Device for applying fluid

Abstract

A device for applying fluid is provided, comprising: a cylinder (13); a piston (26) movable within the cylinder (13) between a front end position and a rear end position and connected to a piston rod (25); and a tensioning device (S) connected to the piston rod (25); wherein the tensioning device (S) has a ramp (42) rotatable by a motor (51) and a ramp path (41) extending along a helical line; wherein the tensioning device (S) further comprises a roller (40) contacting the ramp path (41) and rotatably mounted in a driver (31) connected to the piston rod (25), such that when the ramp (42) rotates in a first rotation direction (52), the ramp path (41) travels below the rotating roller (40); wherein a dose setting device (36) is provided, comprising a spacer (70) and a moving unit, wherein when the moving unit... When the plug (26) is in its rear end position, the moving unit can move the spacer (70) from the neutral position where the spacer (70) is not located between the driver (31) and the cylinder (13) into the working position between the driver (31) and the cylinder (13), such that the driver (31) is stopped by the spacer (70) after the roller (40) passes through the transition area (46), thereby resulting in a shorter piston stroke during the movement of the piston (26) toward the open distribution end compared to when the spacer (70) is in its neutral position; wherein the spacer (70) has a through hole (140) in which a spindle (143) having a spindle thread (142) is guided, wherein the spacer (70) has a pin (141) protruding into the spindle thread (142), and wherein the spindle thread (142) is inserted into an annular groove (144, 145) at at least one of its two ends.

Description

TECHNICAL FIELD

[0001] The present invention relates to a device for administering a fluid, which can be designed as a needle-free self-filling syringe, through which a liquid drug, a liquid medicament product, a liquid vaccine, etc. can be administered to an animal by intramuscular administration injection. BACKGROUND

[0002] Such a device for administering a fluid should be as light as possible, so that it can be held by the user for a long time with one hand, while it should allow the desired needle-free intramuscular injection. SUMMARY

[0003] It is therefore an object of the present invention to provide such a device for administering a fluid.

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

[0005] The device for administering a fluid according to the invention comprises a cylinder with an open administration end, a piston, a non-return valve, and a tensioning device connected to the piston rod, the piston being movable in the cylinder between a front end position and a rear end position and being connected to the piston rod, the piston rod projecting in a first direction from a rear end of the cylinder opposite the open administration end, the non-return valve, which functions as an outlet valve, closing the open administration end. The tensioning device can move the piston rod in the first direction during a tensioning process until the piston is in its rear end position in order to thereby fill the cylinder with the fluid to be administered and to pre-tension the piston rod towards the open administration end. To this end, the device can have an accessory which opens into the cylinder. For example, a hose or a container with the fluid to be administered can be fixed on the accessory and can be fixed for use of the device. Preferably, the accessory can have a non-return valve which is designed as an inlet valve and which is opened during the tensioning process and closed during the fluid delivery process. Thus, the outlet valve is closed during the tensioning process and opened during the administration of the fluid.

[0006] Furthermore, the tensioning device can release the piston rod during an administration process when the piston is in its rear end position, so that the piston moves due to the pre-tensioning present against the first direction towards the open administration end and in this process the fluid in the cylinder is administered through the non-return valve for administration.

[0007] The tensioning device comprises a ramp which is rotatable by a motor and has a ramp path which extends along a helical line, wherein the ramp path ascends from a first platform along an inclined region to a second platform and descends from the second platform via a transition flank to the first platform, wherein the ramp path has a transition region which connects the second platform and the transition flank. Furthermore, the tensioning device can have a roller which is in contact with the ramp path and is rotatably mounted in a drive which is connected to the piston rod, so that, when the ramp is rotated in a first direction of rotation, the ramp path travels under the thus rotating roller. For a tensioning process, the ramp path can be rotated in the first direction of rotation so that the roller travels on the inclined region up to the second platform and the piston is thereby moved into its rear end position. For a dosing process, the tensioning device can rotate the ramp path in the first direction of rotation starting from the contact of the roller with the second platform until the roller travels on the transition region and accelerates towards the first platform due to the pretension, as a result of which the piston is moved towards the open dosing end.

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

[0009] According to the application, the motor can be connected to the ramp by a coupling, wherein, for the rotation of the ramp, the coupling transmits the torque provided by the motor in a first direction of rotation and, in the process, provides a freewheel / backlash in the opposite direction of rotation, wherein the freewheel / backlash is configured so that it covers at least a rotational angle range corresponding to the transition region.

[0010] The coupling can be designed so that the freewheel / backlash covers a rotational angle range which corresponds to no more than twice the transition region. The freewheel / backlash can in particular cover a rotational angle range which is 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80% or 90% larger than the transition region.

[0011] The coupling can have a first coupling part which is connected to the motor and a second coupling part which is connected to the ramp. One of the two coupling parts can have a protruding engagement element and the other of the two coupling parts can have a recess into which the engagement element protrudes. The engagement element can have a range in the first direction of rotation which is at least as large as a rotational angle range covering the transition region. The recess can have a range in the first direction of rotation which is larger than the range of the engagement element in the first direction of rotation, thereby providing the desired freewheel / backlash.

[0012] The spring can be arranged between a side surface of the engagement element and a side surface of the recess, which side surfaces face each other in the first direction of rotation. In particular, the spring can be arranged between all opposing side surfaces of the engagement element and the recess. The spring can be fixed on the engagement element.

[0013] The spring can be designed as a compression spring. In particular, the spring can be embodied as a disc spring.

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

[0015] The first coupling part can have the engagement element. Furthermore, the ramp body can comprise a base as a 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, which are spaced apart from each other in the first direction. The other of the two coupling parts can have a plurality of recesses, into which the engagement elements protrude. The range of each engagement element in the first direction of rotation is at least smaller than the range of the corresponding recess in the first direction of rotation by a rotational angle range covering the transition area.

[0017] According to the invention, the ramp path can extend on a front side of a wall extending along a circular path, wherein a cover plate is provided, which engages on the ramp path, the drive and the roller and has at least one scraper extending against the first direction, which extends within the wall up to the inner side of the wall in order to scrape lubricant located on the inner side off the inner side.

[0018] The cover can have a plurality of scrapers extending against the first direction and each extending within the wall in the direction of the inner side of the wall in order to scrape lubricant located on the inner side off the inner side, wherein the scrapers are spaced apart from each other in the first direction.

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

[0020] Furthermore, the range of the scrapers in the direction towards the inner side can differ.

[0021] One or more scrapers can be formed on a central portion of the frustoconical shape. In particular, the scrapers can extend radially from the central portion of the frustoconical shape. The central portion of the frustoconical shape can extend counter to the first direction. In particular, the central portion of the frustoconical shape can extend up to the base of the ramp.

