is sprayed out via the check valve 15 and the nozzle 16 for intramuscular injection into an animal. The application device 1 is designed so that the fluid safely penetrates the skin and is applied into the underlying muscle. The piston 26 is then in its front end position, as shown, for example, in the sectional view in Fig. 11 is shown. The application device 1 is preferably designed such that, in the front end position of the piston 26, the driver 31 rests against the rear end of the rear part 12, whereby the rear end of the rear part 12 forms a stop for the driver 31. In this position, a desired minimum distance still exists between the roller 40 and the ramp track 41, so that the roller 40 does not reach the lower plateau 43 of the ramp track 41. This can prevent the roller 40 from hitting the ramp track 41 at the end of the ejection process, which could lead to damage to the roller 40.

[0081] After the ejection process, the ramp 42 is rotated again in the first direction of rotation 52 by means of the motor 51, so that as soon as the roller 40 makes contact with the ramp track 41 in the incline region 44, further rotation results in the driver 31 being moved along the longitudinal direction of the piston rod 25 away from the open discharge end 14, whereby the compression springs 32, 33 are tensioned again and reach their maximum tension when the roller 40 reaches the upper plateau 45. This movement of the driver 31, due to the mechanical connection of the driver 31 to the guide rods 29 and 30, the plate 28 and the piston rod 25, also results in the piston rod 25 and thus the piston 26 being moved in a direction away from the open discharge end in the cylinder 13, thus building up a negative pressure.As soon as the built-up negative pressure is so great that the inlet valve 20 opens, the fluid is sucked through the inlet valve 20 and the radial bores 22 into the cylinder 13, so that the cylinder 13 is filled with the fluid.

[0082] When the roller 40 (which may also be referred to as a cam or roller) has reached the upper plateau 45, the motor 51 stops, so that the cylinder-piston arrangement 10 is tensioned and thus the application device 1 is ready for the next application process, which can be carried out by actuating the trigger 5.

[0083] The plate 28, the springs 32, 33 including guide rods 29, 30, the driver 31 with roller 40, the ramp 42 together with the motor 51 and the coupling 50 form a clamping device S for clamping the cylinder-piston arrangement 10.

[0084] Furthermore, the application device 1 comprises a control unit 54 for controlling the motor 51 and all other electrical components of the device 1. In Fig. 3 a circuit board with the control unit 54 is shown.

[0085] As already described, to apply the fluid, start from the Fig. 6 In the rotational position of the ramp 42 shown, the ramp is rotated further in the first direction of rotation 52, so that the roller 40 runs from the upper plateau 45 over the transition area 46 and is then accelerated along the jump flank 47 to the lower plateau 53. However, when overrunning the transition area 46, the difficulty arises ( Fig. 12A - 12C ) that the spring force F of the tensioned springs 32, 33 has, in addition to a tangential component Ft, a component Fs perpendicular thereto, which includes a component Fd that points in the same direction as the force of the motor Fm for rotating the ramp 42. As a result, the roller 40 running over the transition area 46 accelerates the rotation of the ramp 42 (in addition to the rotation caused by the motor 51). This can disadvantageously result in the motor 51 acting as a generator for this additional acceleration and generating a voltage peak that can damage the control electronics of the control unit 54. In addition, the motor 51 therefore acts as a brake, so that an undesirable braking effect occurs when the ramp 42 rotates, which changes the pressure curve during the application process in an undesirable manner.

[0086] Therefore, the clutch 50 is designed such that it transmits the torque provided by the motor 51 for rotating the ramp track 41 in the first direction of rotation 52 and at the same time has a freewheel opposite to the first direction of rotation 52, which is designed such that it covers at least the rotation angle range (from α1 to α2) corresponding to the transition range 46 (here, for example, 7°).

