EP3740321B1 - Centrifuge - Google Patents

Description

The invention relates to a centrifuge according to the preamble of claim 1.

The features of the generic term and feature a) of the label reveal the DE 28 34 340 QA1. The technological background also includes: DE 28 44 721 A1 called.

The starting product to be clarified with a centrifuge drum and thus also the solids contained therein - which can be waste materials but also valuable materials - are exposed to high centripetal acceleration, which in a separator with a vertical axis of rotation is more than 10,000 times the acceleration due to gravity (more than 10,000 g). can. The closed drum keeps the materials in the rotating system, in which a pressure builds up that is proportional to the square of the angular velocity "ω ² ".

If one or more outlet openings provided for the outlet of solids open on the outer circumference of the drum when the drum is being emptied of solids, the solid under pressure is pressed through these outlet opening(s) at high speed and thus energy. When emptying solids from a self-draining separator at full speed, the solids, especially abrasive solids, can cause wear on the discharge opening(s) of the lower drum part, on the upper drum part and in particular on the piston slide.

In order to reduce this wear, it is known to protect vulnerable areas on the outside of the drum with special elements or with a coating made of a suitable hard material, such as hard metal (eg WO2004/054719 A1 ). In this respect, this also becomes the state of the art DE 1 869 993 U called, which discloses wear protection rings for protection against abrasive wear.

The invention has the task of creating further constructive ways to protect elements of and on centrifuge drums against abrasive wear.

1. a) die Trommel ist an einer Axial-Ringfläche des Trommeloberteils oder des Trommelunterteils mit zwei oder mehr ersten Verschleißschutzelement(en) versehen, wobei die Verschleißschutzelemente die Form von Kreisringsegmenten aufweisen und/oder
2. b) der Kolbenschieber ist an einer korrespondierenden Axial-Ringfläche mit zwei oder mehr zweiten Verschleißschutzelement(en) versehen, wobei die Verschleißschutzelemente die Form von Kreisringsegmenten aufweisen, und
3. c) wobei jedes der Verschleißschutzelemente gemeinsam mit einem oder ggf. zwei jeweils angrenzenden Verschleißschutzelementen jeweils eine Stoßkante aufweist, so dass zwischen aneinander liegenden Stoßkanten eine Fuge ausgebildet ist.

The invention solves this problem through the subject matter of claim 1. This centrifuge is characterized by one or both of the following features a) and/or b) and feature c):

1. a) the drum is provided on an axial annular surface of the upper drum part or the lower drum part with two or more first wear protection element(s), the wear protection elements having the shape of circular ring segments and/or
2. b) the piston slide is provided on a corresponding axial annular surface with two or more second wear protection element(s), the wear protection elements having the shape of circular ring segments, and
3. c) whereby each of the wear protection elements has an abutting edge together with one or possibly two adjacent wear protection elements, so that a joint is formed between adjacent abutting edges.

In this way, the wear protection on the drum and/or on the piston slide is improved in a simple manner.

Advantageous variants of this invention are explained below, with which wear protection can be optimized.

If the piston slide is guided displaceably in the lower drum part, the drum part on which the first wear protection elements are arranged is the upper drum part (which may also include an element such as a ring arranged on the upper drum part). If, on the other hand, the piston slide is guided displaceably in the upper part of the drum - which is less preferred but can be achieved - the drum part on which the first wear protection elements are arranged is the lower drum part.

It can be provided that the first and/or second wear protection element(s) are designed such that they cover the entire axial annular surface of the component on which they are arranged or attached. This configuration offers the advantage that the component or components or functional carriers, which are activated by mechanically opening and closing the solids discharge openings Allow solids outlet to be equipped with wear protection elements over its entire circumference or in the circumferential direction and be protected accordingly.

Alternatively, it can be provided that the first and/or second wear protection elements are designed in such a way that they only cover a part of the axial annular surface of the component on which they are arranged (i.e. either on the one hand the upper drum part or the lower part and/or on the other hand the Cover piston slide). Sections of the correspondingly covered areas are then better protected.

It can advantageously be provided that wear protection elements are provided on both corresponding components - in particular on the upper part of the drum and on the piston slide - and that these abut one another axially in the closed state of the solids discharge openings of the drum. This results in particularly advantageous protection for both components.

According to a variant, it can be provided that the first and/or second wear protection elements are designed such that they only cover a radial part of the axial annular surface of the component on which they are arranged.