[0022] The central portion can also have any other form. In particular, the central portion can be cylindrical.

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

[0024] In particular, for forming the joint, the end of the piston rod facing away from the piston can be rounded and movably mounted in the base.

[0025] The base can be formed on a connecting portion which presses against the rounded end of the piston rod by means of a screw which is screwed into the rounded end of the piston rod. The base can be formed by the curved sides of the washers (or leveling washers).

[0026] Furthermore, the joint can have two washers (or leveling washers) which are arranged above and below one another, and the mutually facing sides of the washers are curved, so that the washers move against one another during rotation of the piston rod. The two washers can be arranged on the side of the connecting portion facing away from the rounded end of the piston rod.

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

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

[0029] According to the application, the application device can have exactly one cylinder with exactly one piston and exactly one piston rod, wherein the tensioning device has two helical screws which extend parallel to one another, both of which contribute to the existing pretension when the piston is in its rear end position.

[0030] The two helical springs can be arranged spaced apart from one another in a direction transverse to their longitudinal direction and / or can have the same dimensions.

[0031] In particular, the helical springs can be arranged such that their longitudinal direction is parallel to the longitudinal direction of the piston rod.

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

[0033] The piston rod can be connected to the two guide rods by means of a connecting portion, wherein each guide rod extends within one of the helical springs.

[0034] The tensioning device can have at least three helical springs which extend parallel to one another. In particular, the helical springs can be arranged symmetrically with respect to the motor in a plane perpendicular to the longitudinal direction of the helical springs.

[0035] According to the application, a device for applying a fluid can comprise a front portion having a cylinder and an open application end and a rear portion having a tensioning device, wherein the front portion and the rear portion are formed from different materials.

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

[0037] The device can have a housing surrounding the front and the rear, wherein a part of the front protrudes from the housing.

[0038] According to the application, the device can comprise a dose setting device with a spacer and a moving unit, wherein the moving unit can move the spacer from an idle position (in which the spacer is not positioned between the driver and the cylinder) into a working position between the driver and the cylinder when the piston is in its rear end position, so that the driver is stopped by the spacer after the roller has passed the transition area, and thus the piston stroke during the movement of the piston towards the open dispensing end is shorter compared to the case where the spacer is in its idle position.

[0039] The spacer can have a threaded hole into which a threaded rod protrudes, wherein the threaded rod is rotated to move the spacer between its idle position and its working position.

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

[0041] The spacer can be designed in such a way that the roller does not come into contact with the spacer when the driver is stopped by the spacer.

[0042] The spacer can have a first and a second abutment area for the driver, wherein for the first abutment area the range of the spacer in the first direction is smaller compared to the second abutment area, and thus a different shortening of the piston stroke can be set depending on whether the first or the second abutment area is moved into the working position of the spacer.

[0043] Of course, the spacer can also have three or more abutment areas, wherein the range of the spacer in the first direction differs for the abutment areas, and thus a different shortening of the piston stroke can be set depending on the abutment area that is moved into the working position of the spacer.

[0044] According to the application, the device can have a control unit which carries out a measurement of a characteristic variable during the tensioning process and / or the dispensing process, and thereby determines whether the tensioning process and / or the dispensing process has been carried out correctly by comparison with at least one specified value. In particular, the measurement of the characteristic variable can be carried out during the dispensing process and the preceding tensioning process, and thereby it is determined whether both the tensioning process and the dispensing process have been completed by comparison with at least one specified value.

[0045] The current consumption of the motor, the acceleration acting on the application device and / or the sound (or noise; e.g. frequency spectrum, frequency, tone, energy and / or volume) can be measured as characteristic variable.

[0046] The desired time-domain curve of current consumption with a lower limit and an upper limit can be predefined as at least one specified value, wherein the control unit determines that the tensioning process is correct when the current consumption measured throughout the tensioning process is not less than the lower limit and not greater than the upper limit.

[0047] The time-domain desired curve of acceleration with an upper limit can be predefined as at least one specified value, wherein the control unit determines that the feeding process is correct when the acceleration measured throughout the feeding process is not greater than the upper limit.

[0048] The first upper desired frequency and the first lower desired frequency and / or the first upper desired amplitude and the first lower desired amplitude can be predefined as at least one specified value, wherein the control unit determines that the feeding process is correct when the main frequency of the measured spectrum is between the first upper desired frequency and the first lower desired frequency and / or the amplitude of the main frequency of the measured spectrum is between the first upper desired amplitude and the first lower desired amplitude.

[0049] The dominant frequency is understood here specifically as the frequency with the largest amplitude in the measured spectrum. The dominant frequency is usually the frequency that determines the pitch.

[0050] The first expected 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 the predetermined first expected main frequency. Furthermore, the first expected 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 predetermined first expected main frequency.

[0051] The first expected 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 the predetermined first expected principal amplitude. Furthermore, the first expected 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 predetermined first expected principal amplitude.

[0052] Furthermore, the second upper desired frequency and the second lower desired frequency and / or the second upper desired amplitude and the second lower desired amplitude can be predefined as at least one specified value, wherein the control unit determines that the feeding process is correct when the first-level frequency of the measured spectrum is between the second upper desired frequency and the second lower desired frequency and / or the amplitude of the first-level frequency of the measured spectrum is between the second upper desired amplitude and the second lower desired amplitude.

[0053] The first-order frequency is hereby understood in particular as the frequency that has the second highest amplitude in the measured spectrum and therefore has the highest amplitude after the main frequency.

[0054] The second desired 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 the predetermined first desired secondary frequency. Furthermore, the second desired 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 predetermined first desired secondary frequency.

[0055] The second expected 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% larger than the predetermined first expected secondary amplitude. Furthermore, the second expected 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 predetermined first expected secondary amplitude.

[0056] Of course, the second, third, fourth, and fifth secondary frequencies and / or other secondary frequencies (with smaller amplitudes in each case) can be measured in the same manner and considered for evaluating the feeding process.

[0057] The matching process is deemed correct when the dominant frequency of the measured spectrum is less than the desired frequency, and / or the amplitude of the dominant frequency of the measured spectrum is greater than the desired amplitude. The dominant frequency is hereby understood specifically as the frequency of the measured spectrum with the largest amplitude. The dominant frequency is typically the frequency that determines the pitch.

[0058] The duration of the tensioning process can be measured as a characteristic variable.

[0059] The first expected duration can be predefined as a specified value, wherein the control unit determines that the tensioning process is correct when the measured duration is greater than the first expected duration.

[0060] The second desired duration can be predefined as a specified value, wherein when the measured duration is less than the second desired duration, the control unit determines that the tensioning process is correct.

[0061] Furthermore, the rotation angle covered by the slope path along the first rotation direction during the tensioning process can be measured as a characteristic quantity.

