EP3030784B1 - Positive displacement pump - Google Patents

Description

The invention relates to a positive displacement pump with a drive unit and a pump unit.

Displacement pumps are already known in many designs. A disadvantage of the known positive displacement pumps is that they are either not suitable for high pressures and high volume flows or that they are difficult to maintain.

From the DE 1 528 456 A is a positive displacement pump with a drive unit and a pump unit with at least one inline valve unit, wherein the inline valve unit is clamped in an operating position between two flanges known.

The DE 10 2011 001 087 A1 discloses a double-tube membrane process pump with conveyor valves arranged in cassettes and a hydraulically activatable clamping device for biasing the delivery valves.

The invention has set itself the task of creating a positive displacement pump which is improved, at least with regard to one of the disadvantages mentioned.

This object is achieved by the reproduced in claim 1 positive displacement pump.

In the context of this publication, the term "displacement pump" refers to a pump which has at least one displacement element in at least one working space through which the medium to be pumped, that is to say the conveying medium, flows.

The positive displacement pump according to the invention has a drive unit. In addition, a pump unit is provided with at least one inline valve unit. Preferably, two inline valve units are provided per working space.

The inline valve unit is braced in an operating position between two flanges of the pump unit. This distortion of the valve units between two flanges can also be referred to as Zwischenflanscheinbau.

The flanges are interconnected by means of connecting and / or spacing means, preferably at a fixed distance from one another. The clamping is therefore preferably not by successively moving the flanges, but preferably by the spreading (in other words: clamping) of a clamping device.

A displacement of the valve unit is possible without disassembly of a connecting and / or spacer means. It must therefore be disassembled for the displacement of the inline valve unit no connection and / or spacer means by means of which or the flanges are connected to each other.

As a result, the maintenance of the inline valve units is significantly simplified and accelerated.

The distance between two adjacent connection and / or spacer means is preferably greater than the outer dimensions - such as the diameter - of the inline valve unit.

The connecting and / or spacing means are either arranged such that adjacent connecting and / or spacing means always have the same distance from one another or in such a way that different distances between adjacent connecting and / or spacing means result.

The connecting and / or spacing means are arranged such that the greatest distance (more precisely, the clear width) between two adjacent connection and / or spacer means is greater than the outer dimensions - such as the diameter - of the in-line valve unit. As a result, a prerequisite for a displacement of the inline valve unit between two connecting and / or spacer means, without their disassembly created.

It has been found that a resilient connection of the flanges to each other and the inline valve units between the flanges is possible even with such a large distance of the connecting and / or spacer means.

Preferably, a valve displacement device is provided by means of which the inline valve unit can be displaced from an operating position into a maintenance position. In this case, the valve unit is preferably displaceable on a path deviating from a circular path.

The valve displacement device is preferably fixedly connected to the rest of the pump.

The inline valve unit is preferably braced exclusively with the flanges. Thus, there are preferably no other fastening means, such as a screw connection of the valve unit with the flanges provided. By virtue of the fact that the inline valve unit is preferably clamped exclusively between the flanges, a prerequisite for simplified and rapid maintenance is created.

The term "inline valve unit" is referred to in the context of this publication, in particular a valve unit, which is flowed through in a straight line. The term "flows straight through" in the context of this document specifically means that the flow direction immediately before the valve at least approximately corresponds to the flow direction immediately after the valve. This distinguishes inline valve units of angle valve units, in which the fluid enters, for example, on the bottom and at an angle of 90 degrees laterally exit. An advantage of in-line valve units over corner valve units is that a pipe bend connecting the valve unit to the diaphragm housing can be dispensed with and the flow loss associated with the deflection and the dead volume can be dispensed with. Even with corner valve units increased wear due to uneven load is eliminated.

The inline valve units are preferably flowed through at least approximately vertically. This means in particular that the flow direction is at least approximately perpendicular immediately before and immediately after the valve unit. It is also conceivable that the valve units are not flowed through at least approximately vertically.

The pump can have exactly one or more working spaces. It can be single-acting or double-acting.

In particular, the maintenance of the in-line valve units is significantly simplified by the displacement device, since the considerable weight of these units is borne by the valve displacement device and does not have to be held by the installer.