According to another variant, however, it can be provided that the first and/or second wear protection element(s) are designed such that they only cover individual circumferential sections of the axial annular surface of the component on which they are arranged, so that they do not form a circumferentially closed ring .

It can also be provided that the first and/or second wear protection elements work together to form a circumferentially closed ring. In this way, particularly advantageous wear protection is achieved.

According to one variant, this ring projects axially inwards over the respective component. This means that some solid matter can accumulate here, which provides further protection against wear. This will be explained in more detail below and also based on the description of the figures. However, the ring can also be flush with the respective component radially inwards.

In order to achieve good wear protection and good mountability, it can also be provided that the first and/or second wear protection elements (e.g. in two directions) are arranged in a form-fitting manner on the component whose surface they cover.

In the context of this document, “solids” are understood to mean the substances that are emptied through the outlet openings of the drum. These can be, for example, cloudy substances or contamination, but also auxiliary materials such as bentonite or valuable materials such as algae, yeast, cell cultures or microorganisms. The term solid should not be understood too narrowly. This also includes a possibly flowable phase, which can be emptied through the openings that can be released and closed by the piston slide.

The first wear protection element(s) can thus be designed in such a way that they cover the entire axial annular surface of the upper drum part. Alternatively, they can also be designed in such a way that they extend radially and/or in the circumferential direction only over part of the axial annular surface of the upper drum part and only partially cover it. It can preferably be provided that the first wear protection element(s) form a circumferentially closed ring. However, it or they can only be provided in sections in the circumferential direction, so that no circumferentially closed ring is formed. However, it is preferably provided that at least the radial region is assigned a wear protection element of the upper drum part radially in front of each discharge opening. In this way, the abrasive wear on the upper part of the drum is effectively reduced in this vulnerable area. This is a preferred embodiment of the invention. A particularly advantageous wear protection results when the ring of wear protection elements on the upper part of the drum is designed to be closed around the circumference.

The second wear protection element or elements can be designed in such a way that they cover the entire axial annular surface of the piston slide. Alternatively, they can also be designed in such a way that they extend radially and/or in the circumferential direction only over part of the axial annular surface of the piston slide and only partially cover it. It can preferably be provided that the second wear protection element(s) has a circumferentially closed ring form. However, it or they can only be provided in sections in the circumferential direction, so that no circumferentially closed ring is formed. However, it is preferably provided that at least the radial region is assigned a wear protection element of the piston slide radially in front of each discharge opening. In this way, the abrasive wear on the piston valve in this vulnerable area is effectively reduced. This is a preferred embodiment of the invention. Particularly advantageous wear protection results when the ring of wear protection elements on the piston slide is designed to be circumferentially closed.

According to a preferred embodiment, the first and/or second wear protection elements can be designed as plates, in particular as arcuate plate sections of an otherwise preferably flat ring at least on one side. These can then preferably have the shape of a circular ring segment. As a result, the wear protection elements can advantageously be produced cost-effectively without large amounts of waste. The circular ring segments can complement each other to form a closed circle or ring. They can each be placed next to each other in the circumferential direction. Each circular ring segment is then not circumferentially closed and is preferably smaller than 360°, in particular smaller than 180° or even smaller than 90°.

According to the invention, the plurality of wear protection elements together with one (if, for example, two semicircles form a ring) or possibly two adjacent wear protection elements (for example, if three or more circular ring segments form a ring) then each have a common abutting edge. A joint is therefore formed between adjacent or abutting abutting edges.

According to one embodiment, the respective joint or all joints can run completely or partially radially. However, it is preferred that it does not run radially entirely or in sections but is inclined at an angle α in the direction of rotation of the drum. This prevents the radially escaping solid from following the course of the joint and eroding it. Since the direction of the escaping solid essentially crosses the course of the joint at the angle α, erosion of the joint is minimized.

The respective joint or all joints can also have a wave-shaped or zigzag-like contour, in such a way that adjacent wear protection elements can be lined up or lined up with one another in a form-fitting manner in the circumferential direction.

This means that the radially emerging abrasive solid particles do not immediately follow a joint that forms the respective abutting edge between two wear protection elements, but are advantageously slowed down by the wavy or zigzag-like course of the abutting edge and thus do not expand or further grind the joint can. Furthermore, the wave or zigzag shape of the abutting edge also enables the abrasive solid particles to get stuck in the joint, which results in further advantageous protection of the abutting edge from further abrasive expansion of the joint.