[0062] The desired rotation angle can be predefined as a specified value, whereby the control unit determines that the tensioning process is correct when the measured covered rotation angle is greater than the desired rotation angle.

[0063] It should be understood that the above features and the features to be explained below can be used not only in the specified combinations, but also in other combinations or individually, without departing from the scope of the invention. Attached Figure Description

[0064] The invention will now be explained in more detail with reference to exemplary embodiments and the accompanying drawings, which also disclose features important to the invention. These exemplary embodiments are illustrative only and should not be construed as limiting. For example, the description of exemplary embodiments having multiple elements or components should not be construed as meaning that all of these elements or components are necessary for implementation. Rather, other exemplary embodiments may include alternative elements and components, fewer elements or components, or additional elements or components. Unless otherwise stated, elements or components of different exemplary embodiments may be combined with each other. Modifications and variations described with respect to one exemplary embodiment may also be applied to other exemplary embodiments. To avoid repetition, the same elements or corresponding elements in different drawings are denoted by the same reference numerals and will not be explained again. Wherein:

[0065] Figure 1 A perspective view of an exemplary embodiment of the application device 1 according to the present invention is shown.

[0066] Figure 2 A front view of the cylinder / piston assembly 10 of the application device 1 is shown.

[0067] Figure 3 The cylinder / piston assembly 10 is shown along... Figure 2 The sectional view of section line AA in the figure.

[0068] Figure 4 The cylinder / piston assembly 10 is shown along... Figure 3 The sectional view of section line BB in the diagram.

[0069] Figure 5 The cylinder / piston assembly 10 is shown along... Figure 4 A cross-sectional view of section line CC in the diagram.

[0070] Figure 6 An isometric view of the cylinder / piston assembly 10 is shown, wherein the assembly is tensioned and the piston is in its rear end position.

[0071] Figure 7 An isometric view of the cylinder / piston assembly 10 is shown, with the piston in its front-end position.

[0072] Figure 8 A diagram is shown to illustrate the outline of the slope path 41, in which the rotation angle α is plotted along the x-axis and the stroke of the piston rod 25 along the y-axis.

[0073] Figure 9 It shows that according to Figure 6 A cross-sectional view of the piston / cylinder assembly 10 in a tensioned state.

[0074] Figure 10 A front view of the piston / cylinder assembly 10 is shown, with the piston in its front-end position.

[0075] Figure 11 The piston / cylinder assembly 10 is shown along... Figure 10 The sectional view of section line DD in the diagram.

[0076] Figures 12A-12C A diagram is shown to illustrate the forces acting as the roller 40 travels toward the transition side 47 over the transition region 46.

[0077] Figure 13 A front view of the base 60 of the slope 42 is shown.

[0078] Figure 14 A perspective view of the connecting part 66, which is connected to the motor 51 for hinged rotation, is shown.

[0079] Figure 15 A side view of the connecting part 66 is shown.

[0080] Figure 16 The front view of the connecting part 66 is shown.

[0081] Figure 17 A front view of the connecting portion 66 inserted into the recess 61 of the base 60 is shown.

[0082] Figure 18 and 19 It shows that according to Figure 17 The diagram is used to explain the freewheel / idle travel provided by the connector 50.

[0083] Figure 20 A schematic front view showing the spatial arrangement of springs 32, 33 and motor 51 is shown.

[0084] Figure 21 A comparative diagram showing the arrangement of springs and motors in existing application devices is provided.

[0085] Figure 22 and Figure 23 Further views of another exemplary embodiment of the spatial arrangement of the spring and motor in the application device 1 according to the present invention are shown.

[0086] Figure 24 The diagram shows the front part 11 and the rear part 12 in the connected state.

[0087] Figure 25 The illustration shows the front part 11 and the rear part 12 in a non-connected state.

[0088] Figure 26 A magnified detail view of the dose setting device 36 is shown.

[0089] Figure 27A A perspective view of spacer 70 is shown.

[0090] Figure 27B A schematic diagram of another exemplary embodiment of the spacer 70 is shown.

[0091] Figure 27C A view of a spacer 70 according to another embodiment is shown.

[0092] Figure 27D Show along Figure 27C The sectional view of section line AA in the figure.

[0093] Figure 27E It shows that according to Figure 27C The illustration shows the spacer 70 in its working position.

[0094] Figure 27F A perspective view of the main axis is shown.

[0095] Figure 28 A perspective view of cover 35 is shown.

[0096] Figure 29 Showing the front view of cover 35.

[0097] Figure 30 Show along Figure 29 The sectional view of section line BB.

[0098] Figure 31 Show along Figure 29 The sectional view of section line AA.

[0099] Figure 32 Showing the front view of cover 31.

[0100] Figure 33 Show the edge of cover 35 Figure 32 A cross-sectional view of the section line CC.

[0101] Figure 34 An enlarged partial view of the front portion 11 together with a portion of the piston 26 and piston rod 25 is shown.

[0102] Figure 35A schematic cross-sectional view of the insert 96 for the nozzle 16 is shown.

[0103] Figure 36 A schematic cross-sectional view of piston rod 25, plate 28, guide rods 29 and 30, and springs 32 and 33 is shown.

[0104] Figure 37 It shows Figure 36 A magnified view of detail A.

[0105] Figure 38 and Figure 39 A graph showing the measured acceleration values ​​during the tensioning and feeding processes is presented.

[0106] Figure 40 and Figure 41 A graph showing the measured current consumption of motor 51 during the tensioning and feeding processes is presented. Detailed Implementation

[0107] exist Figure 1 In the exemplary embodiment shown, the device 1 for applying a fluid (e.g., a liquid) according to the present invention includes a housing 2 having a main body portion 3 and a handle portion 4. The handle portion 4 is designed so that a user can grip the device 1 by grasping the handle portion. Furthermore, the handle portion 4 has a trigger 5 for actuating the device. A dispensing area 6 is formed at the front end of the main body portion 3. Additionally, in the top region of the main body portion 3, the device 1 has an accessory 7, such as a hose or container, to which it can be connected. The fluid to be applied can be delivered through the hose. Similarly, the fluid to be applied can be held in the container.

[0108] At the end of the handle portion 4 that is away from the main body portion 3, the handle portion 4 transitions into the base portion 8, where, for example, the power source for the device 1 (e.g., a battery) can be housed.

[0109] In the exemplary embodiments described herein, the device 1 (also referred to as the application device 1) according to the invention is designed for needle-free application of a fluid into an animal. The application preferably involves intramuscular injection of the fluid; for example, the fluid may be a pharmaceutical product, a vaccine, etc.

[0110] The application device 1 has a cylinder / piston assembly 10, which is described in more detail below. Figure 3 and Figure 4 And it is self-filling, so that the movement of the piston toward the feeding area 6 causes the fluid to be discharged, and the opposite movement of the piston causes the cylinder to be filled with fluid for the next discharge process.