[0087] To form the coupling 50, a star-shaped recess 61 is formed in a base 60 of the ramp 42 ( Fig. 13 ). The star-shaped recess 61 comprises a central portion 62 and four arms 63 extending therefrom, which are spaced 90° apart from each other in the circumferential direction. As shown in Fig. 13 As is shown schematically for one of the arms 63, the side surfaces 64, 65 of the arms 63 are inclined to each other so that they enclose an angle ß which corresponds at least to the angle of rotation of the transition region 46 and thus here to 7°.

[0088] Furthermore, the coupling 50 comprises a coupling part 66 connected to the motor, which has four star-shaped walls 67, each spaced 90° apart from each other in the circumferential direction. A spring 69 (here a disc spring) is arranged on each side surface 68 of each wall. The springs 69 serve to support the movement and provide damping. The walls 67 of the star-shaped contour of the coupling part 66 are inserted into the star-shaped recess 61 of the base 60 of the ramp 42, as shown in the front view according to Fig. 17 is shown. Due to the springs 69, each wall 67 is centered in the corresponding arm 63 of the star-shaped recess 61 when no torque is transmitted via the coupling 50.

[0089] When the roller 40 is rotated in the first direction of rotation 52 by means of the motor 51, the front side surfaces 68 seen in the first direction of rotation 52 rest against the corresponding side surface 64 of each arm 63, as shown in Fig. 18 is shown.

[0090] When the roller 40, starting from the upper plateau 45, overruns the transition area 46, the ramp 42 is additionally accelerated in the first direction of rotation 52 due to the described spring force (here the component Fd), so that due to the provided freewheel, the ramp 42 can rotate faster in the first direction of rotation 52 than the coupling part 66 connected to the motor 51. This freewheel ends as soon as the rear side surface 68 of the respective wall 67, seen in the first direction of rotation 52, rests against the side surface 65 of the corresponding arm 63 of the star-shaped recess 61, as in Fig. 19 As the freewheel is designed to cover at least the entire transition area 46, the roller 40 is moved beyond the entire transition area 46 as soon as the contact according to Fig. 19 This allows the roller 40 to move freely along the jump flank 47, and the undesirable acceleration of the rotational movement of the motor 51 when overrunning the transition area 46 is reliably avoided.

[0091] In Fig. 20 A schematic front view is shown showing the spatial arrangement of the springs 32 and 33 as well as the motor 51. The two springs 32 and 33 are connected in parallel via the plate 28, so that their spring rates (spring constants) add up. Thus, when the piston 26 is in its rear end position, the necessary force (spring force) can be provided, which is necessary to accelerate the piston 26 so strongly that the released fluid can be administered intramuscularly to an animal. At the same time, the necessary installation space for the cylinder-piston arrangement 10 can be kept small and compact. As a comparison with the illustration in Fig. 21 shows, in which only one spring 32' is provided instead of the two springs 32 and 33, this would result in a larger installation space for the corresponding cylinder-piston arrangement 10', since this single spring 33' would have to have a larger diameter in order to provide the same spring force.

[0092] Of course, it is also possible to connect more than two springs 32 and 33 in parallel. As shown in the schematic diagrams of Fig. 22 und 23 As can be seen, for example, three or four springs 32, 33, 37 and optionally 38 can be provided in order to achieve a compact design. The more than two (here three or four) springs can preferably be arranged symmetrically to the motor 51, as in Fig. 22 und 23 is shown.

[0093] As already explained, the front part 11 and the rear part 12 are two separate parts that are connected to each other, as can be seen from the illustrations in Fig. 24 and 25 can be seen.

[0094] Preferably, the front part 11 and the rear part 12 are made of different materials. Since the front section of the front part 11 protrudes from the housing 2 ( Fig. 1 ), a material is selected which, for example, has a higher strength than the material for the rear part and / or which has better media resistance than the material of the rear part 12.

[0095] The material of the front part 11 can be titanium, steel or plastic (e.g. PEEK).