The displacement device can also significantly simplify the maintenance of the in-line valve units by making the valve units accessible to a crane installation.

In the embodiment in which the in-line valve units are flowed through perpendicularly, the two flanges, between which the inline valve unit is clamped, are preferably aligned at least approximately horizontally, and particularly preferably arranged exactly one above the other.

In the maintenance position, the inline valve unit is preferably no longer arranged between the flanges, but freely accessible from all sides.

The in-line valve unit may also be referred to as an in-line delivery valve unit.

The displacement pump is preferably a rinsing pump for drilling fluid or a so-called "slurry pump", ie a pump for transporting solids in liquid. Slurry pumps are also called thick matter pumps. Thick substances are mixtures of liquid and solid components. In one embodiment, the pump generates a pressure of up to 300 bar. It preferably has a delivery rate of up to 1500 m ³ / h. The power of the pump is preferably more than 500 kW. It is about 2400 kW in one embodiment and about 5000 kW in another embodiment.

Advantageously, the pump unit is a flat membrane pump unit. The displacement element thus preferably comprises a flat membrane.

In the preferred embodiment, the membrane is arranged vertically in its center position. However, it is also conceivable that the membrane is not arranged vertically in its central position. This can be effected for example by a non-horizontal installation of the pump.

The displacer element is preferably actuated by a working fluid, which in turn is preferably pressurized by an oscillating piston of a drive unit. In the embodiment in which the pump unit is a flat diaphragm pump unit, the piston pressurizing the working fluid is completely separated from the fluid to be pumped by the diaphragm.

In the embodiment with flat membrane, this is more preferably arranged in its central position perpendicular to the direction of movement of the oscillating piston of the drive unit. However, it is also conceivable that the diaphragm is not aligned in its central position perpendicular to the direction of movement of the oscillating piston of the drive unit.

The connection and / or spacer means preferably comprise threaded bolts, which more preferably pass through spacer sleeves.

The connection and / or spacer means are preferably arranged such that different distances between two adjacent connection and / or spacer means result.

Preferably, the connection and / or spacer means are arranged such that the greatest distance between adjacent connection and / or spacer means is provided in the region of the movement path of the inline valve unit.

When the connecting and / or spacing means are arranged such that the largest distance (more precisely, the inside width) between two adjacent connecting and / or spacing means is only slightly larger than the outer dimensions - such as the diameter - of the in-line valve unit , then on the one hand a prerequisite for a compact pump unit is created. In addition, the bending load on the flanges caused by the distortion of the valve units is reduced, compared to an arrangement with adjacent connecting and / or spacing means of greater spacing. On the other hand, this continues to be a prerequisite for a displacement of the inline valve unit between two connecting and / or spacer means, without their disassembly, created.

The largest distance (more precisely, the inside width) between two adjacent connecting and / or spacing means can be only less than thirty and in particular only less than ten percent of the outer dimensions of the inline valve unit greater than this.

Preferably, exactly four connecting and / or spacing means are provided, which are arranged in the form of a rectangle. Another number of connecting and / or spacers is conceivable.

In an alternative embodiment with equal distances between connection and / or spacer means, this is greater than the outer dimensions - such as the diameter - of the inline valve unit.

In the embodiment in which the inline valve unit is displaceable by means of the valve displacement device on a movement path deviating from the circular path, even with such a small (largest) distance between adjacent connection and / or spacer means, a displacement of the inline valve unit from an operating position take place in a maintenance position by means of the valve displacement device, without disassembly of a connecting and / or spacer means is required.

Also, a maintenance position can be achieved, which is characterized by a desirable large distance from the rest of the pump unit, without the need for a complex, in turn, much tree space-consuming displacement device would be required.

In the preferred embodiment, the in-line valve unit is displaceable without disengaging a screw connection on the pump unit-in one embodiment, except for the hydraulic tensioner. It must therefore preferably be solved for displacing the inline valve unit at most a screw of the hydraulic tensioning device.

In one embodiment, the in-line valve unit is displaceable already after loosening a threaded element of the clamping device. To relocate the inline valve unit, so a threaded element of the clamping device - if necessary after hydraulic relief of the threaded element - and no threaded element of the remaining pump to be solved.