[0111] Figures 2-5The entire cylinder / piston assembly 10 without the housing 2 is shown. The cylinder / piston assembly 10 includes a front portion 11 and a rear portion 12 connected to the front portion. The front portion 11 includes a cylinder 13 for receiving fluid, the cylinder 13 having an open feeding end 14 in which a check valve 15 is located, fluidly connected to a nozzle 16. According to... Figure 34 The check valve 15 is clearly visible in the diagram, and it is designed to allow fluid to be supplied from the cylinder 13 through both the check valve 15 and the nozzle 16. It is impossible for air or liquid to be drawn in through the nozzle and check valve 15. The check valve 15 closes in this direction.

[0112] An accessory 7 is also formed at the front 11, in which a check valve 20 is placed. Figure 3 The check valve allows fluid connection from accessory 7 to cylinder 13 and prevents fluid connection in the opposite direction. Accessory 7 has a channel 21 that leads to cylinder 13 through a plurality of radial holes 22.

[0113] The other check valve 20 can therefore be referred to as the inlet valve and the check valve 15 can be referred to as the outlet valve.

[0114] A piston 26 is formed at the end of the piston rod 25 that points towards the open feeding end 14. The piston rod is guided within the cylinder body 13, wherein the piston 26... Figure 3 and Figure 4 In the cross-sectional view, it is located at its rear end. In this position, the cylinder 13 is filled with the fluid to be supplied.

[0115] The piston rod 25 points away from the open feeding end 14 towards the rear end 27 (in Figure 37 (Clearly shown in the diagram) A first guide rod 29 and a second guide rod 30, which extend parallel to each other and parallel to the piston rod 25, are connected by a plate 28, and the first and second guide rods are guided in the rear section 12. Figure 4 The ends of guide rods 29 and 30 that are away from plate 28 are connected to driver 31.

[0116] Additionally, each guide rod 29, 30 is provided with a compression spring 32, 33 (e.g., a helical spring), the front ends of which are supported on the plate 28, and their rear ends are supported on the stop 34 of the rear part 12. Figure 3 and Figure 4 The position of piston 26 is shown, and springs 32 and 33 are tensioned / compressed.

[0117] A cover 35 and a dose setting device 36 are provided at the rear end of the rear part 12. The cover and the dose setting device are configured according to... Figure 6The cylinder / piston assembly 10 is not shown in the isometric view so that the actuator 31 can be clearly identified. The actuator 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.

[0118] Roller 40 travels on slope path 41 of slope 42, which rotates below roller 40, wherein slope path 41 has a single revolution, especially as Figures 6-8 As shown.

[0119] exist Figure 8 In the diagram, the rotation angle α is plotted with reference to the pitch difference z in the longitudinal direction parallel to the piston rod 25. It is assumed that at a rotation angle α0 = 0°, there exists a minimum pitch height z0, and the piston 26 is therefore in the forward position, where the distance to the open feeding end 14 is minimized. This position of the piston 26 is, for example, based on... Figure 11 It is shown in the sectional view.

[0120] The slope path 41 has a lower platform 43 adjacent to an inclined region 44 that extends to an upper platform 45. The upper platform 45 is adjacent to a transition region 46, which incorporates a transition side 47 (rotation angle α1), which in turn leads to the first platform 43. The rotation angle range from α0 to α2 is therefore equal to 360°.

[0121] The transition side 47 is characterized by its almost vertical extension, as it extends from height z1 to height z0 at a rotation angle (α2 in this case). The transition region 46 is therefore the range of rotation angles from height z1, which continuously decreases from the upper platform 45 until reaching the rotation angle α2 (=transition side 47). Thus, the rotation angle range from α1 to α2 covers the transition region 46.

[0122] The slope 42 is connected to the motor 51 via the connector 50. Figure 3 Motor 51 in the first rotation direction 52 ( Figure 6 and 7 The ramp 42 rotates. If tensioned from the cylinder / piston assembly 10... Figure 6Starting at the position shown, motor 51 now causes ramp 42 to rotate further in the first rotational direction 52 (because the user has actuated trigger 5). Due to the tensioned compression springs 32 and 33 accelerating plate 28 in the direction toward the open dispensing end 14, roller 40 operates on transition region 46 and then descends along transition side 47 in the direction toward the lower platform 43. Consequently, piston rod 25, connected to plate 28, also moves toward the open dispensing end 14, and fluid contained in cylinder 13 is then discharged via check valve 15 and nozzle 16 for intramuscular injection into the animal. The dispensing device 1 is designed to allow fluid to safely pass through the skin and be administered to the muscle located beneath the skin. Piston 26 is then in its forward position, for example as... Figure 11 The cross-sectional view is shown in the figure. The feeding device 1 is preferably configured such that, in the front position of the piston 26, the drive 31 is supported on the rear end of the rear member 12, so that the rear end of the rear member 12 forms an abutment of the drive 31. In this position, a desired minimum distance remains between the roller 40 and the ramp path 41, so that the roller 40 does not reach the lower platform 43 of the ramp path 41. Therefore, it is possible to prevent the roller 40 from impacting the ramp path 41 at the end of the discharge process, which could damage the roller 40.

[0123] After the discharge process, the ramp 42 rotates again in the first rotation direction 52 by means of the motor 51, such that once the roller 40 contacts the ramp path 41 in the inclined area 44, further rotation has the effect that the actuator 31 moves away from the open feeding end 14 along the longitudinal direction of the piston rod 25, thereby re-tensioning the compression springs 32, 33 and reaching their maximum tension when the roller 40 reaches the upper platform 45. Due to the mechanical connection of the actuator 31 with the guide rods 29 and 30, the plate 28 and the piston rod 25, this movement of the actuator 31 has the effect that the piston rod 25 and, consequently the piston 26, also move away from the open feeding end in the cylinder 13, thus establishing a negative pressure. Once the established negative pressure is large enough to open the inlet valve 20, fluid is drawn into the cylinder 13 through the inlet valve 20 and the radial hole 22, so that the cylinder 13 is filled with fluid.

[0124] When the roller 40 (also referred to as a cam or roller) reaches the upper platform 45, the motor 51 stops, thereby tensioning the cylinder / piston assembly 10 and thus preparing the feeding device 1 for the next injection process, which can be done by actuating the trigger 5.

[0125] Plate 28, springs 32, 33, guide rods 29, 30, driver 31 with roller 40, and ramp 42 together with motor 51 and connector 50 form a tensioning device S for tensioning cylinder / piston assembly 10.

[0126] The application device 1 also includes a control unit 54 for controlling the motor 51 and all other electrical components of the device 1. Figure 3 A printed circuit board with a control unit 54 is shown.

