EP4166786A1 - Peristaltic pump - Google Patents

Abstract

A hose pump (100) contains a housing (1) containing a hose track (2) for supporting a hose (5) and a rotary body (15), the rotary body (15) having a plurality of displacement bodies (10) for temporarily squeezing the hose (5) in the hose track (2). The hose (5) is designed to hold a fluid. The tubular track (2) contains an inlet-side tubular track section (21), an outlet-side tubular track section (23) and a central tubular track section (22) arranged between the inlet-side tubular track section (21) and the outflow-side tubular track section (23). The middle tubular track section (22) has a curvature. At least one of the inlet-side and outlet-side tubular track sections (21, 23) has a first and second tubular track segment. At least one of the inlet-side or outlet-side tube track sections contains a curved tube track section (24, 25). An occlusion angle (y) is formed between a starting point (12) of an occlusion and an end point (13) of the occlusion, the occlusion angle (γ) corresponding to the angle (52) that two adjacent displacement bodies (10) enclose to one another.

Description

The present invention relates to a hose pump.

Peristaltic pumps are used for pumping tasks in the fields of medicine, laboratories and production. One of its great advantages is that the working area is formed by a flexible hose and apart from the inner hose wall, no other elements of the hose pump come into contact with the fluid to be pumped. The media are transported by occlusion by means of one or more displacement bodies in the form of rotating rollers or sliding blocks at at least one point on the tube and displacement of this occlusion in the conveying direction.

The occlusion occurs through a periodic reduction of the tube volume by the displacement body(s) rolling on the tube and pressing on the tube. The occlusion is thus caused by the hose being squeezed, which is made possible by the flexible material from which such hoses are usually made. The occlusion is followed by an increase in the tube volume when the displacement body moves away from the tube again. The change in the hose volume results in pulsating flow rates both on the inlet side of the hose pump and on the outlet side of the hose pump.

Such pulsating flow rates are undesirable for many applications. Especially when dosing or mixing, pulsating flow rates are undesirable because, for example, the dosing quantity or the mixing ratio cannot be precisely adjusted.

State of the art

Various measures have been taken in the past to reduce pulsating flow rates. On the one hand, the number of rollers is increased, which reduces pulsation somewhat, but significantly reduces hose life. Other options for reducing pulsating flow rates are in EP 2 419 636 B1 , DE20109803 U1 , EP 3 364 032 A1 , EP 2 990 647 A1 described.

In the document EP 2 419 636 B1 also describes a method for pulsation-free volumetric delivery, which, however, leads to a complex and expensive linear peristaltic finger pump.

Therefore, there is a need for an improved peristaltic pump by which a substantially pulsation-free flow rate is obtainable.

object of the invention

The object of the invention is to provide a peristaltic pump whose throughput is essentially constant.

Description of the invention

The object of the invention is achieved by a hose pump according to claim 1. Advantageous exemplary embodiments of the hose pump are the subject matter of claims 2 to 15.

When the term "for example" is used in the following description, this term refers to exemplary embodiments and/or embodiments, which is not necessarily to be construed as a more preferred application of the teachings of the invention. Similarly, the terms "preferably", "preferred" should be understood as referring to one example from a set of exemplary embodiments and/or embodiments, which should not necessarily be construed as a preferred application of the teachings of the invention. Accordingly, the terms "for example," "preferably," or "preferred" may refer to a plurality of exemplary embodiments and/or embodiments.

The following detailed description contains various exemplary embodiments of the hose pump according to the invention. The description of a specific peristaltic pump is to be considered as an example only. In the specification and claims, the terms "include", "comprise", "have" are interpreted as "including but not limited to".

A fluid can include a liquid or gaseous medium, which can also contain solid particles. The fluid can be in a single-phase or multi-phase state, ie it can be liquid, gaseous or in the form of an emulsion, a foam or a slurry.

A hose pump according to the invention contains a housing containing a hose track for supporting a hose and a rotating body containing a plurality of displacement bodies for temporarily squeezing the hose in the hose track, the hose being designed to hold a fluid. The fluid can flow through the hose; in particular, the fluid can be conveyed through the hose from the inlet end to the outlet end of the hose pump in the operating state.

The tubular track contains an inflow-side tubular track section, an outflow-side tubular track section and a central tubular track section arranged between the inflow-side and outflow-side tubular track sections. The middle tubular track section has a curvature. A plane containing the central axis of the tubular track is referred to below as the tubular track plane. The curvature runs in the hose track plane. The curvature can in particular be in the form of an arc of a circle. At least one of the inlet-side and outlet-side tubular track sections is adjoined by a curved inlet-side or a curved outlet-side tubular track section. An occlusion angle γ is formed between a starting point of an occlusion and an end point of the occlusion, the occlusion angle γ corresponding to the angle that two adjacent displacement bodies form with respect to one another. The angle between the two adjacent displacers is measured in particular between the respective central axes containing the displacers. The central axis runs between the center of rotation of the displacement body and the center of rotation of the rotary body. The center of rotation of the rotating body is the intersection of the axis of rotation of the rotating body with the plane of rotation in which the rotating bodies move.

According to one embodiment, the displacement body hits the hose at a starting point of the hose deformation. In particular, the distance between the displacement body and the tube path can decrease from the starting point of the tube deformation as the rotating body continues to rotate, so that the tube is increasingly squeezed until the starting point of an occlusion is reached. The starting point of the occlusion is reached when a cavity formed by the hose has disappeared as a result of the hose being squeezed by the displacement body. In particular, a deformation angle α is formed between the starting point of the tube deformation and the starting point of the occlusion. In particular, the deformation angle α can correspond to the angle between two adjacent displacement bodies.

According to one exemplary embodiment, the starting point of the hose deformation is arranged in the curved hose track section on the inlet side. According to one exemplary embodiment, the starting point of the occlusion is arranged in the inflow-side tubular track section.

According to one exemplary embodiment, the end point of the occlusion is reached when a cavity is created by relieving the pressure on the hose by increasing the distance between the hose track and the displacement body. In particular, an end point of an occlusion can be formed when a cavity is created by relieving the load on the hose by increasing the distance between the hose track and the displacement body.

According to one exemplary embodiment, a hose deformation end point is formed when the displacement body lifts off the hose. In particular, the displacement body can lift off the hose at an end point of the hose deformation, in other words the displacement body loses contact with the hose at the end point of the hose deformation.

In particular, a deformation angle β is formed between the end point of the occlusion and the end point of the tube deformation. In particular, the deformation angle β can correspond to the angle between two adjacent displacement bodies.

According to one embodiment, at least one of the curved inlet-side tubular track sections or the curved outlet-side tubular track sections can be obtained by a measurement specification, by means of which the tubular track can be determined over a plurality of heights H _i , which correspond to a constant volume given a constant change in angle Δα. If at least one of the curved inlet-side hose track sections or the curved outlet-side hose track sections is determined experimentally or arithmetically by means of a simulation using the measurement specification, a substantially constant volume flow can be conveyed by means of the hose pump.

According to one exemplary embodiment, a curved tubular track section on the inflow side is arranged upstream of the inflow-side tubular track section. According to one exemplary embodiment, a curved hose track section on the discharge side is arranged downstream of the hose track section on the outlet side.