[0096] For the rear part 12, a material that is as lightweight as possible is selected. Aluminum, magnesium, titanium, or plastic are preferred.

[0097] The dosing adjustment device 36 comprises, as can be seen in particular from the enlarged detailed sectional view in Fig. 26 as well as Fig. 27A can be seen, a spacer 70, into which a threaded rod 71 is screwed, which is coupled via a first and second gear 72, 73 to a shaft 74 of a second motor 75. The threaded rod 71 is inserted into a threaded hole 76 in the spacer 70 ( Fig. 3 ) screwed in. Furthermore, the spacer 70 comprises two laterally projecting guide webs 77, 78 ( Fig. 27A ). The guide bars 77, 78 are guided in guide grooves 79 of the cover 35. The guide grooves 79 are best positioned in Fig. 28 Furthermore, the cover 35 includes an opening 80 through which the spacer 70 can be moved.

[0098] In the representation according to Fig. 3 the spacer 70 is in its neutral position, in which it does not influence the return movement of the roller 40 and thus of the driver 31 from the upper plateau 45 over the transition area 46 along the jump flank 47 to the lower plateau 43. In Fig. 26 the spacer 70 has been moved into its active position, in which it is positioned between the driver 31 and the rear end of the rear part 12 so that it forms a stop for the driver 31. The movement of the spacer from the Fig. 3 shown position to that in Fig. 26 The position shown is generated by a rotation of the shaft 74, whereby, for example, a right rotation of the shaft 74 causes a movement from the position shown in Fig. 3 shown position to that in Fig. 6 shown position, and a left-hand rotation of the shaft 74 causes an opposite movement. Of course, the dosage adjustment device 36 can also be designed so that the opposite directions of rotation cause the same movements. What is important here is that the two gears 72 and 73, and thus the shaft 74, can be rotated by means of the second motor 75 in order to convert this rotational movement into a translational movement of the spacer 70 perpendicular to the longitudinal direction of the piston rod 25. The spacer 70 can thus be moved back and forth between its active position and its neutral position.

[0099] If the spacer 70 is now in the Fig. 26 shown active position, the movement of the driver 31 in the longitudinal direction of the piston rod 25 is shortened after the roller 40 has overrun the transition area 46, since this movement now ends when the driver 31 rests against the spacer 70. The extension of the spacer 70 along the longitudinal direction of the piston rod 25 thus corresponds to the shortening of the piston stroke when applying the fluid located in the cylinder 13. This allows a smaller amount of fluid to be ejected, whereby two different dosages can be administered with the application device 1 (here, for example, 2 ml and 1 ml). If the dosage is to be changed, the spacer 70 only has to be moved to its Fig. 26 shown active position.

[0100] The spacer 70 is designed such that, when the driver 31 rests against it, the roller 40 has no contact with the spacer 70. This prevents the roller 40 from being damaged when the driver 31 is stopped by the spacer 70.

[0101] With the described spacer according to Fig. 27A It is therefore possible to set a single lower dosage, as described. Fig. 27B a modification of the spacer 70 is shown, with which it is possible to set two different lower dosages, since the spacer 70 has a first stop area 140 and a second stop area 141, which extend through the extension of the spacer 70 along the first direction (in Fig. 27B from left to right). Since this expansion corresponds to the reduction in the piston stroke of the piston 26 during the application process, two different reductions in dosage are possible. If the spacer 70 is retracted so far between the driver 31 and the rear end of the rear part 12 that the driver 31 is stopped by the section 140 during the application process, a first reduction in the piston stroke occurs. If, on the other hand, the spacer 70 is retracted so far that the driver 31 rests against the area 141 during the application process, then a second reduction in the piston stroke occurs, which is greater than the reduction by the section 140. This stepped design of the spacer 70 thus makes it possible to set two different reductions in dosage.