[0127] As already described, in order to apply the fluid, from Figure 6 Starting from the rotational position of the slope 42 shown, the slope further rotates along the first rotational direction 52, causing the roller 40 to travel from the upper platform 45 through the transition area. 46, and then accelerates along the transition side (Sprungflanke) 47 toward the lower platform 53. However, difficulties arise when the roller travels over the transition area 46. Figures 12A-12C In addition to the tangential component Ft, tension springs 32 and 33 also have a component Fs perpendicular to the tangential component and include a component Fd pointing in the same direction as the force Fm of the motor used to rotate the ramp 42. As a result, the roller 40 traveling in the transition region 46 accelerates the rotation of the ramp 42 (in addition to the rotation caused by the motor 51). This adversely causes the motor 51 to act as a generator for this additional acceleration and generate voltage spikes, which may damage the control electronics of the control unit 54. Furthermore, the motor 51 thus acts as a brake, therefore producing an undesirable braking effect during the rotation of the ramp 42, thereby altering the pressure distribution in an undesirable manner during the application of the braking effect.

[0128] Therefore, the connector 50 is designed to transmit the torque provided by the motor 51 to rotate the ramp path 41 in the first rotation direction 52, while having a freewheel / idle stroke opposite to the first rotation direction 52. The freewheel / idle stroke is configured such that it at least covers the rotation angle range (from α1 to α2) corresponding to the transition region 46, for example, 7°.

[0129] To form the connector 50, a star-shaped recess 61 is formed in the base 60 of the slope 42. Figure 13 The star-shaped recess 61 includes a central portion 62 and four arms 63, which extend from the central portion and are spaced 90° apart from each other in the circumferential direction in each case. Figure 13 One of the arms 63 is schematically shown, with the side surfaces 64 and 65 of the arms 63 inclined relative to each other such that they form an angle β, which corresponds at least to the rotation angle of the transition region 46 and is therefore 7° here.

[0130] Furthermore, the connector 50 includes a connecting portion 66 that connects to the motor and has four walls 67 arranged in a star shape and spaced 90° apart from each other in the circumferential direction in each case. Springs 69 (here, disc springs) are arranged on each side surface 68 of each wall. Springs 69 are used to support movement and for damping. Figure 17 As shown in the front view, the star-shaped wall 67 of the connecting part 66 is inserted into the star-shaped recess 61 of the base 60 of the slope 42. If the torque is not transmitted through the connector 50, each wall 67 is centered in the corresponding arm 63 of the star-shaped recess 61 due to the spring 69.

[0131] If the roller 40 of motor 51 rotates along the first rotation direction 52, then the front side 68 viewed from the first rotation direction 52 abuts against the corresponding side 64 of each arm 63, such as Figure 18 As shown.

[0132] If, starting from the upper platform 45, the roller 40 moves over the transition region 46, the described spring force (here, component Fd) additionally accelerates the ramp 42 in the first rotational direction 52, so that, due to the set freewheel / idle stroke, the ramp 42 can rotate faster in the first rotational direction 52 than the coupling 66 connected to the motor 51. Figure 19 As shown, the freewheel / free travel stops once the rear surface 68 of the corresponding wall 67, viewed in the first rotational direction 52, abuts against the side surface 65 of the corresponding arm 63 of the star-shaped recess 61. Because the freewheel / free travel is configured to cover at least the entire transition area 46, once the freewheel / free travel occurs... Figure 19 Upon contact, the roller 40 moves across the entire transition region 46. The roller 40 can thus move freely along the transition side 47, and undesirable acceleration of the rotational motion of the motor 51 is reliably avoided as the roller travels over the transition region 46.

[0133] Figure 20 A schematic front view is shown, illustrating the spatial arrangement of springs 32 and 33 and motor 51. The two springs 32 and 33 are connected in parallel via plate 28, such that their spring stiffnesses (spring constants) are added together. Therefore, when piston 26 is in its rear position, the required force (spring force) can be provided, which is necessary to greatly accelerate piston 26 so that the supplied fluid can be applied within the muscle and into the animal's body. Simultaneously, the required structural space for the cylinder / piston assembly 10 can be kept small and compact. Figure 21 Compared to the illustration which uses only one spring 32' instead of two springs 32 and 33, this will allow for greater structural space in the corresponding cylinder / piston assembly 10', because the single spring must have a larger diameter to provide the same spring force.

[0134] Of course, two or more springs 32 and 33 can also be connected in parallel. From Figure 22 and Figure 23 As can be seen from the schematic diagram, for example, three or four springs 32, 33, 37 and optional 38 can be provided to achieve a compact structural form. Figure 22 and Figure 23 As shown, two or more springs (here, three or four springs) can preferably be arranged symmetrically with respect to the motor 51.

[0135] As already explained, the front part 11 and the rear part 12 are two independent parts that are connected to each other, which is in Figure 24 and Figure 25 This can also be clearly seen in the illustration.

[0136] The front part 11 and the rear part 12 are preferably formed of different materials. Because the front portion of the front part 11 protrudes from the outer casing 2... Figure 1 Therefore, a material with greater strength than the material of the rear section and / or with better medium stability than the material of the rear section 12 is selected for it.

[0137] The material of the front part 11 may therefore include titanium, steel or plastic (e.g., PEEK).

[0138] For the material of the rear part 12, it is particularly important to choose a material that is as lightweight as possible. Aluminum, magnesium, titanium, or plastic are preferred.

[0139] Especially Figure 26 and Figure 27A As can be seen in the enlarged detailed cross-sectional view, the dosage setting device 36 includes a spacer 70, a screw 71 screwed into the spacer 70, and the screw 71 is connected to the shaft 74 of the second motor 75 via first and second gears 72 and 73. The screw 71 is screwed into the spacer 70 (…). Figure 3 The threaded hole 76 is located in the spacer 70. Additionally, the spacer 70 includes two laterally projecting guide strips 77 and 78. Figure 27A Guide strips 77 and 78 are guided in guide grooves 79 of cover 35. Guide groove 79 can... Figure 28 This is best viewed from the center. Furthermore, the cover 35 includes an opening 80 through which the spacer 70 can move.

[0140] According to Figure 3 In the illustration, spacer 70 is in the neutral position, in which it does not affect roller 40 and therefore does not affect the return movement of drive 31 from upper platform 45 through transition region 46 along transition side 47 toward lower platform 43. In contrast, in Figure 26In the middle, the spacer 70 has moved to its working position, in which the spacer is positioned between the drive 31 and the rear end of the rear portion 12 in such a way that the spacer forms a stop for the drive 31. The spacer from Figure 3 The location shown is to Figure 26 The movement at the indicated position is generated by the rotation of axis 74, where, for example, a rightward rotation of axis 74 causes movement from... Figure 3 The location shown is to Figure 26 The movement of the position shown, and the leftward rotation of shaft 74, causes the opposite movement. Of course, the dosage setting device 36 can also be configured such that opposite directions of rotation cause the same movement. Importantly, the two gears 72 and 73, and thus shaft 74, can be rotated by means of the second motor 75 to convert the rotational movement into a translational movement of the spacer 70 perpendicular to the longitudinal direction of piston rod 25. Therefore, the spacer 70 can move back and forth between its working position and its neutral position.