According to one exemplary embodiment, at least one of the curved inlet-side and the curved outlet-side tubular track sections has a variable radius of curvature. In particular, the curvature of the curved hose track section on the inlet side can differ at least partially from the curvature of the curved hose track section on the outlet side. In particular, at least one of the hose track sections on the inlet side and the hose track sections on the outlet side can have a curvature. In particular, the curvature of the tube track section on the inlet side can differ at least partially from the curvature of the tube track section on the outlet side.

According to one exemplary embodiment, the displacement bodies are arranged on the rotary body in such a way that they execute a circular movement when the rotary body rotates. According to one embodiment, the displacement bodies are rotatably mounted in the rotary body.

According to one exemplary embodiment, the rotating body contains a plurality of rotating body arms, with the displacement bodies being arranged on the rotating body arms of a rotating body. In particular, the tubular track is arranged in the tubular track plane, with the rotating body being rotatable about an axis of rotation which is oriented vertically in relation to the tubular track plane.

According to one embodiment, the displacement bodies are rotatably mounted on the rotating body arms. In particular, a bearing point in the rotary body arm forms a rotary pole for the relevant displacement body. In particular, the bearing point can be designed in such a way that it has no springing, ie the distance L between the pivot point of the axis of rotation of the rotary body and the rotary pole of the displacement body remains constant. This design has the particular advantage that the hose is always subjected to the same pressure. An elastic bearing can possibly have disadvantages if fluids containing lumps are conveyed and such lumps in the fluid are undesirable. If the bearing point is elastic, the displacement body can be pushed away by the lump in such a way that the hollow space in the tube opens at a location where the tube should be closed. The fluid can therefore be pumped and the volume flow can be changed, which can result in inaccurate dosing. A resilient mounting of the displacement body is not desirable when using the peristaltic pump in the laboratory, since such a solution only makes sense if dispersions with large particles have to be transported, which does not happen in the laboratory. Such a resilient mounting is therefore unnecessarily complicated for use in the laboratory and can also complicate the slow lifting of the displacement body for pulse compensation.

If the bearing point is located at a constant distance L from the pivot point, i.e. the point at which the axis of rotation intersects with the plane of the hose track, the hose can be replaced without the need for additional adjustment of the rotating body or the individual displacement bodies. In other words, the displacement bodies are connected to the rotary body in such a way that they perform a circular movement when the rotary body rotates. According to this exemplary embodiment, the rotary body has a bearing point that is stationary with respect to the rotary body for each displacement body.

According to one embodiment, a delivery chamber can be formed when two adjacent displacement bodies are located at the starting point and end point of the occlusion or between the starting point and end point. In particular, the fluid cannot leave the pumping chamber as long as the hose is closed by two adjacent displacement bodies. In particular, a pumping chamber can only be formed if the angle between the starting point of the occlusion and the end point of the occlusion corresponds to the angle that two adjacent displacement bodies form with respect to one another and the two angles overlap. In other words, the pumping chamber can only be formed if the distance between two adjacent displacement bodies corresponds to the distance between the starting point and the end point of the occlusion, i.e. one of the displacement bodies is at the starting point of the occlusion and the adjacent displacement body downstream is itself located at the end point of the occlusion.

In particular, the tube can only be closed by a displacement body if two adjacent displacement bodies are not arranged at the starting point and end point of the occlusion. This means that no pumping chamber is formed in any other position of the displacement bodies. Thus, the volume of fluid displaced corresponds to the volume of fluid sucked back. This means that the pulse that occurs when the pumping chamber is opened results in the same volume being displaced as was is sucked back. In this case, therefore, there is no change in the total volume flow, because the displaced and sucked-back volume flows cancel each other out. Consequently, a constant volume flow can be achieved by means of the hose pump according to this exemplary embodiment.

The conveying direction through the peristaltic pump can also be selected as desired. In particular, the conveying direction can be reversed by changing the direction of rotation of the rotary body. Advantageously, at least one hose holding device can be provided in order to prevent the hose from performing a migratory movement in the pumping direction. The hose holding device can include a clamping device in order to fix the hose in its position in the conveying direction. The hose aging device can comprise a spring element in order to release the clamping device when the direction of rotation of the rotary body is reversed, ie the conveying direction is changed. In particular, a hose holding device can be formed at the inlet end and at the outlet end of the hose, that is to say at the pump inlet and at the pump outlet. On the one hand, the hose holding devices allow the hose to be fixed at the inlet end if the hose is essentially fixed in its position by means of the clamping device, and on the other hand an extension of the hose at the outlet end in order to prevent the hose from being compressed when the clamping device is released. Pulsations in each conveying direction can be effectively prevented by means of such a hose holding device. In addition, the service life of the hose can be increased.

In particular, the hose holding device on the suction side can create itself by the hose movement in the housing of the hose pump in the direction of the pressure side and clamp the hose. On the pressure side, the hose holding device can lift off due to the hose movement toward the pressure side and allow a hose movement toward the pressure side, which prevents the hose from jamming in the region of the hose track sections on the outlet side. This enables a particularly simple reversal of the direction of rotation of the peristaltic pump, since no further measures are necessary due to the autonomous switching of the clamping devices of the hose holding devices, in particular no intervention by a user who would have to actuate an actuator in order to activate the hose holding device.

Brief description of the drawings

• Fig. 1 eine vorbekannte Schlauchpumpe,
• Fig. 2 eine Darstellung des Volumenstroms der Schlauchpumpe gemäss Fig. 1 in Abhängigkeit von der Zeit,
• Fig. 3a ein Ausführungsbeispiel einer Schlauchpumpe gemäss der vorliegenden Erfindung in einer ersten Stellung,
• Fig. 3b das Ausführungsbeispiel gemäss Fig. 3a in einer zweiten Stellung,
• Fig. 4a einen Querschnitt einer Schlauchbahn und eines zugehörigen Verdrängungskörpers nach einem ersten Ausführungsbeispiel,
• Fig. 4b einen Querschnitt einer Schlauchbahn und eines zugehörigen Verdrängungskörpers nach einem zweiten Ausführungsbeispiel,
• Fig. 4c einen Querschnitt einer Schlauchbahn und eines zugehörigen Verdrängungskörpers nach einem dritten Ausführungsbeispiel,
• Fig. 4d einen Querschnitt einer Schlauchbahn und eines zugehörigen Verdrängungskörpers nach einem vierten Ausführungsbeispiel,
• Fig. 5a ein Detail einer Schlauchalterungsvorrichtung in Klemmstellung,
• Fig. 5b ein Detail der Schlauchhalterungsvorrichtung in Freilaufstellung,
• Fig. 6 eine schematische Darstellung eines Ausführungsbeispiels einer Messvorrichtung,
• Fig. 7a ein exemplarisches Beispiel für Messdaten, die mittels der Messvorrichtung gemäss
• Fig. 6 erhalten werden können,
• Fig. 7b eine Grafik eines Messresultats, erhalten mit den Messdaten gemäss Fig. 7a,
• Fig. 8 ein Schema zur Ermittlung der Schlauchbahn der Schlauchpumpe.