[0102] For example, in Fig. 28 As can be clearly seen, the cover 35 comprises a first, second and third wiper 80, 81, 82 which, in the assembled state according to Fig. 3 , extend from a rear end of the cover 35 towards the discharge end of the application device 1. Such as Fig. 28 As can be seen, the scrapers 80-82 are formed on a frustoconical central part 83 and are spaced apart from each other in the circumferential direction. The frustoconical central part 83 tapers towards the discharge end, as shown in Fig. 3 is evident.

[0103] In the assembled state, the frustoconical central part 83 extends to the bottom 60 of the ramp 41. In the same way, the first wiper 80 extends to the bottom 60. In the radial direction, the first wiper 80 extends to the inside 84 of the wall 85, on the front side of which the ramp track 42 is formed ( Fig. 6 ).

[0104] The second wiper 81 is shorter in both the axial and radial directions than the first wiper 80. Similarly, the third wiper 82 is shorter in both the radial and axial directions than the second wiper 81.

[0105] Furthermore, the cover 35 comprises an intermediate wall 86 in which an axially extending slot is formed, in which the roller 40, together with its mounting section of the driver 31, can move in the axial direction. Otherwise, the intermediate wall 86, together with the lower cover part 88, surrounds the outer side 89 of the wall 85 in the assembled state. In this remaining space between the cover 35 and the wall 85, a lubricant (for example, a grease) is provided, which serves to ensure that the roller 40 rotates as smoothly as possible and is guided on the ramp track 41 with as little friction as possible. The wipers 80 to 82 move the grease that does not remain on the ramp track 41 back towards the ramp track and roller 40 due to the relative movement between the ramp track 41 and the wipers 80-82, so that permanent lubrication can be ensured.Thus, the lubricant that accumulates at the bottom of the cover 35 is conveyed back to the ramp track 41 and the roller 40, so that the desired permanent lubrication is ensured.

[0106] In Fig. 34 An enlarged sectional view of the front part 11 including the piston 26 and part of the piston rod 25 is shown. The cylinder 13 has an annular groove 90 in its rear region (facing away from the open discharge end 14), in which an O-ring 91 or a sealing ring 91 (e.g., an elastomer seal) is inserted for sealing. Furthermore, a first and a second support ring (92, 93) are arranged in the groove 90 such that the sealing ring 91 is positioned between the two support rings 92 and 93. The groove 90 and the support rings 92 and 93 are dimensioned such that the gap between the support rings 92 and 93 and the piston rod 25 is smaller than between the inside of the cylinder 13 and the piston rod 25. The support rings, which can be made of PTFE or other plastics, for example, reliably prevent a part of the sealing ring 91 from breaking off due to the pressure built up when the piston rod 95 moves.negative pressure is extruded into the gap between the piston rod 25 and the inside of the cylinder 13, which would destroy the sealing ring 91.

[0107] The second support ring 93 prevents the described gap extrusion during a movement of the piston rod 25 toward the open discharge end 14, thus during the application of the fluid. The first support ring 92 prevents the undesired gap extrusion during the opposite movement, thus during the filling of the cylinder 13 with the fluid.

[0108] As in Fig. 34 As can be seen, the nozzle 16 has a tapered through-bore 95 through which the fluid is dispensed during application. The necessary through-bore 95 can also be formed in an insert 96, as in Fig. 35 which is then to be screwed into the remaining nozzle body 97. The insert 96 comprises a base body 98 with an external thread, which comprises a receiving area 99 at the distal end. A sapphire element 100 is inserted into the receiving area 99, in which the last section of the through-bore 95 is formed. As shown in Fig. 35 can be seen, the diameter of the last section of the through-bore 95 is the smallest, or smaller, than the diameter of the sections of the through-bore 95 formed in the base body 98. This advantageously ensures that the necessary very small diameter of the through-bore 95 at its distal end can be reliably manufactured, since the section of the through-bore 95 in the sapphire element 100 can be manufactured more precisely than a bore in the base body 98, which is made of metal. The diameter of the last section of the through-bore 95 in the sapphire element 100 can, for example, be in the range from 0.30 to 0.38 mm, whereby the manufacturing tolerance should not be greater than 0.02 mm.