[0141] If spacer 70 is now in Figure 26 In the working position shown, after the roller 40 passes through the transition region 46, the movement of the actuator 31 in the longitudinal direction of the piston rod 25 is shortened because the movement ends when the actuator 31 abuts against the spacer 70. The extent of the spacer 70 in the longitudinal direction of the piston rod 25 thus corresponds to the shortening of the piston stroke during the application of fluid located in the cylinder 13. Therefore, a smaller amount of fluid can be discharged, resulting in the application of two different doses (here, for example, 2 ml and 1 ml) using the application device 1. If the roller 40 is on the upper platform 45, all that is needed to change the dose is to move the spacer 70 into the upper platform 45. Figure 26 The working position is shown.

[0142] The spacer 70 is designed so that the roller 40 does not contact the spacer 70 when the drive 31 is abutting against it. This prevents the roller 40 from being damaged by the spacer 70 when the drive 31 stops.

[0143] As already described, use according to Figure 27A The spacer described allows for the setting of a single, smaller dose. Figure 27B A variation of the spacer 70 is shown, wherein the spacer 70 has a first abutting region 140A and abutting region 141A, the first abutting region 140A and the second abutting region 141A are along a first direction ( Figure 27BThe range (Ausdehnung) from left to right is different, thus allowing for two different smaller doses. Since this range corresponds to a reduction in the stroke of piston 26 during administration, two different dose reductions are possible. A first reduction in piston stroke occurs if the spacer 70 retracts to the extent that the drive 31 is stopped by portion 140A during administration. Conversely, a second reduction in piston stroke occurs if the spacer 70 retracts to the extent that the drive 31 rests against region 141A during administration, a reduction greater than the reduction through portion 140A. This stepped design of the spacer 70 thus allows for two different dose reductions.

[0144] In the simplest case, to move the spacer 70 between its neutral and working positions, the motor 75 is activated within a predetermined time, during which time the motor rotates the screw 71. For example, corresponding abutments / stops can be provided for the working and neutral positions, against which the spacer moves. A potential disadvantage here is that the screw 71 may get stuck in the threaded hole 76, and the motor 75 may not provide sufficient force or torque to rotate the spacer 70 and prevent it from getting stuck when it moves in the other direction.

[0145] Therefore, according to another embodiment (which is in Figure 27C As shown in the figure, the spacer 70 may have a through hole 140 with smooth sidewalls instead of a threaded hole 76, such as Figure 27D The cross-sectional view shown in the figure illustrates the cross-sectional view based on Figure 27C The spacer 70 has a cross-section AA. Additionally, a spring-preloaded pusher 141 (or spring-preloaded pin 141) is provided, such as... Figure 27D As shown in the cross-sectional view, the pusher engages in the spindle thread 142 of the spindle 143 (which is configured to replace the screw 71).

[0146] The spring-loaded pin 141 is designed to press against the spindle thread 142.

[0147] The spindle thread 142 is designed to pass into corresponding straight grooves 144 and 145 at both ends. The difference between the straight grooves 144 and 145 is that they do not have a pitch / helical rise, but always have the same height when viewed in the longitudinal direction of the spindle 143.

[0148] Because the pusher 141 engages in the spindle thread 142, rotation of the spindle 143 causes the spacer 70 to move up or down (i.e., back and forth between the neutral and working positions). If the end of the spindle thread 142 is reached, the pusher 141 enters the corresponding straight grooves 144, 145, thus preventing further axial movement of the spacer 70. Only the spindle 143 rotates further.

[0149] The straight grooves 144 and 145 are preferably designed such that their depth is less than that of the spindle thread 142.

[0150] If the rotation direction of the spindle 143 is reversed, the pusher 141 (due to spring preload) reliably falls into the deeper spindle thread 142, so the spacer 70 moves in the opposite direction until the pusher 141 engages in another straight groove 145, 144, and thus further rotation of the spindle 143 will not cause any further axial movement.

[0151] In this way, it is possible to reliably prevent the spindle 143 from getting stuck in the spacer 70. Furthermore, simple motor start / control is possible because the motor 75 only needs to be started in such a way that it drives the spindle 143 for a sufficiently long time. Based on the corresponding straight grooves 144, 145, freewheeling / free-running is ensured, thus allowing further rotation of the spindle 143 without causing axial movement of the spacer 70 during this process.

[0152] Spindle 143 can be referred to as a spindle with freewheel / free-running.

[0153] For example in Figure 28 As can be clearly seen, cover 35 includes first, second, and third scrapers 80, 81, and 82, which are based on... Figure 3 In its assembled state, it extends from the rear end of the cover 35 in the direction toward the dispensing end of the application device 1. For example, in Figure 28 As can be seen, scrapers 80-82 are formed on the truncated conical central portion 83 and are spaced apart from each other in the circumferential direction. Figure 3 As shown, the truncated conical central portion 83 gradually tapers in the direction toward the feeding end.

[0154] In the assembled state, the truncated conical central portion 83 extends to the base 60 of the slope 41. Similarly, the first scraper 80 extends to the base 60. The first scraper 80 extends radially to the inner side 84 of the wall 85, where a slope path 42 is formed on the end / front surface of the wall. Figure 6 ).

[0155] The second scraper 81 is shorter than the first scraper 80 in both the axial and radial directions. Similarly, the third scraper 82 is shorter than the second scraper 81 in both the radial and axial directions.

[0156] Furthermore, the cover 35 includes an intermediate wall 86 in which an axially extending groove is formed, within which the roller 40, together with the retaining portion of the drive 31, can move axially. Additionally, in the assembled state, the intermediate wall 86, together with the lower cover portion 88, surrounds the outer side 89 of the wall 85. A lubricant (e.g., grease) is provided in the remaining space between the cover 35 and the wall 85, allowing the roller 40 to rotate as smoothly as possible and be guided with minimal friction along the ramp path 41. With the aid of scrapers 80-82, due to the relative movement between the ramp 41 and the scrapers 80-82, grease not remaining on the ramp 41 is moved again along the ramp and roller 40, thus ensuring permanent lubrication. The lubricant accumulated at the bottom of the cover 35 is therefore re-delivered to the ramp path 41 and roller 40, thus ensuring the required permanent lubrication.