In one embodiment, the inline valve unit after the release of a single threaded element, preferably a lock nut of the clamping device, displaced.

The maintenance of the in-line valve units is thereby facilitated and accelerated.

In one embodiment, the valve displacement device comprises an articulated articulated arm. Advantageously, the articulated arm is mounted on a connection and / or spacer. An arranged between the flanges, only the storage of the articulated arm on the other pump unit serving element can therefore, as preferred, omitted.
More preferably, the articulated arm is also hinged to the inline valve unit.

It has been found that a displaceability of the in-line valve unit deviating from a circular path can be achieved in a simple and reliable manner by means of such an articulated arm.

In a preferred embodiment, the inline valve unit is at least partially displaceable on a translational movement path. In another embodiment, the in-line valve unit is displaceable exclusively on a translatory movement path.

In one embodiment, the valve displacement device comprises a telescopic arm.

Even if the valve displacement device comprises lateral telescopic rails - preferably two per inline valve unit - there is a suitable, then drawer-like, displaceability of the valve unit.

It is conceivable to provide a plurality of valve units and a plurality of displacement devices on a single pair of flanges. The quick change system created in this manner reduces the downtime of the pump due to maintenance of the in-line valve assemblies because the in-line valve assemblies can be serviced while already serviced inline valve assemblies have been returned to the operating position.

Advantageously, at least one inline valve unit is clamped by means of a hydraulic tensioning device between the flanges. The tension can thereby be made in a low-torque and precise manner.

The hydraulic tensioning device preferably adjoins one of the flanges. In particular, in the embodiment in which the flanges are arranged exactly one above the other, the hydraulic tensioning device preferably adjoins the lower flange. The hydraulic tensioning device is therefore preferably arranged between the lower flange and the in-line valve unit.

If the hydraulic tensioner is a stand-alone unit, which preferably is not fixedly connected to the pump unit, such as an adjacent flange, then it can be easily replaced or serviced (e.g., replacement of gaskets).

Preferably, the hydraulic tensioning device is removable without tools in the relaxed state.

An alternative embodiment, in which the hydraulic tensioning device can not be removed without tools in the relaxed state, is conceivable in particular if the two flanges are not exactly one above the other, but are arranged obliquely one above the other or next to one another, for example. It can then be provided securing means which fix the hydraulic tensioning device against falling out. These securing means can be designed so that they can be solved only with tools.

In a preferred embodiment, the hydraulic tensioning device - particularly preferably exactly - a hydraulic cylinder element.

The hydraulic cylinder element provides exactly one hydraulic cylinder in one embodiment.

In one embodiment, exactly one pressure piston is provided.

It is conceivable that the hydraulic tensioning device has exactly one annular piston in exactly one annular cylinder.

However, the hydraulic cylinder element preferably provides a plurality of cylindrical hydraulic cylinders. And with advantage, a plurality of single hydraulic piston is provided. The single hydraulic piston can also be referred to as a pressure piston. Preferably, they are cylindrical.

The hydraulic tensioner is double-acting in one embodiment. Thus, in this embodiment, the hydraulic pistons can be pressurized selectively on two different sides of an effective surface and thereby moved in two directions.

However, in the preferred embodiment, the hydraulic tensioner is single acting and the individual pistons are each equipped with a piston return spring.

It is conceivable that a plurality of counter-elements are provided to fix the hydraulic tensioning device in a tensioned state.

If exactly one locknut is provided to fix the hydraulic tensioning device in a tensioned state, then a particularly fast and resilient producible possibility is created to depressurize the hydraulic tensioning device while maintaining the tensioned state of the inline valve unit.