In a further preferred embodiment of the invention, the abutting edge has an alternating arrangement of one or more angular sections. As a result, the wavy or zigzag-like course of the abutting edge is formed in an advantageously simple manner.

Solids that have penetrated into the joint are slowed down by the angle section and prevented from flowing further. The solid collected in this way closes the joint, which advantageously protects the abutting edge from further abrasive expansion of the joint.

In a further preferred embodiment of the invention, the opening direction of the angle α is directed in the direction of rotation of the drum. Since the escaping solid is braked in the opposite direction to the direction of rotation, an angle α in the direction of rotation favors the crossing of the escaping solid and the joint.

In a further preferred embodiment of the invention, the first wear protection elements and the second wear protection elements are designed so that they each protrude a defined distance radially beyond the inner edge of the upper drum part or piston slide into the interior of the drum.

This is advantageous because, despite the outlet opening(s) being open, solid remains on the inside of the wear protection elements and thus on the inside surface of the piston slide or on the inside surface of the upper drum part. The solid slides on this remaining layer during further emptying. This is advantageous because the surfaces of the upper drum part or the piston slide are additionally protected against abrasive wear, since the adhering solid layer covers the surfaces and thereby creates an advantageous protective effect.

Further advantageous embodiments of the method according to the invention can be found in the subclaims.

Figur 1:

eine schematische Schnittansicht einer Zentrifuge, welche nach einem erfindungsgemäßen Verfahren betrieben werden kann;

Figur 2:

in a) eine Ausschnittsvergrößerung der Trommel im Bereich einer Auslassöffnung mit geschlossener Auslassöffnung und in b) die Ausschnittsvergrößerung aus Fig. 2a) mit geöffneter Auslassöffnung

Figur 3:

in a) eine Ausführungsvariante der Erfindung und in b) die Ausschnittsvergrößerung aus Fig. 3a) mit geöffneter Auslassöffnung:

Figur 4:

eine Draufsicht auf die geöffnete Auslassöffnung nach Fig. 3a bzw. Fig. 3b, wobei das Trommeloberteil ausgeblendet wurde.

The invention is explained in more detail below using a preferred exemplary embodiment with reference to the accompanying drawings. It shows:

Figure 1:

a schematic sectional view of a centrifuge which can be operated using a method according to the invention;

Figure 2:

in a) an enlargement of the detail of the drum in the area of an outlet opening with a closed outlet opening and in b) the enlargement of the detail Fig. 2a ) with the outlet opening open

Figure 3:

in a) an embodiment variant of the invention and in b) the enlarged section Fig. 3a ) with the outlet opening open:

Figure 4:

a top view of the opened outlet opening Fig. 3a or. Fig. 3b , with the drum top hidden.

Fig. 1 shows a centrifuge - here designed as a separator - for clarifying solids-containing, flowable starting products AP from solids with a rotatable drum 1 with a vertical axis of rotation D. The starting product AP is processed in continuous operation.

The separator shown here is a self-draining separator. This means that the inflow of the suspension to be clarified or the starting product AP to be clarified takes place continuously and the discharge of at least one clarified liquid phase, called clear phase KP, also takes place continuously. In the design as a self-emptying separator, the drum 1 of the centrifuge, on the other hand, has a discontinuous solids outlet, whereby the solid F separated from the starting product AP by clarification is removed at intervals by opening and reclosing one or more outlet openings 2.

The rotatable drum 1 has a lower drum part 3 and an upper drum part 4. The drum 1 is surrounded here by a hood 5 which is spaced apart from it and does not rotate during operation. The drum 1 is also placed on a drive spindle 6, which is rotatably mounted and can be driven by a drive motor. The rotatable parts overall form a rotating system, which includes the drum 1 and the drive spindle 6. During operation, the rotating system is rotated in a direction of rotation U.

The drum 1 has a product inlet 7 through which the starting product AP is passed into the drum 1. It also has at least one process 8 - provided with a gripper - which serves to derive a clear phase KP from the drum 1. The gripper - also called a peeling disk - is designed here as a centripetal pump. The process 8 can also be carried out constructively in a different way or with other means. In addition to the clarification, it is also conceivable to separate the starting product AP into two liquid phases of different densities. For this purpose, another liquid drain is required. The drum can be hermetically sealed or not hermetically sealed.