The hose pump according to the invention is presented below using a few exemplary embodiments. Show it

• 1 a previously known peristaltic pump,
• 2 a representation of the volume flow of the peristaltic pump according to 1 depending on the time
• Figure 3a an embodiment of a peristaltic pump according to the present invention in a first position,
• Figure 3b the embodiment according to Figure 3a in a second position
• Figure 4a a cross section of a tubular track and an associated displacement body according to a first embodiment,
• Figure 4b a cross section of a tubular track and an associated displacement body according to a second embodiment,
• Figure 4c a cross section of a tubular track and an associated displacement body according to a third embodiment,
• Figure 4d a cross section of a tubular track and an associated displacement body according to a fourth embodiment,
• Figure 5a a detail of a hose aging device in the clamped position,
• Figure 5b a detail of the hose holding device in free running position,
• 6 a schematic representation of an embodiment of a measuring device,
• Figure 7a an exemplary example of measurement data by means of the measuring device according to
• 6 can be obtained
• Figure 7b a graphic of a measurement result obtained with the measurement data according to Figure 7a ,
• 8 a scheme for determining the hose track of the peristaltic pump.

Detailed description of the drawings

1 shows a hose pump 50 comprising a housing 1 containing a hose track 2 for supporting a hose 5 and a plurality of displacement bodies 10. The Displacement bodies 10 are arranged on rotating body arms 16 of a rotating body 15 which can be rotated about an axis of rotation 9 which is oriented vertically in relation to the central plane of the hose track. In the present illustration, the central plane of the hose track corresponds to the plane of the drawing. The displacement bodies 10 can be designed, for example, as rollers or sliding shoes. The displacement bodies 10 can be rotatably mounted on the rotary body arms 16 . If the displacement bodies 10 are rotatably mounted on the rotary body arms 16 , the bearing point of the displacement body 10 in the rotary body arm 16 forms the rotary pole 17 for the displacement body 10 in question. The direction of rotation of the rotating body 15 about the axis of rotation 9 is indicated schematically with an arrow 8 . In the present illustration, the axis of rotation 9 runs at a right angle to the plane of the drawing, so the axis of rotation 9 is in 1 shown as a pivot.

The rotary poles 17 of the displacement bodies 10 lie on a circle whose center is formed by the axis of rotation 9 . The displacement bodies 10 form rotationally symmetrical bodies when they can be rotated about the rotary pole 17 . The maximum diameter of the displacement body 10 characterizes the maximum extension of the displacement body 10 in the central plane of the hose track. If the displacement body 10 is designed as a cylinder, the maximum diameter corresponds to the diameter of the cylinder. Each of the displacement bodies 10 has the same maximum diameter. The displacement bodies 10 thus span an enveloping circle whose radius R _HK corresponds to the distance L of the rotary pole 17 from the axis of rotation 9 plus the radius Rv of the displacement body 10 . The maximum diameter is therefore twice the maximum radius Rv.

The tubular track 2 contains different tubular track sections according to FIG 1 an inlet-side tubular track section 21, a central tubular track section 22 and an outlet-side tubular track section 23. The inlet-side tubular track section 21 and the outflow-side tubular track section 23 are formed by a straight line lying in the plane of the tubular track. The middle tubular track section 22 is formed by a curved track. According to the present exemplary embodiment, the curved path is designed as part of a circular path. The circle of this circular path also has its center at the pivot point 9. The radius RK of the circle of the circular path is larger than the radius RHK of the enveloping circle HK. In particular, the difference between the radius RK and the radius RHK is essentially twice the wall thickness of the hose 5 if the hose 5 is not excessively squeezed, ie pressed in this way that the wall thickness of the hose in the pressing area is reduced compared to the original wall thickness.

The hose 5 contains an inflow end 6 and an outflow end 7, the inflow end 6 forming the pump inlet and the outflow end 7 forming the pump outlet. The hose 5 rests on the hose track 2 . As soon as the enveloping circle HK intersects the tube 5, one of the displacement bodies 10 comes into contact with the tube 5. This point of intersection will be referred to below as the starting point 11 of the tube deformation. Since the tube 5 is designed as a hollow body, the outer diameter of the tube 5 corresponds to the diameter of the hollow body plus twice the wall thickness of the tube 5 when the hollow body is not subjected to any deformation. The displacement body 10 moves on the circular path formed by the enveloping circle HK.

From the starting point 11 of the tube deformation, the displacement body 10 moves on and there is an increasing deformation of the tube 5 until the tube walls rest on one another and the hollow body has disappeared. This condition is called occlusion. In the occlusion state, there is no fluid between the tube walls lying on top of one another. The deformation of the tube 5 increases until the starting point 12 of the occlusion is reached. At the starting point 12 of the occlusion, the difference between the radius R _K and the radius R _HK is essentially twice the wall thickness of the hose in the middle plane of the hose web or less if the hose is additionally pressed, so that the wall thickness of the hose in the pressing area is reduced. This difference remains constant as long as the displacement body moves along the middle hose track section 22 .

In the inlet-side tubular track section 21, the distance between the displacement body 10 and the tubular track 2 decreases, so that the tube volume is reduced, with the tube 5 being increasingly squeezed. The displacement body 10 dives according to 1 increasingly into the tube 5. Since in most peristaltic pumps 50 the contact surface of the hose 5 in the hose track 2 of the housing 1 is straight in this inlet-side hose track section 21 and tangential to the next, central hose track section 22, the duration of the squeezing process until occlusion is relatively short in relation to the total pumping time. The during the duration of the squeezing process in the hose 5 displaced volume of the fluid to be pumped against the direction of flow, since in the direction of flow Tube is closed from the starting point 12 of the occlusion. For this reason, during the squeezing process, there is a smaller conveying volume in the hose in the feed-side hose track section. This results in a pulsation of the volume flow in the hose track section on the inlet side. In 2 this state is shown as a valley-shaped indentation in the volume flow curve 41 .

A delivery chamber 3 is formed between two adjacent displacement bodies 10 in the middle section 22 of the tubular track, which chamber contains a volume of fluid that is conveyed from the inlet end 6 to the outlet end 7 by the rotational movement of the displacement bodies 10 .

In the central hose track section 22, the hose is occluded by the displacement bodies 10 and the transported volume in the conveying chamber 3 is defined by the angle that two adjacent rotary body arms 16 enclose to one another. According to the present exemplary embodiment, the rotary body arms are each arranged at an angle of 60 degrees to one another. In order to ensure tightness of the peristaltic pump, the angle enclosed by the circular segment of the middle tubular track section 22 is greater than the angle between two adjacent displacement bodies 1 about 90 degrees.

In the hose track section 23 on the outlet side, the distance between the displacement body 10 and the hose track 2 increases, so that the hose volume increases. The squeezing of the tube 5 is reversed, the tube 5 can resume its original shape as soon as the displacement body 10 is no longer in contact with the tube 5 . The displacement body 10 emerges from the tube volume. Since in most peristaltic pumps the contact surface of the hose in the hose track is straight and tangential to the preceding, central hose track section 22 in this area, the duration of the return process until it is completed is relatively small in relation to the total pumping time. For this reason, there is a smaller conveying volume in the hose 5 in the hose track section on the outlet side for the duration of the resetting process. In other words, the cumulative ascent time becomes relatively small in relation to the total pumping time. The volume of fluid to be pumped out of the tube during the emergence period is sucked back against the direction of flow, since the tube is occluded against the direction of flow. For this reason, there is thus during the reset process, ie during the surfacing period, a smaller delivery volume in the hose 5 in the hose track section 23 on the outlet side. This creates a pulsation of the volume flow in the hose track section 23 on the outlet side.