Fig. 1

eine beispielhafte Verdrängerpumpe mit einer Antriebseinheit und einer Pumpeneinheit;

Fig. 2

eine teilgeschnittene Seitendarstellung einer Pumpeneinheit mit oberer Inline-Ventileinheit in Betriebsstellung und unterer Inline-Ventileinheit in Wartungsstellung, wobei die Ventilverlagerungseinrichtung als Gelenkarm ausgeführt ist;

Fig. 3

ein vergrößertes Detail aus Fig. 2;

Fig. 4

eine perspektivische Darstellung der in Fig. 2 gezeigten Pumpeneinheit;

Fig. 5

eine Seitendarstellung der in Fig. 2 gezeigten Pumpeneinheit, mit oberer Inline-Ventileinheit in Wartungsstellung und unterer Inline-Ventileinheit in Betriebsstellung;

Fig. 6

ein vergrößertes Detail aus Fig. 5;

Fig. 7

eine perspektivische Darstellung der in Fig. 5 gezeigten Pumpeneinheit ;

Fig. 8

eine teilgeschnittene Seitendarstellung einer Pumpeneinheit mit Teleskoparmen;

Fig. 9

ein vergrößertes Detail aus Fig. 8;

Fig. 10

eine perspektivische Darstellung der in Fig. 8 gezeigten Pumpeneinheit;

Fig. 11

eine teilgeschnittene Seitendarstellung einer Pumpeneinheit, bei der jede Ventilverlagerungseinrichtung zwei Teleskopschienen umfasst;

Fig. 12

ein Detail aus Fig. 11;

Fig. 12a

eine Ansicht wie in Fig. 12, jedoch in kleinerem Maßstab und mit durch die Kontermutter fixiertem Hydraulikzylinderelement

Fig. 13

eine perspektivische Darstellung der in Fig. 11 gezeigten Pumpeneinheit;

Fig. 14

eine teilgeschnittene Seitendarstellung einer Pumpeneinheit, bei der an jedem Flanschpaar mehrere Ventileinheiten und mehrere Verlagerungseinrichtungen angeordnet sind;

Fig. 15

ein Detail aus Fig. 14;

Fig. 16

eine perspektivische Darstellung einer Pumpeneinheit, bei der an jedem Flanschpaar mehrere Ventileinheiten und mehrere Verlagerungseinrichtungen vorgesehen sind, wobei eine obere Ventileinheit in Betriebsstellung und eine obere Ventileinheit in Wartungsstellung und beide untere Ventileinheiten in Wartungsstellung sind;

Fig. 17

eine geschnittene Darstellung einer Inline-Ventileinheit im gespannten Zustand;

Fig. 18

eine geschnittene Darstellung einer Inline-Ventileinheit im ungespannten Zustand.

The invention will now be explained in more detail with reference to embodiments shown in the drawings. Show it:

Fig. 1

an exemplary positive displacement pump with a drive unit and a pump unit;

Fig. 2

a partially sectioned side view of a pump unit with upper inline valve unit in the operating position and lower inline valve unit in the maintenance position, wherein the valve displacement device is designed as an articulated arm;

Fig. 3

an enlarged detail Fig. 2 ;

Fig. 4

a perspective view of in Fig. 2 shown pump unit;

Fig. 5

a page representation of in Fig. 2 shown pump unit, with upper inline valve unit in maintenance position and lower inline valve unit in operating position;

Fig. 6

an enlarged detail Fig. 5 ;

Fig. 7

a perspective view of in Fig. 5 shown pump unit;

Fig. 8

a partially sectioned side view of a pump unit with telescopic arms;

Fig. 9

an enlarged detail Fig. 8 ;

Fig. 10

a perspective view of in Fig. 8 shown pump unit;

Fig. 11

a partially sectioned side view of a pump unit, wherein each valve displacement device comprises two telescopic rails;

Fig. 12

a detail from Fig. 11 ;

Fig. 12a

a view like in Fig. 12 but on a smaller scale and with fixed by the lock nut hydraulic cylinder element

Fig. 13

a perspective view of in Fig. 11 shown pump unit;

Fig. 14

a partially sectioned side view of a pump unit, in which a plurality of valve units and a plurality of displacement devices are arranged on each pair of flanges;

Fig. 15

a detail from Fig. 14 ;

Fig. 16

a perspective view of a pump unit, in which a plurality of valve units and a plurality of displacement devices are provided on each pair of flanges, wherein an upper valve unit in the operating position and an upper valve unit in the maintenance position and both lower valve units in the maintenance position;

Fig. 17

a sectional view of an inline valve unit in the tensioned state;

Fig. 18

a sectional view of an inline valve unit in the untensioned state.