[0109] Since the unit consisting of piston rod 26, plate 28, and guide rods 29, 30 is relatively long and high forces are exerted during fluid application, it must be ensured that the piston rod 26 can move freely in the cylinder 13 and, for example, does not become jammed. To this end, the piston rod 26 should be aligned as parallel as possible to the guide rods 29, 30, and this should remain the case even over extended periods of use of the application device 1.

[0110] Therefore, the piston rod 25 is not absolutely rigidly connected to the plate 28. The connection is designed in such a way that tilting or rotation of the piston rod 26 relative to the plate 28 is possible. The piston rod 25 is thus connected to the plate 28 via a swivel joint. As can be seen from the illustrations in Fig. 36 and 39As can be seen, a first washer 110 is provided between the rear end 27 of the piston rod 25 and the plate 28. Furthermore, a fixing screw 111 is screwed into the rear end 27 and runs through a corresponding hole in the plate 28. Between a head 112 of the fixing screw 111, a second and a third washer 113, 114 are arranged. In order to provide the desired rotatability, the rear end 27 is rounded (here, for example, spherical) and the side of the first washer 110 facing the rear end 27 is correspondingly concave, so that this side forms a bed for the rear end 27. As shown in Fig. 37 As can be seen, the first washer 110 sits in a recess in the plate 28, so that the first washer 110 cannot move transversely to the longitudinal direction of the piston rod 25. The side of the first washer 110 facing away from the rear end 27 is flat, since the corresponding bottom of the recess in the plate 28 is also flat. Thus, the first washer can also be described as concave-flat.

[0111] The second and third washers 113 and 114 are designed such that the sides facing each other are again curved. The side of the second washer 113 facing the third washer 114 has a convex curvature. The side of the third washer 114 facing the second washer 113 is correspondingly concavely curved. The other sides of the second and third washers 113, 114 are flat. The head 112 of the fixing screw 111 presses the third washer 114 onto the second washer 113, which is thereby pressed against the side of the plate 28 facing away from the rear end 27. The second washer 113 is thus plano-convex, and the third washer 114 is thus concave-flat.

[0112] Due to the selected dimensions and curvatures, the pivot point 115 for the rotation of the piston rod 25 relative to the plate 28 is spaced from the plate 28 and on the side of the screw head 112.

[0113] Since the described connection allows rotation of the piston rod 25 relative to the plate 28, it can be ensured that the piston rod 25 can always be moved in the cylinder 13 without jamming.

[0114] The motor 51 can be designed as an electric motor, particularly as a brushless electric motor. This improves the durability of the application device 1, since electric motors with brushes can be problematic because the brushes can break due to the vibrations that occur during fluid application.

[0115] To detect whether fluid in cylinder 13 is present at the Fig. 3 shown position of the piston 26, a sensor 55 is provided which, in the embodiment described here, is arranged upstream of the further check valve 20 (which can also be referred to as the inlet valve). The sensor 55 can, for example, distinguish between air and liquid, so that the application device 1 can be prevented from carrying out an application process when there is no liquid in the cylinder 13. This can prevent damage to the application device 1, since it is designed such that the liquid dampens the movement of the piston rod 25 or the piston 26 during application towards the open discharge end. If there is no liquid in the cylinder 13, this dampening function is omitted, which can lead to mechanical damage, for example to the piston rod 25, the connection of the piston rod 25 to the plate 28 or to the guide rods 29, 30.The sensor 55 can be designed as a voltage sensor, as a capacitive sensor or, for example, as a light barrier.