2 shows the effect of the pulsation on the volume flow, represented by the volume flow curve 41, which is obtained with a peristaltic pump according to FIG 1 is promoted and a pulsation-free volume flow, which with a peristaltic pump according to 3a or 3b is conveyed, represented by the volume flow curve 42. The time is plotted on the abscissa and the volume flow, which is conveyed with the corresponding peristaltic pump, is plotted on the ordinate.

Figure 3a 10 shows a hose pump 100 according to an exemplary embodiment of the invention. Figure 3b shows the hose pump 100 according to FIG Figure 3a at a later time. A pulsation reduction can be achieved by means of the peristaltic pump 100, so that, surprisingly, a substantially constant volume flow can be supplied and/or conveyed. Identical parts or parts with the same function have the same reference numbers in order to compare them with the previously known hose pump 50 according to FIG 1 to facilitate. If the tube dimensions and the dimensions of the rotary body 15 and the displacement body of the tube pump 100 correspond to the tube pump 50, the pumped volume of the tube pump 100 corresponds to the pumped volume of the tube pump 50 at the same speed. In other words, the area under the volume flow curve 41 corresponds to the area under the volume flow curve 42. The fluid to be pumped is guided through a hose 5 of the hose pump 100, which runs on an inlet-side hose path section 21, 24, a middle hose path section 22 and an outlet-side hose path section 23 , 25 of a hose track 2 located in the housing 1 rests.

The hose pump 100 comprises a housing 1 containing a hose track 2 for supporting a hose 5 and a plurality of displacement bodies 10. The displacement bodies 10 are arranged on rotating body arms 16 of a rotating body 15 which can be rotated about an axis of rotation 9 which is vertical in relation to the Hose track center plane is aligned. In the present illustration, the central plane of the hose track corresponds to the plane of the drawing. The displacement bodies 10 can be designed, for example, as rollers or sliding shoes. The displacement bodies 10 can be rotatably mounted on the rotary body arms 16 . When the displacement body 10 is rotatable on the Rotating body arms 16 are mounted, the bearing point of the displacement body 10 in the rotating body arm 16 forms the rotary pole 17 for the displacement body 10 in question. The direction of rotation of the rotating body 15 about the axis of rotation 9 is indicated schematically with an arrow 8 . In the present illustration, the axis of rotation 9 runs at a right angle to the plane of the drawing, so the axis of rotation 9 is in 1 shown as a pivot.

The rotary poles 17 of the displacement bodies 10 lie on a circle whose center is formed by the axis of rotation 9 . The displacement bodies 10 form rotationally symmetrical bodies when they can be rotated about the rotary pole 17 . The maximum diameter of the displacement body 10 characterizes the maximum extension of the displacement body 10 in the central plane of the hose track. If the displacement body 10 is designed as a cylinder, the maximum diameter corresponds to the diameter of the cylinder. Each of the displacement bodies 10 has the same maximum diameter. The displacement bodies thus span an enveloping circle HK, the radius R _HK of which corresponds to the distance L of the rotary pole 17 from the axis of rotation 9 plus the radius Rv of the displacement body 10 . The maximum diameter is therefore twice the maximum radius Rv.

The tubular track 2 contains different tubular track sections according to FIG Figure 3a an upstream hose path portion 21, an upstream curved path portion 24, an intermediate path portion 22, a downstream path portion 23, and a curved outgoing path path portion 25. The intermediate path portion 22 is formed by a curved path. According to the present exemplary embodiment, the curved path is designed as part of a circular path. The circle of this circular path also has its center at the pivot point 9. The radius R _K of the circle of the circular path is larger than the radius R _HK of the enveloping circle. In particular, the difference between the radius R _K and the radius R _HK is essentially twice the wall thickness of the hose. In particular, the tube 5 can be squeezed under pressure, in which case the sum of the wall thicknesses of the two tube sections lying one above the other is less than twice the wall thickness. The deviation from twice the wall thickness can be in the range of 0.1 mm to 1 mm.

The curved upstream-side hose path section 24 is connected to the upstream-side hose path section 21 and is located upstream of the upstream-side hose path section 21 with respect to the direction of flow of the fluid. The curved one The downstream hose path section 25 adjoins the downstream hose path section 23 and is located downstream of the downstream hose path section 23 with respect to the flow direction of the fluid.

The hose 5 contains an inflow end 6 and an outflow end 7, the inflow end 6 forming the pump inlet and the outflow end 7 forming the pump outlet. The tube 5 rests on the tube sheet 2 when the tube sheet 2 is formed as a flat surface or a convex surface, or in the tube sheet when the tube sheet is formed by a concave surface. Figures 4a, 4b, 4c and 4d show possible variants for a hose track 2 and associated displacement body 10. A hose holding device 4, 26 can be provided to prevent the hose 5 from slipping in the hose track 2 or to prevent the hose 5 from being compressed in the hose track. In particular, the hose holding device 4, 26 can be equipped with a clamping device 29 for the hose 5, which is Figures 5a and 5b is shown. In particular, the hose holding device 4 can be attached to the housing 1 in the area of the inlet end. A further hose holding device 26 can be attached to the housing 1 in the area of the outlet end 7, which can have the same structure as the hose aging device 4, but is arranged in a mirror-inverted manner.

As soon as the enveloping circle HK intersects the tube 5, one of the displacement bodies 10 comes into contact with the tube 5. This point of intersection will be referred to below as the starting point 11 of the tube deformation. Since the hose 5 is designed as a hollow body, the outer diameter of the hose corresponds to the diameter of the hollow body plus twice the wall thickness of the hose when the hollow body is not subjected to any deformation. For hoses with a non-circular cross-section, the outer contour of the hose is used instead of the term outer diameter. The displacement body 10 moves on the circular path formed by the enveloping circle HK.

From the starting point 11 of the tube deformation, the displacement body 10 moves on and there is an increasing deformation of the tube 5 until the tube walls rest on one another and the hollow body has disappeared. This condition is called occlusion. In the occlusion state, there is no fluid between the tube walls lying on top of one another. The deformation of the tube 5 increases until the starting point 12 of the occlusion is reached. At the starting point 12 of the occlusion, the difference between the radius R _K and the radius R _HK is essentially double Wall thickness of the hose in the middle plane of the hose track. In particular, the tube 5 can be squeezed under pressure, in which case the sum of the wall thicknesses of the two tube sections lying one above the other is less than twice the wall thickness. The deviation from twice the wall thickness can be in the range of 0.1 mm to 1 mm.

This difference remains constant as long as the displacement body 10 moves along the central tubular path section 22 .

The distance between the displacement body 10 and the hose path 2 decreases in the curved hose path section 24 on the inlet side and in the hose path section 21 on the inlet side, so that the hose volume is reduced, with the hose 5 being increasingly squeezed. The displacement body 10 dives according to Figure 3a increasingly into the tube 5. The contact surface of the tube 5 in the tube track 2 of the housing 1 already increases in the curved inlet-side tube track section 24 and continues to increase in the inflow-side tube track section 21 and is arranged tangentially to the next, middle tube track section 22, whereby the duration of the squeezing process up to the occlusion in relation to the Total pumping time according to compared to the previously described embodiment 1 is significantly enlarged. In particular, the radius of curvature of the hose track section 21 on the inlet side can be at least partially larger than the radius of curvature of the curved hose track section 24 on the inlet side. The radii of curvature of the curved hose track section 24 on the inlet side and/or of the hose track section 21 on the inlet side can be variable.