Fig. 1 shows an exemplary positive displacement pump with a drive unit A and a pump unit 100. The drive unit A comprises a drive shaft 15 which is rotated by a motor, not shown, for example, an electric motor in rotation. On the drive shaft 15 at least one indicated only gear is arranged, which meshes with at least one much larger, also merely indicated gear of the crankshaft 13. The drive shaft 15 may protrude on both sides of the housing of the drive unit. On the crankshaft a connecting rod 14 is arranged. The connecting rod is mounted on the crankshaft with the help of a connecting rod bearing, which is designed as a rolling bearing.

The connecting rod transmits its movement by means of a crosshead 16 to a crosshead rod 17, which merges into the piston rod 18. The crosshead bearing is also a rolling bearing. The crosshead also includes sliding blocks, which serve its linear bearing on the Gleitlagerwandungen. On the piston rod, a working medium piston 19 is arranged, which carries out a rectilinear oscillating movement in a working medium cylinder 20.

On the drive unit A, a pump unit 100 is provided. This provides a work medium space adjoining the working medium cylinder 20, in which working medium 21, for example hydraulic oil, is provided, which transfers the movement of the working medium piston 19 to a flat membrane 24. The flat membrane 24 is in Fig. 1 shown in their two extreme positions. The flat membrane 24 forms together with a part of the diaphragm housing 26 a working space 25. This is via check valves in inline valve units 1, 1 'with a in Fig. 1 Not shown pressure tube and suction pipe connected.

A rotational movement of the crankshaft causes working fluid in the working medium space to be moved back and forth and thus deflects the flat membrane alternately to the right and left. The deflection to in Fig. 1 left leads to a closing of the outlet check valve or pressure valve and to a suction of fluid through the open inlet check valve or suction valve. The subsequent displacement of the piston according to Fig. 1 to the right leads to a closing of the inlet check valve and a delivery of a displacement or displaced piston volume corresponding volume of fluid through the now open outlet check valve and the displacement of the membrane based on Fig. 1 to the right. At the in Fig. 1 shown pump can be arranged side by side three connecting rods, working medium cylinder and pump units 100. It can therefore be a triplex pump with three working spaces. It can also more or less - about exactly two - connecting rods, working medium cylinders and pump units are arranged side by side.

Per working space 25, two inline valve units 1, 1 'are provided.

The inline valve units 1, 1 'are traversed in a straight line by conveying medium. The flow direction immediately before the valve thus corresponds at least approximately to the flow direction immediately after the valve. A change of direction of the pumped medium does not take place in the area of these valves.

Approximately Fig. 2 shows that in the operating position each inline valve unit 1, 1 'between two flanges 2, 2' is braced. Two parallel and spaced apart flanges 2, 2 'thus form a flange pair 2a, between which the inline valve unit 1, 1' is braced. Fig. 2 also shows that a valve displacement device 3 fixedly connected to the rest of the pump is provided, with the aid of which each inline valve unit 1, 1 'is clamped from an operating position B in which the inline valve unit 1 is braced between the flange pair 2a into a maintenance position W, in which the in-line valve unit 1 'is not arranged between the pair of flanges, is displaceable.

About the Fig. 2 and 4 show that the flanges 2, 2 'in all the embodiments shown by means of connecting and / or spacers 4 are interconnected. The connecting and / or spacing means 4 are designed in all embodiments shown as connecting and spacer means 4, which connect the flanges firmly together at a predetermined, fixed distance. As connecting means, the connection and spacer means 4 in all the embodiments shown with the flanges 2, 2 'screwed by means of nuts threaded bolt. As a spacer they have between the flanges arranged spacers, which are penetrated by the threaded bolt.

For example Fig. 7 shows that four connecting and spacer means 4 are provided per valve unit 1, 1 ', which are arranged in the form of a rectangle. There are therefore two different distances K, L between adjacent connection and spacer means 4. The Fig. It can also be seen that the connecting and spacer means 4 are arranged so that the larger the two distances L is perpendicular to the direction of displacement V of the inline valve unit 1, 1 'extends and is slightly larger than the outer dimensions M of the inline valve unit 1. The largest distance L between two adjacent connecting and spacing means 4 is thus in the range Movement path of the inline valve unit 1, 1 'provided. The perpendicularly running smaller distance K between two adjacent connection and spacer means 4 may be smaller than the outer dimensions M of the in-line valve unit 1 (FIG. Fig. 5 ).