[0157] Figure 34 This is an enlarged cross-sectional view showing the front portion 11 together with the piston 26 and part of the piston rod 25. The cylinder body 13 has an annular groove 90 in its rear region (away from the open feeding end 14). An O-ring 91 or a sealing ring 91 (e.g., an elastomeric seal) is inserted for sealing purposes. Furthermore, first and second support rings (92, 93) are arranged in the recess 90 such that the sealing ring 91 is located between the two support rings 92 and 93. The groove 90 and the support rings 92 and 93 are sized such that the gap between the support rings 92 and 93 and the piston rod 25 is smaller than the gap between the inner side of the cylinder body 13 and the piston rod 25. The support rings, made of polytetrafluoroethylene or other plastics, reliably prevent a portion of the sealing ring 91 from being squeezed into the gap between the piston rod 25 and the inner side of the cylinder body 13 due to pressure or negative pressure generated during the movement of the piston rod 95 (which would damage the sealing ring 91).

[0158] The second support ring 93 prevents the described gap squeezing during the movement of the piston rod 25 toward the open dispensing end 14 and thus during the application of fluid. The first support ring 92 prevents undesirable gap squeezing during reverse movement and thus during the filling of the cylinder 13 with fluid.

[0159] like Figure 34 As can be seen, the nozzle 16 has a tapered through-hole 95 through which the fluid is supplied during application. The required through-hole 95 can also be formed in the insert 96, such as... Figure 35As shown, the insert is then screwed into the remaining main nozzle body 97. The insert 96 includes a base 98 with external threads, which includes a receiving region 99 at a distal end. A sapphire element 100 is inserted into the receiving region 99, the final portion of which forms a through-hole 95. From Figure 35 As can be seen in the illustration, the diameter of the final portion of the through-hole 95 is the smallest or smaller than the diameter of those portions of the through-hole 95 formed in the substrate 98. This advantageously achieves the effect that the very small diameter required for the through-hole 95 can be reliably manufactured at its distal end, because this portion of the through-hole 95 in the sapphire element 100 can be manufactured with greater precision than the hole in the metal substrate 98. The diameter of the final portion of the through-hole 95 in the sapphire element 100 can be, for example, in the range of 0.30 to 0.38 mm, with the intention of manufacturing a tolerance of no more than 0.02 mm.

[0160] Because the unit consisting of piston rod 26, plate 28, and guide rods 29 and 30 is relatively long and exerts a large force during fluid application, it is essential to ensure that piston rod 26 can move freely within cylinder 13, and, for example, without tilting. For this purpose, piston rod 26 should be oriented, for example, as parallel as possible to guide rods 29 and 30, and this orientation should be maintained throughout the long term of use of the application device 1.

[0161] The piston rod 25 is therefore not absolutely rigidly connected to the plate 28. The connection is configured such that the piston rod 26 can tilt, rotate, or be positioned relative to the plate 28. The piston rod 25 is therefore connected to the plate 28 via a swivel joint. Figure 36 and Figure 39 As shown in the diagram, a first washer 110 is disposed between the rear end 27 of the piston rod 25 and the plate 28. Furthermore, a retaining screw 111, extending through a corresponding hole in the plate 28, is screwed into the rear end 27. Second and third washers 113 and 114 are arranged between the heads 112 of the retaining screw 111. To provide the required rotatability, the rear end 27 is circular (here, for example, spherical), and the side of the first washer 110 facing the rear end 27 is correspondingly recessed, forming a receiving portion for the rear end 27. Figure 37 As shown in the diagram, the first washer 110 is located in the recess of the plate 28, preventing it from moving laterally relative 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 because the bottom of the corresponding recess in the plate 28 is also flat. Therefore, the first washer can also be described as a plano-concave shape.

[0162] The second and third washers 113 and 114 are designed with their facing sides also curved. In this case, the side of the second washer 113 facing the third washer 114 has a convex curve. The side of the third washer 114 opposite to the second washer 113 has a concave curve accordingly. The other side of the second and third washers 113 and 114 is flat. The head 112 of the retaining screw 111 presses the third washer 114 onto the second washer 113, thereby pressing the second washer 113 onto the side of the plate 28 away from the rear end 27. Therefore, the second washer 113 is plano-convex, while the third washer 114 is plano-concave.

[0163] By selecting the dimensions and curvature, the rotation point 115 for the piston rod 25 to rotate relative to the plate 28 is spaced apart from the plate 28 and is on one side of the screw head 112.

[0164] Since the described connection allows the piston rod 25 to rotate relative to the plate 28, it can be ensured that the piston rod 25 can always move within the cylinder 13 without being wedged in.

[0165] Motor 51 can be designed as an electric motor, and in particular as a brushless electric motor. The durability of the application device 1 is thus improved, because in the case of a brushed motor, there may be a difficulty that the brush may break due to vibrations that occur during fluid application.

[0166] In order to identify in Figure 3 A sensor 55 is provided to indicate whether there is fluid in the cylinder 13 at the position of piston 26, which, in the exemplary embodiment described herein, is positioned upstream of another check valve 20 (also referred to as an inlet valve). Sensor 55 can, for example, distinguish between air and liquid, thereby preventing the application device 1 from performing the application process when there is no liquid in the cylinder 13. Damage to the application device 1 can thus be prevented because the application device is configured to inhibit the movement of the piston rod 25 or piston 26 toward the open dispensing end during application. If there is no liquid in the cylinder 13, this inhibition function is omitted, potentially resulting in mechanical damage to, for example, the piston rod 25, the connection between the piston rod 25 and plate 28, or guide rods 29, 30. Sensor 55 can be designed as a voltage sensor, a capacitive sensor, or, for example, a light barrier.

[0167] The outer casing 2 may have a light-emitting area 120 that can emit light in different colors. Figure 1The area 120 can be, for example, a strip or any other form. Different colors can be used to share user information about the status of the application device 1. For example, a first color (e.g., red) can be used to share with the user that the device 1 is not yet ready for use. A second color can be used to share that the device is essentially ready for use. A third color can be used to indicate that the cylinder / piston device 10 is tensioned and that the application process can be performed by actuation of the trigger 5. A fourth color (e.g., green) can be used to share with the user that the application process was successful. In addition, other colors can be used to share with the user the presence of an error state. Of course, the information described can not only be shared by different colors, but also by the same color if the difference is represented by, for example, flashing in different ways. Furthermore, tactile or acoustic feedback can be provided to the user instead of the visual feedback described above. Of course, visual, tactile, and auditory feedback can also be combined.