The volume of fluid to be pumped that is displaced in the tube 5 during the squeezing process is thus not pumped against the direction of flow, since the tube is closed in the direction of flow only from the starting point 12 of the occlusion. For this reason, there is no or at least no significantly smaller delivery volume in hose 5 in the curved inlet-side hose track section 24 and in the inlet-side hose track section 21 during the duration of the squeezing process. This means that there is no pulsation or at least no noticeable pulsation of the volume flow in the curved inlet-side hose track section 24 and in the inlet-side tubular track section 21. In 2 the volume flow curve 42 is therefore shown with a constant progression over time.

In order to avoid pulsations as completely as possible, it is therefore important that the duration of the squeezing process is equal to the total pumping time. In particular, it is advantageous if the tube 5 is permanently and continuously in a squeezing phase. As soon as a displacement body 10 has completed the squeezing of the tube 5 and has thus occluded the tube, the subsequent displacement body 10 must start squeezing according to this exemplary embodiment, so that the formation of pulsations can be avoided as far as possible. According to this particularly advantageous exemplary embodiment, the deformation angle α from the beginning of the pinching of the hose 5 to the occlusion is essentially equal to the angle 52 between two displacement bodies 10 that follow one another. This means that the angle between the starting point 11 of the hose deformation and the starting point 12 of the occlusion corresponds at least the angle between two adjacent displacement bodies 10.

A delivery chamber 3 is formed between two adjacent displacement bodies 10 in the middle section 22 of the tubular track, which chamber contains a volume of fluid that is conveyed from the inlet end 6 to the outlet end 7 by the rotational movement of the displacement bodies 10 . In the central hose track section 22, the hose 5 is occluded by the displacement body 10 squeezing the hose and the transported volume in the conveying chamber 3 is defined by the angle 52, which two adjacent rotary body arms 16 enclose to one another. According to the present exemplary embodiment, the rotary body arms 16 are each arranged at an angle of 60 degrees to one another. The angle enclosed by the circular segment of the central tubular track section 22 corresponds to the angle between two adjacent displacement bodies 10, it is in Figure 3a about 60 degrees.

In the hose track section 23 on the outlet side and in the curved hose track section 25 on the outlet side, the distance between the displacement body 10 and the hose track 2 increases, so that the hose volume increases. The squeezing of the tube 5 is reversed, the tube 5 can resume its original shape as soon as the displacement body 10 is no longer in contact with the tube 5 . The displacement body 10 emerges from the tube volume.

The bearing surface of the hose 5 in the hose track 2 of the housing 1 already decreases again in the hose track section 23 on the outlet side and continues to decrease in the curved hose track section 25 on the outlet side.

The duration of the restoring process from the occlusion to the deformation-free hose 5 is significantly increased in relation to the total pumping time in comparison to the previously described embodiment according to FIG 1 . In particular, pulsations can be avoided if the duration of the reset process is equal to the total pump duration. The tube 5 must be permanently and continuously in a recovery phase. As soon as one of the displacement bodies 10 has finished squeezing the hose and the hose 5 is therefore free, the subsequent displacement body 10 must begin the reset process. Thus, the angle from the start of the return process of the hose 5 until the hose 5 is completely released is at least equal to the angle between two displacement bodies 10 following one another, ie two adjacent displacement bodies 10. The release of the hose 5 means that the displacement body 10 releases the hose 5 just left untouched.

The volume of fluid to be pumped that is in the tube 5 during the reset process is therefore not pumped against the flow direction, since the tube 5 is closed against the flow direction up to the end point 13 of the occlusion.

The rotation of the displacement body 10 about the axis of rotation 9 promotes a volume flow from the inlet end 6 to the outlet end 7 of the hose 5 in the central hose path section 22, which corresponds approximately to: ω(PHK + D _hose /2) A _{inner hose} . ω denotes the angular velocity of the rotation in the axis of rotation 9, D _hose /2 half the outer diameter of the hose 5, and A _{inner hose} the inner cross-sectional area of the hose 5. This calculated volume flow corresponds to the maximum of the volume flow 41 in 2 , ie the highest point in the graph that curve 41 ever reaches. The resetting process of the displacement bodies 10 from the hose 5 in the hose track section 23 on the outlet side and in the curved hose track section 25 on the outlet side counteracts this volume flow. Thus, the volume flow calculated above is reduced by the amount of the volume change per unit of time, ie the volume flow, of the hose 5 in the outlet-side hose path section 23 and in the curved outlet-side hose path section 25 by the resetting of the displacement bodies 10 . This results in a continuous and constant return flow for the hose pump according to the invention, which must be subtracted from the volume flow calculated above and the maximum achievable volume flow in the central hose track section 22 . This creates a constant volume flow, which corresponds to the volume flow curve 42 in 2 corresponds and which is conveyed by the hose pump 100 according to the invention.

For this reason, the delivery volume does not decrease, or at least not significantly, during the duration of the resetting process in the hose track section 23 on the outlet side and in the curved hose track section 25 on the outlet side. In other words, the cumulative ascent time becomes relatively large in relation to the total pumping time. Surprisingly, the volume of fluid to be pumped out of the tube 5 that is required during the ascent is not sucked back in the direction of flow, since the tube 5 is occluded against the direction of flow. For this reason, there is no smaller delivery volume in the hose 5 in the outlet-side hose track section 23 during the reset process, i.e. during the emergence period, so that the delivery volume remains constant or essentially constant. There is no pulsation of the volume flow in the hose path section 23 on the outlet side or in the curved hose path section 25 on the outlet side due to the relationships described above. The fluid therefore leaves the hose pump 100 at the outlet end 7 essentially without pulsation.

According to an exemplary embodiment that is not shown, either only the inlet-side hose track section 21 or the outlet-side hose track section 23 according to FIG 1 according to 3a or 3b be modified such that either only a curved upstream tube track section 24 is provided when reduced pulsation is required at the pump inlet, or only a curved downstream tube track section 25 is provided when reduced pulsation is required at the pump outlet.

According to 3a or 3b the occlusion angle γ in the central tubular track section 22 corresponds to the angle 52 between two adjacent displacement bodies 10. This adjusts the penetration/emergence duration of each displacement body 10 so that at the end of the penetration/emergence process of this displacement body, the penetration/emergence -Process of the next sinker starts. A continuous penetration/emergence process thus occurs in the inlet-side tubular track section 21 , in the curved inlet-side tubular track section 24 and/or in the outlet-side tubular track section 23 , in the curved outlet-side tubular track section 25 . In particular, by selecting the radius of curvature or the course of the curvature, the contact surface of the hose 5 in the hose track 2 can be adjusted in such a way that a constant volume displacement or Volume back suction occurs. In particular, a pulse with a constant volume flow can be generated, which ends when the next pulse starts. If a constant volume flow is overlaid with a constant volume flow pulse that restarts as soon as the previous one ends, this results in a constant volume flow at the pump inlet and/or at the pump outlet.