The displacement direction V simultaneously symbolizes a movement path of an inline valve unit 1. This deviates from a circular path. She can, as in Fig. 7 shown to be at least partially rectilinear.

Due to the small distance between the connecting and spacer means 4 a compact design is achieved and the bending load of the flanges 2, 2 'is reduced. Since at least sections of a linear trajectory of the inline valve units 1, 1 'is possible, they can still be moved between two connection and spacer means 4, without disassembly of movement and spacers 4 would be required.

In the in the Fig. 2 to 7 In the exemplary embodiment shown, the valve displacement device 3 comprises an articulated arm 5 which articulates in itself.

In the in the Fig. 8 to 10 In contrast, the valve displacement device 3, on the other hand, comprises a telescopic arm 6.

In the in the Fig. 11 to 13 In the embodiment shown, the valve displacement device 3 comprises two telescopic rails 7, 7 '.

In the in the Fig. 14 to 16 shown embodiment, a plurality of inline valve units 1, 1 ', namely two inline valve units 1, 1' and a plurality of displacement devices 3, namely two displacement devices 3, are provided on each pair of flanges 2a. The displacement device 3 comprises in This embodiment, as in the in the Fig. 2 to 7 shown embodiment, an articulated arm. 5

In all the exemplary embodiments shown, the in-line valve units 1, 1 'are respectively braced exclusively by means of a hydraulic tensioning device 8 between the flanges 2, 2'.

Approximately Fig. 3 shows that the hydraulic tensioning device 8 forms a self-contained unit, which is not firmly connected to the pump unit 100, such as the adjacent lower flange 2. It is in the relaxed state without tools, so without the aid of tools, removable. The hydraulic tensioner 8 has a hydraulic cylinder element 9 which is annular and in which a plurality of cylinder bores 9a are arranged. Fig. 3 also shows that the flange 2, on which the hydraulic tensioning device 8 is arranged, has an annular projection 2b. The outer diameter of the annular projection 2b is slightly smaller than the inner diameter of the annular hydraulic cylinder member 9, so that the hydraulic cylinder element 9 on the annular projection 2b of the flange 2 - guided by means of a linear sliding bearing - and at the same time centered.

In each cylinder bore 9a, a cylindrical single hydraulic piston 10 is arranged. Each single hydraulic piston 10 has a collar 23. By a hydraulic line 27, each cylinder bore 9a can be filled above the piston collar 23 with hydraulic fluid and pressurized. As a result, the hydraulic cylinder element 9 lifts and thereby biases the in-line valve unit 1, 1 '. The hydraulic cylinder element 9 is based on the hydraulic fluid to the single hydraulic piston 10, which in turn are supported on the flange 2. This tensioned state of the hydraulic tensioning device 8 is, for example, in Fig. 3 shown. Then, the lock nut 12 can be screwed down so far, until it is also supported on the lower flange 2 (only in Fig. 12a shown). The hydraulic cylinder element 9 is fixed in this way and the hydraulic system of the hydraulic tensioning device 8 can be relieved. The inline valve unit 1 is thus stretched securely between the flange pair 2a. Also Fig. 17 shows this state, the lock nut 12 also in Fig. 17 not screwed down yet.

The single hydraulic piston 10 have, such as the FIGS. 17 and 18 point away from the respective in-line valve unit 1, 1 'and the hydraulic cylinder element 9 faces the in-line valve unit 1, 1' and is in contact therewith. A twisted by 180 degrees arrangement in which the individual hydraulic piston 10 of the respective inline valve unit 1, 1 'are facing and the hydraulic cylinder element 9 of the inline valve unit 1, 1' away, is conceivable.