[0116] The housing 2 may have a luminous area 120 ( Fig. 1 ), which can illuminate in different colors. The area 120 can, for example, be strip-shaped or have any other shape. The different colors can be used to communicate user information about the status of the application device 1. For example, a first color (for example the color red) can be used to inform the user that the device 1 is not ready to be used. A second color can be used to inform that it is basically ready for operation. A third color can be used to inform that the cylinder-piston arrangement 10 is tensioned and that an application process can be carried out by actuating the trigger 5. A fourth color (for example green) can be used to inform the user that the application process was successful. Furthermore, a further color can be used to inform the user that an error condition exists.Of course, the described information can be communicated not only through different colors, but also through the same colors, if the differences are represented, for example, by different flashing patterns. It is also possible to provide the user with haptic or acoustic feedback instead of the described visual feedback. Of course, visual, haptic, and acoustic feedback can also be combined.

[0117] Furthermore, the application device 1 can have an acceleration sensor 130, which, for example, is only Fig. 3 Since the measured acceleration values ​​for a correct application process differ from those of an incorrect application process, the measured values ​​can be used to decide whether an application process was successful or not. Fig. 38 The measured acceleration values ​​for a successful application process are plotted along the y-axis in g (= acceleration due to gravity) versus time along the x-axis (in ms). The measured acceleration values ​​are shown as points connected by a line. A test curve is shown in dashed lines. If the acceleration values ​​are below the values ​​of the test curve, the application process is determined to have been successful.

[0118] In Fig. 39 An example of an unsuccessful application process (hereinafter referred to as a shot) is shown. The acceleration values ​​exceed the maximum value of the test curve, so it can be assumed that the shot was unsuccessful.

[0119] Furthermore, the current consumption of the motor 51 can be measured and evaluated to assess the quality of the shot.

[0120] In Fig. 40 The measured current consumption for the charging and firing process of the application device 1 is shown, with the measured current values ​​in A (= amperes) plotted as points connected by a line. The current value is plotted along the y-axis (versus time in ms along the x-axis). A successful charging and firing process occurs when the measured current values ​​are less than the upper limit curve and greater than the lower limit curve (both curves are shown in dashed lines).

[0121] In the case of an unsuccessful shot, the measured current consumption is outside the range limited by the two limit curves, as shown in Fig. 41 shown. In this case, the application process was not successful.

[0122] Instead of or in addition to the acceleration sensor 130, a sensor 131 for measuring sound or tones (e.g. a microphone) can be provided, which is shown schematically in Fig. 3is shown. Based on the pitches during the delivery process, it can be determined, for example, whether the application process was successful or not. If the temporal progression of the measured pitch is, for example, higher than a specified upper limit or is a temporal progression of the upper limit, the application process is assessed as unsuccessful. The temporal progression of the measured pitch can also, for example, fall below a temporal progression of a lower limit, which suggests a faulty application process. For example, a measured frequency spectrum can also be evaluated as a parameter that must fulfill a target temporal progression in order for the application process to be assessed as successful. In the same way, the temporal progression of the intensity (or volume) can be used as a parameter, which in turn must fulfill a target temporal progression.

[0123] Of course, several of the described parameters can also be used to evaluate the application process. For example, only the dispensing process, only the clamping process, or both the clamping and dispensing processes can be measured and evaluated.

[0124] The control unit 54 can perform the described measurement and evaluation of the parameters to determine whether the application process was successful or not. Depending on the decision, the control unit can, for example, generate visual, haptic, and / or acoustic feedback in the manner described.