Figure 4a shows a cross section of a tubular track 2 and an associated displacement body 10 according to a first embodiment. According to this exemplary embodiment, the displacement body 10 is designed as a cylinder. The tubular track 2 has a flat course. A pinched hose 5 is located between the displacement body 10 and the hose track 2 in the housing 1.

Figure 4b shows a cross section of a tubular track 2 and an associated displacement body 10 according to a second embodiment. According to this exemplary embodiment, the displacement body 10 is designed as a rotationally symmetrical body with convex side surfaces. The tube sheet 2 is formed as a concave surface. A pinched hose 5 is located between the displacement body 10 and the hose track 2 in the housing 1.

Figure 4c shows a cross section of a tubular track 2 and an associated displacement body 10 according to a third embodiment. According to this exemplary embodiment, the displacement body 10 is designed as a rotationally symmetrical body with concave side faces. The tube sheet 2 is formed as a convex surface. A pinched hose 5 is located between the displacement body 10 and the hose track 2 in the housing 1.

Figure 4d shows a cross section of a tubular track 2 and an associated displacement body 10 according to a fourth embodiment. According to this exemplary embodiment, the displacement body 10 is designed as a rotationally symmetrical body with concave side surfaces. The tube sheet 2 is formed as a concave surface. A pinched hose 5 is located between the displacement body 10 and the hose track 2 in the housing 1. This variant can ensure a particularly gentle pumping process, for example, this variant is used when fluids that contain biological material, such as cells, have to be pumped.

Figures 5a and 5b show the hose holding device 4 in detail. The hose aging device 26 has the same design, it is arranged mirror-inverted in relation to the hose holding device 4 . According to Figures 5a and 5b the hose 5, of which only a small part is shown, is guided through an opening in the housing 1. The hose is guided from the opening in the housing 1 on the hose track 2 in the interior of the housing 1 . If the conveying direction of the fluid is in Figure 5a takes place in the direction of the arrow shown, ie the rotary body moves as in 3a or 3b is moved clockwise, the contact of the tube 5 with the clamping device 29 by the friction of the tube in the contact area of the housing 1 and the clamping device 29 prevents the tube from being displaced. Tensile forces are transmitted to the tube 5 by the displacement bodies, so that the tube 5 would be drawn into the tube track 4 if the tube holding device 4 did not contain a clamping device 29 .

The hose holding device 4 is held in the housing 1 by means of a fastening element 28 . The hose holding device 4 can be arranged so as to be rotatable about the fastening element 28 . The fastening element 28 can be designed as a bolt, for example. According to the present exemplary embodiment, a first arm element 31 and a second arm element 32 extend from the fastening element 28 in essentially opposite spatial directions. The first arm element 31 contains a spring element 27. The second arm element 32 contains the clamping device 29. The spring element 27 is supported on a wall of the housing 1. FIG. The clamping force acting on the hose 5 via the clamping device 29 can thus be increased and/or adjusted by means of the spring element 27 . The spring element 27 can be designed, for example, as a spring clip that is held in the first arm element 31 . The second arm element 32 contains a channel which at least partially surrounds the hose 5 and in which the hose 5 rests on the second arm element 32 . The second arm element 32 comprises a stop 30 which bears against the housing in order to hold the hose holding device 4 in the position shown in Figure 5a to fix the position shown.

In Figure 5b the tube holding device 4 is shown in a position that it can assume when the conveying direction with respect to FIG Figure 5a is reversed, as indicated by the arrow in Figure 5b shown. In this position, which is also referred to below as the free-running position, compression of the hose at the outlet end is prevented. For example, by means of the hose holder device 4, the hose 5 at Hose extension in the pressure direction, according to the in Figure 5b arrow shown, are released by the pumping process, so that the hose 5 cannot accumulate when the displacement body 10 relieves the hose 5 from the end point of the occlusion and moves away from the hose 5 again at the end point of the hose deformation.

Especially with a slow leading of the displacement body 10 to the hose 5 and a subsequent lifting of the hose 5, the

Hose holding device 4 and the hose holding device 26 have surprising advantages. For example, by means of the hose holder device 26, the hose 5 can be fixed in the pressure direction when the hose is extended, according to the Figure 5a shown arrow are released by the pumping process, so that the hose 5 can not accumulate when the displacement body 10 relieves the hose 5 from the end point of the occlusion 13 and moves away from the hose 5 again at the end point of the hose deformation 14 . By using the hose holding devices 4, 26, not only unwanted pulsations, but also destruction of the hose 5 can be avoided. In particular, each of the hose holding devices 4, 26 can contain a spring element 27, so that the holding force or the force for relieving the pressure on the hose can be adjusted depending on the fluid to be pumped, the nature of the hose 5 and the dimensions of the hose track 2 or the displacement body 10 can.

When the clamping device 29 of the hose holding device 4, 26 is in the clamping position, the hose 5 is prevented from being able to migrate in the flow direction of the fluid when the displacement bodies 10 transport the fluid in the corresponding flow direction in this configuration. In the Figure 5a The hose holding device 26 (not shown) is in the freewheeling position and allows the hose 5 to exit the housing 1 if it moves in the direction of the discharge end 7 despite the clamping device of the hose holding device 4 being in the clamping position, so that the hose 5 is not jammed or compressed , when the displacement bodies 10 lift off from the hose 5. This state is in Figure 5b for the hose holding device 4 for the reference Figure 5a reverse pumping direction shown.

According to Figures 5a, 5b contain the tube mounting devices 4, 26 each have a spring element so that they press the tube 5 slightly. The The hose holding device 4 can be drawn completely towards the housing 1 by the initial displacement of the hose 5 in the pumping direction and by the friction between the outer wall of the hose and the clamping device 29 . The use of a spring element 27 for the clamping device 29 also allows a change in the direction of rotation of the rotary body 15, with the hose holding devices 4, 26 automatically adjusting so that no manual intervention is required. In the event of a change in direction of the fluid to be pumped, the hose pump 100 is therefore automatically switched over. In particular, the clamping device of the hose aging device 4 rests against the housing 1 and brakes the hose 4. The clamping device of the hose holding device 26 is lifted out of the housing 1 by the displacement of the hose 5 when the pumping direction of the fluid to be pumped changes from that in Figure 5a corresponds to the direction of the arrow shown.

6 shows a measuring device 51 for determining the hose path for a hose 5 of a hose pump 50, 100 according to one of the preceding exemplary embodiments. The measuring device includes a base 57 which serves as a support for the tube 5 . A roller 58 is arranged above the base and has a bracket 59 which is slidably arranged in relation to a stationary guide element 52 . The guide element 52 can be connected to the base 57, which is not shown in the drawing. A measuring transducer 60 is arranged on the holder 59, by means of which the displacement path of the roller 58 in the holder 59 can be determined. The measuring sensor 60 can be designed as a micrometer screw, for example.

The tube 5 is filled with a liquid, such as water, alcohol. According to the present exemplary embodiment, the hose 5 is adjoined by a measuring hose 55 which forms a common fluid chamber with the hose 5 . The tube 5 is connected to the measurement tube 55 via a transition element 61 . In other words, a first end of the hose 5 ends in the transition element 61. The second end of the hose 5 can be closed by means of a closure element 56.