To relax the hydraulic tensioning device 8 in order to be able to displace and service the in-line valve unit 1, 1 ', the pressure fluid of the hydraulic tensioning device is first pressurized again. Then the lock nut 12 can be easily solved. If then the pressure of the hydraulic fluid is reduced in the cylinder bores, then arranged between the collar 23 of the piston 10 and a collar 22 of the hydraulic cylinder member 9 piston return spring 11 ensures that the piston 10 hineinverlagern into the hydraulic cylinder element 9, as in Fig. 18 is shown. In the unstressed state of the hydraulic tensioning device 8 shown there, the in-line valve unit 1 can be displaced. A return connection between the hydraulic cylinder element 9 and the adjacent to the hydraulic tensioning device 8 flange 2 is not present. It has been shown that it is expendable.

The hydraulic tensioning device 8 has seals 28, to seal against pumped liquid ( Fig. 12 ).

List of reference numbers :

100

pump unit

1, 1 '

Inline valve unit

2, 2 '

flange

2a

flanges

2 B

annular projection

3

Valve displacement device

4

Connecting and / or spacer means

5

articulated articulated arm

6

telescopic arm

7, 7 '

telescopic rails

8th

hydraulic tensioning device

9

Hydraulic cylinder element

9a

cylinder bores

10

Single hydraulic pistons

11

piston return

12

locknut

13

crankshaft

14

pleuel

15

drive shaft

16

Phillips

17

Phillips rod

18

piston rod

19

Working medium piston

20

Working medium cylinder

21

working medium

22

Covenant of the cylinder

23

Bunch of the piston

24

flat membrane

25

working space

26

membrane housing

27

hydraulic lines

28

seals

A

drive unit

B

operating position

K

smaller distance

L

clear width and greater distance

M

external dimensions

W

maintenance position

V

displacement direction

Claims (9)

1. Positive displacement pump having a drive unit (A) and a pump unit (100) having at least one inline valve unit (1, 1'),
   wherein the inline valve unit (1, 1') is tensioned in an operating position (B) between two flanges (2, 2')
   and the flanges (2, 2') are connected to each other by means of connection and/or spacer means (4),
   wherein a displacement of the inline valve unit (1, 1') is possible without dismounting a connection and/or spacer means (4), characterized in that either the connection and/or spacer means (4) are arranged in such a way that different distances between adjacent connection and/or spacer means (4) arise and the largest distance between two adjacent connection and/or spacer means (4) is greater than the outer dimensions (M) of the inline valve unit (1, 1')
   or
   adjacent connection and/or spacer means (4) have the same distance to each other, and this distance is greater than the outer dimensions (M) of the inline valve unit (1, 1').
2. Pump according to claim 1, characterized in that the distance (L) between two adjacent connection and/or spacer means (4) is greater than the outer dimensions (M) of the inline valve unit (1, 1') and the pump unit (100) is a flat membrane pump unit.
3. Pump according to claim 1 or 2, characterized in that a valve displacement device (3) is provided by means of which the inline valve unit (1, 1') is displaceable from the operating position (B) to a maintenance position (W), wherein the inline valve unit (1, 1') is displaceable on a movement path deviating from a circular path.
4. Pump according to claim 3, characterized in that the valve displacement device (3) comprises a self-articulated arm (5).
5. Pump according to any one of claims 3 or 4, characterized in that the valve displacement device (3) comprises a telescopic arm (6).
6. Pump according to any one of claims 3 to 5, characterized in that the valve displacement device (3) comprises two telescopic rails (7, 7').
7. Pump according to any one of claims 1 to 6, characterized in that several inline valve units (1, 1') and several displacement devices (3) are provided on a single flange pair (2a).
8. Pump according to any one of claims 1 to 7, characterized in that the inline valve unit (1, 1') is tensioned between the flanges (2, 2') by means of a hydraulic tensioning device (8) and the hydraulic tensioning device (8) constitutes an independent unit which is not firmly connected to the pump unit (100).
9. Pump according to claim 8, characterized in that the hydraulic tensioning device (8) has a hydraulic cylinder element (9) and a plurality of individual hydraulic pistons (10) and the hydraulic tensioning device (8) is double acting or the individual hydraulic pistons (10) are equipped with a piston return spring (11) and exactly one counter nut (12) is provided for fixing the hydraulic tensioning device (8) in a tensioned state.

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