Claims

1. A device for administering a fluid, comprising a cylinder (13), which has an open dispensing end (14), a piston (26), which is displaceable in the cylinder (13) between a front end position and a rear end position and is connected to a piston rod (25) which, along a first direction, protrudes from a rear end of the cylinder (13) opposite the open dispensing end (14), a nonreturn valve (15) closing the open dispensing end, and a tensioning device (S) connected to the piston rod (25); wherein the tensioning device (S) can move the piston rod (25) along the first direction in a tensioning procedure until the piston (26) is in its rear end position, in order thereby to fill the cylinder (13) with the fluid to be administered and to pretension the piston rod (25) toward the open dispensing end (14), and wherein the tensioning device (S), when the piston (26) is in its rear end position, can release the piston rod (25) in a dispensing procedure such that, owing to the pretension which is present, the piston (26) is moved counter to the first direction toward the open dispensing end (14) and, in the process, fluid in the cylinder (13) is dispensed via the nonreturn valve (15) for administration, characterized in that the tensioning device (S) has a ramp (42) which is rotatable by means of a motor (51) and has a ramp track (41) extending along a helical line, wherein the ramp track (41) ascends from a first plateau (43) along a region of inclination (44) to a second plateau (45) and descends from the second plateau (45) to the first plateau (43) via a transition flank (47), wherein the ramp track has a transfer region (46) connecting the second plateau (45) and the transition flank (47), wherein the tensioning device (S) moreover has a roller (40) which is in contact with the ramp track (41) and which is mounted rotatably in a driver (31), the latter being connected to the piston rod (25), and therefore, upon rotation of the ramp (42) along a first rotation direction (52), the ramp track (41) runs below the thus rotating roller (40), wherein, for the tensioning procedure, the ramp track (41) is rotated along the first rotation direction (52) such that the roller (40) runs on the region of inclination (44) as far as the second plateau (45) and the piston (26) is thereby moved to its rear end position, wherein, for the dispensing procedure, starting from a contact of the roller (40) with the second plateau (45), the ramp track (41) is rotated along the first rotation direction (52) until the roller (40) runs over the transfer region (46) and, on account of the pretension, is accelerated toward the first plateau (43) and, as a result, the piston (26) is moved toward the open dispensing end (14), wherein the motor (51) is connected to the ramp (42) via a coupling (50), wherein, for the rotation of the ramp (42), the coupling (50) transmits the torque, which is provided by the motor (41), in the first rotation direction (52) and, in the process, provides a freewheel counter to the first rotation direction (52), the freewheel being configured in such a manner that it covers at least a rotation angle range which corresponds to the transfer region (46).

2. The device as claimed in claim 1, wherein the coupling (50) is designed in such a manner that the freewheel covers a rotation angle range which corresponds to no more than twice the transfer region (46).

3. The device as claimed in claim 1 or 2, wherein the coupling (50) has a first coupling part (66), which is connected to the motor (51), and a second coupling part (60), which is connected to the ramp (42), wherein one of the two coupling parts (66) has a protruding engagement element (67) and the other of the two coupling parts (60) has a recess (63) into which the engagement element (67) protrudes, wherein the extent of the engagement element (67) in the first rotation direction (52) is smaller by at least the rotation angle range covering the transfer region (46) than the extent of the recess (63) in the first rotation direction (52).

4. The device as claimed in claim 3, wherein a spring (69) is arranged between a side surface (68) of the engagement element (66) and a side surface (64, 65) of the recess (63), said side surfaces facing each other in the first rotation direction (52).

5. The device as claimed in claim 4, wherein the spring (69) is designed as a compression spring.

6. The device as claimed in one of claims 3 to 5, wherein the engagement element (67) is designed as a web.

7. The device as claimed in one of claims 3 to 6, wherein the first coupling part (66) has the engagement element (67).

8. The device as claimed in one of claims 3 to 7, wherein the ramp (42) comprises a base (60) as the second coupling part and wherein the recess (63) is formed in the base (60).

9. The device as claimed in one of claims 3 to 8, wherein one of the two coupling parts (66) has a plurality of protruding engagement elements (67) which are spaced apart from one another in the first rotation direction (52), and the other of the two coupling parts (60) has a plurality of recesses (63) into which the engagement elements (67) protrude, wherein the extent of each engagement element (67) in the first rotation direction (52) is smaller by at least the rotation angle range covering the transfer region (46) than the extent of the corresponding recess (63) in the first rotation direction (52).