A measurement with the measuring device is carried out as follows:
The hose 5 and the measuring hose 55 connected to the hose are closed at the second end 5 by means of the closure element 56 . The tube 5 is laid down on the base 57 and the roller 58 is moved by moving the holder 59 in the guide element 52 in such a way that the roller 58 touches the tube 5 . According to the 6 Measuring device 51 shown, the roller 58 is lowered for this purpose, the displacement of Holder 59 in the guide element 52 takes place in the vertical direction. When the roller 58 touches the tube 5, the level of the liquid in the measuring tube 55 is measured. In addition, the position of the roller 58 is determined by means of the measuring transducer 60 when the roller 58 touches the hose 5.

The roller 58 is then shifted until a specific change in the level ΔN of the liquid in the measuring hose 55 is reached, see also Figure 7b . The corresponding position of the roller 58 is again determined with the measuring sensor. This measurement is repeated with a constant value for ΔN until the tube is occluded, in other words until the tube is pinched in such a way that it is closed. For each level change, the corresponding position of the roller 58 is determined by the sensor. Figure 7a shows a table for ΔN= 20 mm. According to this exemplary embodiment, the level of the liquid N rises from 30 mm to 250 mm. The distance of the roller from the base 57 decreases, in which in Figure 7a shown in the table as height H.

Figure 7b 12 shows the variation in height H as a function of the variation in the level of the liquid in the measuring tube 55, the level of the liquid N being plotted on the ordinate and the height H of the roller 58 on the abscissa. Out of Figure 7b it can be seen that the decrease in height H is not linear.

A method for determining a hose web 2 for a hose 5 for a hose pump 50, 100 comprises the following steps: the hose 5 is filled with a fluid, the hose 5 being closed at a second, lower end, the hose being closed at a first , upper end is provided with a measuring tube 55 for measuring a level of the fluid, or a mathematical model is created in which a roller 58 is displaced relative to the tube 5 along a path such that the tube 5 is increasingly squeezed by the roller 58, whereby the fluid in the hose 5 is displaced. A sensor for measuring the travel distance is provided, the travel distance being determined when the level change in the measuring tube 55 increases step by step by a constant value.

If the change in level is constant, the associated hose track can be determined from the measured distances for a constant delivery flow of the hose pump. The distance covered thus correlates with the hose path of the hose pump as follows.

The roller, which corresponds to the displacement body 10 of the hose pump, strikes the hose 5 at a starting point 11 of a hose deformation. The distance between the displacement body 10 and the hose track 2 from the starting point 11 of the hose deformation decreases as the rotation of the rotating body 15 progresses according to FIG Figures 3a and 3b , so that the hose 5 is increasingly squeezed until the starting point 12 of the occlusion is reached, when a cavity formed by the hose 5 disappears as a result of the hose being squeezed by the displacement body 10 . The displacement body 10 moves along the curved hose track section 24 on the inlet side. When the displacement body has reached the starting point 12 of the occlusion, another displacement body 10 reaches the starting point 11 of the hose deformation.

The delivery flow is constant if it is ensured that the same volume of fluid is delivered at every point of the hose path at a constant speed of the rotating body of the peristaltic pump. A constant fluid volume is obtained when the length of the curved hose path section 24 on the inlet side corresponds to the distance that corresponds to the angle between two adjacent displacement bodies of the rotating body and the curvature of the hose path in the curved hose path section on the inlet side is designed in such a way that the volume of fluid pumped remains constant. The deformation angle α between two adjacent displacement bodies 10 results from the relationship 360°/number of displacement bodies. If, for example, 6 displacement bodies 10 are arranged on the rotary body 15, an angle α=60° results. In order to fulfill the condition of the constant pumped fluid volume, essentially 1/60 of the fluid volume located between two adjacent displacement bodies is to be pumped with a rotation of 1° according to the exemplary embodiment with 6 displacement bodies. It is therefore the case for each partial angle that the corresponding partial angle proportion of the fluid volume delivered is conveyed, with the partial angle proportion of the fluid volume delivered being constant. In other words, the same partial volume is conveyed with each rotation of the rotating body by each partial angle. To determine the partial angle, the deformation angle α between two adjacent displacement bodies is divided by the number of measured values minus 1. In the present example, 12 measured values are determined, which are Figure 7a are shown. If the deformation angle is α = 60°, the partial angle is 60° / 11 = 5.45°.

In 8 1 shows the course of a curved hose track section 24 on the inlet side for an exemplary embodiment with 12 measured values. The measured values can, for example, according to the measured values 7a or 7b match where 7a or 7b show only one exemplary series of measured values, which is presented as representative of a large number of possible series of measured values. Of course, the measured values of another series of measured values for a hose with a different hose diameter or hose contour or hose thickness, a hose pump with different rotary bodies, a different enveloping circle radius R _HK , or a different angle 52 between adjacent rotary bodies can deviate from this example.

8 serves to illustrate the method step for determining the course of curvature of the curved inlet-side tubular track section 24. For each of the partial angles of the deformation angle α, the measured height Hi is plotted in the radial direction, starting from the enveloping circle radius R _HK . The end point of the segment that corresponds to the measured value for the height Hi is a point P on the hose track. The line connecting the end points of the sections for all i measured values for the heights Hi results in the course of the tubular track, i.e. in this example the curved tubular track section 24 on the inlet side and the tubular track section 21 on the inlet side.

If the displacement body 10 of the hose pump 100 is in the in 8 shown horizontal position, this position on the enveloping circle HK corresponds to the starting point 11 of the tube deformation. At this point in time, the displacement body 10 of the hose pump 100, which is adjacent in the counterclockwise direction, is located at the starting point 12 of the occlusion. The measured value for the height H at the starting point of the tube deformation should be denoted by H ₀ . According to this exemplary embodiment, a height H _i is plotted for each partial angle α _i , which corresponds to a point P _i on the tubular track.

According to the present exemplary embodiment, the points P ₀ to P ₁₁ are determined in this way. The height H ₀ is plotted at the point P ₀ . The height H ₀ corresponds to the outside diameter or the outside contour of the undeformed hose. The term outer contour is used if the cross section of the undeformed hose is not circular.

For the partial angle, α _(i+1) =α _i +Δα applies. Each partial angle has a constant value since Δα is obtained from the equation Δα = α/(n-1). n denotes the number of measured values. For each partial angle αi, the associated measured value for the height H _i in plotted in the radial direction starting from the enveloping circle with the enveloping circle radius R _HK . The obtained end point of the line R _HK + H _i gives the point P _i on the hose track.

The hose path of the curved hose path section 24 on the inlet side and possibly of the hose path section 21 on the inlet side thus results as a connecting line of the points P _i , where i can assume integer values from 0 to n-1. According to the present exemplary embodiment, n=12 since twelve measured values for the height H _i have been determined, here H ₀ to H ₁₁ . According to the Figure 7a The series of measured values shown is H ₀ =10.8 mm, H ₁ =9.0 mm, H ₂ =8.0 mm etc.

The measured values _Hi correspond to a constant change in the level N, ie it holds that N(i+1)-Ni=ΔN=constant. This measurement specification ensures that the change in height, which results from all adjacent pairs of measured values, corresponds to the delivery of a constant volume. The hose path determined for the curved hose path section 24 on the inlet side is thus suitable for conveying a constant, ie constant, volume. Therefore, a particularly pulsation-free delivery can be ensured by means of the curved inlet-side tubular track section, which is obtained from the measurement specification described above.