[0168] Furthermore, the application device 1 may have an acceleration sensor 130, which is only an example in... Figure 3 As shown in the diagram. Since the measured acceleration values ​​from a correctly applied procedure differ from those from those from an incorrectly applied procedure, the success of the application can be determined based on the measurements. Figure 38 In the diagram, the measured acceleration values ​​for a successful application are plotted over time along the x-axis (in milliseconds) and along the y-axis (in units of g, which is the acceleration due to gravity). The measured acceleration values ​​are represented by points connected by a line. The test curve is shown as a dashed line. If the acceleration value is lower than the value on the test curve, the application is considered successful.

[0169] Figure 39 An example of an unsuccessful administration procedure (hereinafter also referred to as an injection (Schuss)) is shown. The acceleration value exceeded the maximum value of the test curve, so it should be assumed to be an unsuccessful injection.

[0170] In addition, the current consumption of motor 51 can be measured and evaluated to assess the quality of the injection.

[0171] Figure 40 The measured current consumption during the feeding and injection process of the application device 1 is shown, with the measured current value in A (= Amperes) shown as a point connected by a line. The current values ​​are plotted along the y-axis (and in milliseconds along the x-axis in terms of time). The feeding and injection process is considered successful if the measured current value is less than the upper limit curve and greater than the lower limit curve (both curves are represented by dashed lines).

[0172] If the injection is unsuccessful, the measured current value will be outside the range defined by the two limit curves, such as... Figure 41 As shown. In this case, the application process was unsuccessful.

[0173] Instead of or in addition to the accelerometer 130, a sensor 131 may be provided for measuring sound or tone (e.g., a microphone), in which sensor 131 is... Figure 3 The diagram illustrates this schematically. For example, the success of the application process can be determined based on the pitch during the application process. If the measured pitch time curve is, for example, above a predetermined upper limit or the upper limit time curve, the application process is evaluated as unsuccessful. The measured pitch time curve may also fall below, for example, the lower limit time curve, which can lead to the conclusion that the application process is incorrect. For example, the measured spectrum can also be evaluated as a characteristic variable, which must execute the desired time curve for the application process to be evaluated as successful. In the same way, the intensity (or volume) time curve can be used as a characteristic variable, which in turn must execute the desired time curve.

[0174] Of course, multiple described characteristic variables can be used to evaluate the application process. For example, the feeding process alone, the tensioning process alone, or both the tensioning and feeding processes can be measured and evaluated.

[0175] The control unit 54 can perform the described measurements and evaluations of the characteristic variables to determine whether the application process was successful. Depending on the determination process, the control unit can generate visual, tactile, and / or auditory feedback, for example, in the described manner.

Claims

1. A device for administering a fluid, comprising: a cylinder (13) having an open dispensing end (14), a piston (26) movable within the cylinder (13) between a front end position and a rear end position and connected to a piston rod (25) projecting in a first direction from a rear end of the cylinder (13) opposite the open dispensing end (14), a check valve (15) closing the open dispensing end, and a tensioning device (S) connected to the piston rod (25), wherein the tensioning device (S) is capable of moving the piston rod (25) in the first direction during a tensioning process until the piston (26) is in its rear end position, thereby filling the cylinder (13) with the fluid to be administered and pre-tensioning the piston rod (25) towards the open dispensing end (14), and wherein the tensioning device (S) is capable of releasing the piston rod (25) during a dispensing process when the piston (26) is in its rear end position, so that the piston (26) moves against the first direction due to the pre-tensioning force present and in the process the fluid in the cylinder (13) is dispensed through the check valve (15) for administration, the tensioning device (S) having a ramp (42) with a ramp path (41) extending along a helix, wherein the ramp path (41) rises from a first plateau (43) along a ramp region (44) to a second plateau (45) and descends from the second plateau (45) via a transition flank (47) to the first plateau (43), wherein the ramp path has a transition region (46) connecting the second plateau (45) and the transition flank (47), wherein the tensioning device (S) further has a roller (40) in contact with the ramp path (41), which is rotatably mounted in a drive (31) connected to the piston rod (25), so that the ramp path (41) travels underneath the roller (40) rotating thereby when the ramp (42) is rotated in a first rotational direction (52), wherein for the tensioning process the ramp path (41) is rotated in the first rotational direction (52) so that the roller (40) travels over the ramp region (44) up to the second plateau (45), so that the piston (26) moves to its rear end position, wherein for the dispensing process the ramp path (41) is rotated in the first rotational direction (52) starting from the contact of the roller (40) with the second plateau (45) until the roller (40) travels over the transition region (46) and accelerates towards the first plateau (43) due to the pre-tensioning, so that the piston (26) moves towards the open dispensing end (14), wherein a dose setting device (36) is provided, which comprises a spacer (70) and a movement unit, wherein the movement unit is capable of moving the spacer (70) from a neutral position in which the spacer (70) is not between the drive (31) and the cylinder (13) into a working position between the drive (31) and the cylinder (13) when the piston (26) is in its rear end position, such that the drive (31) is stopped by the spacer (70) after the roller (40) has passed the transition area (46), so that the piston stroke during the movement of the piston (26) towards the open dispensing end is shorter compared to the case in which the spacer (70) is in its neutral position wherein the spacer (70) has a through hole (140) in which a spindle (143) with a spindle thread (142) is guided, wherein the spacer (70) has a pin (141) which projects into the spindle thread (142), and wherein the spindle thread (142) opens into a recess (144, 145) at at least one of its two ends.

2. The device of claim 1, wherein the spindle thread (142) opens into a recess (144, 145) at both of its ends.

3. The device of claim 1, wherein, the recess (144, 145) has a depth which is smaller than the depth of the spindle thread (142).

4. The device of claim 2, wherein the recess (144, 145) has a depth which is smaller than the depth of the spindle thread (142).

5. The device of claim 1, wherein the spindle thread (142) is a single start thread.

6. The device of claim 2, wherein the spindle thread (142) is a single start thread.

7. The device of claim 1, wherein the spindle thread (142) is a multi start thread.

8. The device of claim 2, wherein the spindle thread (142) is a multi start thread.

9. The device of claim 1, wherein the pin (141) is designed as a spring preloaded pin (141).

10. The device of claim 1, wherein the spindle thread (142) is rotated by a motor (51) of the movement unit to move the spacer (70) between its neutral position and its working position.

11. The device of claim 1, wherein, the spacer (70) is guided in such a way that it can only move in a plane which is perpendicular to the piston rod (25).

12. The device of claim 1, wherein the spacer (70) is designed in such a way that the roller (40) does not come into contact with the spacer (70) when the drive (31) is stopped by the spacer (70).

13. The device of claim 1, wherein The spacer (70) has a first abutment area (140A) and a second abutment area (141A) for the driver (31), wherein the range of the spacer (70) in the first direction is smaller for the first abutment area (140A) compared to the second abutment area (141A), so that different shortening of the piston stroke can be set depending on whether the first or the second abutment area (140A, 141A) is moved into the working position of the spacer (70).

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