In particular, the measuring hose 55 is designed as a tubular element, with the tubular element having a smaller diameter than the diameter of the hose 5. If the measuring hose has a smaller diameter 55, small changes in volume can also be measured, so that the corresponding height Hi can be determined much more precisely . The use of a measuring tube 55, which has a smaller diameter than the tube 5, enables a more precise measurement of the heights H _i .

In particular, the tube element can be designed as a transparent tube. The measured value for the level N of the fluid can thus be read more easily, either manually or by using an optical sensor.

The invention also includes a method for operating a peristaltic pump, the peristaltic pump 50, 100 comprising a housing 1, which contains the hose track 2, on which the hose 5 rests, and a rotating body 15 containing at least two displacement bodies 10 for temporarily pinching the hose 5 in the hose track 2, with the hose 5 containing a fluid to be pumped, with the displacement bodies 10 are connected to the rotary body 15 in such a way that the displacement bodies execute a circular movement when the rotary body 15 rotates, so that the fluid is transported through the hose 5 . The displacement body hits the hose 5 at a starting point 11 of the hose deformation, with the distance between the displacement body 10 and the hose track 2 decreasing from the starting point 11 of the hose deformation as the rotating body 15 continues to rotate, so that the hose 5 is increasingly squeezed until a starting point 12 of an occlusion is reached, so that a cavity formed by the hose 5 disappears as a result of the hose being squeezed by the displacement body 10 . An end point 13 of an occlusion is reached when a cavity is created by relieving the hose 5 by increasing the distance between the hose track 2 and the displacement body 10, with an end point 14 of the hose deformation being reached when the displacement body 10 lifts off the hose 5. At least one of the tube tracks from the starting point 11 of the tube deformation to the starting point 12 of the occlusion or from the end point 13 of the occlusion to the end point of the tube deformation 14 is designed as a curved tube track section 24 on the inlet side or a curved tube track section 25 on the outlet side. In particular, an occlusion angle γ is formed between the starting point 12 of an occlusion and the end point 13 of the occlusion, the occlusion angle γ) corresponding to the angle that two adjacent displacement bodies 10 enclose in relation to one another.

In particular, at least one of the curved inlet-side tubular track sections 24 or the curved outlet-side tubular track section 25 is obtained by a measurement specification, by means of which the tubular track is determined over a plurality of heights Hi, which correspond to a constant volume given a constant change in angle Δα.

In particular, a deformation angle α is formed between the starting point 11 of the tube deformation and the starting point 12 of the occlusion. In particular, a deformation angle β is formed between the end point 13 of the occlusion and the end point of the tube deformation 14 . At least one of the deformation angles α, β can correspond to the angle 52 that two adjacent displacement bodies 10 enclose in relation to one another.

According to a variant of the method, the displacement bodies 10 are rotatably mounted in the rotating body 15 . According to a variant of the method, the rotating body 15 contains a plurality of rotating body arms 16 , the displacement bodies 10 being arranged on the rotating body arms 16 of the rotating body 15 .

It is obvious that many other variants are possible in addition to the exemplary embodiments described, without departing from the inventive concept. The subject of the invention is thus not limited by the foregoing description and is to be determined by the scope of protection defined by the claims. For the interpretation of the claims or the description, the broadest possible reading of the claims is decisive. In particular, the terms "comprising" or "include" should be construed as referring to elements, components or steps in a non-exclusive sense, thereby indicating that the elements, components or steps may be present or used that they can be combined with other elements, components or steps that are not explicitly mentioned. When the claims relate to an element or component from a group that may consist of A, B, C to N elements or components, this language should be interpreted as requiring only a single element of that group, and not one Combination of A and N, B and N or any other combination of two or more elements or components of this group.

Claims (15)

Hose pump (100) containing a housing (1) containing a hose track (2) for supporting a hose (5) and a rotating body (15) containing a plurality of displacement bodies (10) for temporarily squeezing the hose (5) in the hose track ( 2), the hose (5) being designed to hold a fluid, the hose track (2) having an inlet-side hose track section (21), a discharge-side hose track section (23) and a hose track section (21) on the inlet side and the outlet-side hose track section (23 ) arranged central tubular track section (22), the central tubular track section (22) having a curvature, with at least one of the inlet-side and outlet-side tubular track sections (21, 23) being adjoined by a curved inlet-side tubular track section (24) or a curved outlet-side tubular track section (25). , characterized in that an occlusion angle (y) is formed between a starting point (12) of an occlusion and an end point (13) of the occlusion, the occlusion angle (γ) corresponding to the angle (52) that two adjacent displacement bodies (10) make to one another lock in. The hose pump according to claim 1, wherein the displacement body hits the hose (5) at a starting point (11) of a hose deformation, the distance between the displacement body (10) and the hose track (2) increasing from the starting point (11) of the hose deformation as the rotation progresses of the rotary body (15) is reduced, so that the hose (5) is increasingly squeezed until the starting point (12) of the occlusion is reached. Hose pump according to claim 2, wherein a deformation angle α is formed between the starting point (11) of hose deformation and the starting point (12) of occlusion, the deformation angle α corresponding to the angle (52) between two adjacent displacement bodies (10). Hose pump according to one of the preceding claims, in which the end point (13) of the occlusion is reached when the hose (5) is relieved through Increasing the distance between the tubular track (2) and the displacement body (10) creates a cavity. Hose pump according to one of the preceding claims, wherein an end point (14) of a hose deformation is formed when the displacement body (10) lifts off the hose (5). Hose pump according to claims 4 and 5, wherein a deformation angle β is formed between the end point (13) of the occlusion and the end point of the hose deformation (14), the deformation angle β corresponding to the angle (52) between two adjacent displacement bodies (10). Hose pump according to one of the preceding claims, wherein at least one of the curved hose path sections (24) on the inlet side or the curved hose path sections (25) on the outlet side can be obtained by means of a measurement specification, by means of which the hose path can be measured over a plurality of heights Hi, which at a constant angle change Δα has a constant Volume correspond, can be determined. Hose pump according to one of the preceding claims, wherein at least one of the curved inlet-side hose path sections (24) and the curved outlet-side hose path sections (25) has a variable radius of curvature. Hose pump according to Claim 8, in which the curvature of the curved hose path section (24) on the inlet side differs at least partially from the curvature of the curved hose path section (25) on the outlet side. Hose pump according to one of the preceding claims, wherein at least one of the inlet-side hose path sections (21) and the outlet-side hose path sections (23) has a curvature, it being possible for the curvature of the inlet-side hose path section (21) to differ at least partially from the curvature of the outlet-side hose path section (23). . Hose pump according to one of the preceding claims, in which the displacement bodies (10) are connected to the rotating body (15) in such a way that they perform a circular movement when the rotating body (15) rotates. Hose pump according to one of the preceding claims, in which the displacement bodies (10) are rotatably mounted in the rotating body (15). Hose pump according to one of the preceding claims, in which the rotating body (15) has a bearing point which is stationary in relation to the rotating body (15) for each displacement body (10). Hose pump according to one of the preceding claims, wherein the rotary body (15) contains a plurality of rotary body arms (16), the displacement bodies (10) being arranged on the rotary body arms (16) of the rotary body (15). Hose pump according to one of the preceding claims, in which the housing (1) contains at least one hose holding device (4, 26).

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