The drum 1 preferably has a plate pack 9 made of axially spaced separating plates. A solids collecting space 10 is formed between the outer circumference of the plate pack 9 and the inner circumference of the drum 1 in the area of its largest inner diameter. Solids, which are separated from the clear phase KP in the area of the plate stack 9, collect in the solids collecting space 10, from which the solids F can be discharged from the drum 1 via one or more outlet openings 2.

The outlet opening(s) 2 can be opened and closed here by means of a piston slide 11, which is arranged in the lower drum part 3 and can be displaced parallel to the axis of rotation (in particular vertically). When the outlet opening(s) 2 is open, the solid F is discharged from the drum 1 into a solids catcher 12.

To move the piston slide 11, the drum 1 has an actuating mechanism. Here this includes at least one supply line 22 for a control fluid, such as water or clear phase KP and a valve arrangement 23 in the drum 1 and further elements outside the drum 1. This enables the control fluid to be supplied via a metering arrangement 24 arranged outside the drum 1, which is assigned to a hydraulic line 25 for the control fluid arranged outside the drum 1, so that the control fluid can be introduced into the drum 1 by releasing the valve arrangement 23 for a solids emptying of the solid F or, conversely, the inflow of control fluid can be interrupted in order to move the piston slide 11 to move accordingly to release the outlet opening(s) 2.

At least one sensor device 26 can be arranged on the drive spindle 6 and/or the drum 1, which is designed to determine the current amount of the speed of the drive spindle 6 or the current speed of the drum 1 or the rotating system of the centrifuge. A sensor device 27 for determining the flow rate volume/time or one or more parameters, such as mass/time, of the starting product AP to be fed into the drum 1 can also be arranged on or in the product inlet 7 for the starting product AP into the drum 1. This is advantageous, but not mandatory.

The sensor devices 26, 27 are connected via data connections 28, 29 to an evaluation and control unit 30 (preferably a control computer for the centrifuge), which evaluates the measured values determined and the movement of the piston slide 11 and thus also the time interval until the opening of the Exhaust opening(s) 2 controls or regulates. The actuating mechanism for the piston slide 11 - here in particular the metering arrangement 24 - can be connected via a data connection 31 to an evaluation and control unit 30, which also has a program routine for controlling and / or regulating the solids outlet. The dosing arrangement 24 can, for example, be of the type DE 10 2005 049 941 A1 be designed. In addition, a further controllable device 32 - for example a controllable valve - can preferably be connected to the product inlet 7, with which the volume flow in the inlet can be changed in order to change the inlet quantity or the current inlet volume V _AP of starting product AP to be processed per unit of time . This controllable device 32 is connected to the control unit 30 via a data connection 33.

The aforementioned data connections 28, 29, 31, 33 enable data transmission from or to the control and evaluation unit. They can each be designed as lines or as wireless connections.

In Fig. 2a is an enlarged detail of the section of the drum 1, in which the outlet opening(s) 2 is shown in section. Also indicated here is a radially outer region of the drum interior, in which solid F has collected radially on the inside in front of the outlet opening 2 shown here.

The piston slide 11 is conically toroidal - and preferably also ring-shaped - and is axially movably guided in the lower drum part 3. In an upper position, it rests with an upper axial annular surface 11a on a corresponding lower axial annular surface 4a of the upper drum part 4, or on a seal which is arranged in this axial annular surface. If he is placed in a lower position - compare Figs. 2a and 2b - moves, an annular gap RS forms between these two axial annular surfaces 11a and 4a.

On an outer circumference, the piston slide 11 has a seal 13 (a sealing ring), with which the circumferential gap between the outer circumference of the piston slide 11 and the inner circumference of the lower drum part 3 is sealed.

The upper drum part 4 also has a groove 15 on its lower axial annular surface 4a, into which a sealing ring 14 is inserted. This seals in the state in which the piston slide 11 additionally closes the annular gap RS.

In order to avoid abrasive wear of the outlet opening(s) 2 when the solid F is emptied through the outlet opening(s) 2, the upper drum part 4 has at least one, two or more first wear protection elements 16 on its lower axial annular surface 4a facing the annular gap RS .

It can be provided that the drum upper part 4 has a step-like gradation or ring clearance 4b, into which these first wear protection elements 16 are inserted in a form-fitting manner. The ring clearance 4b can be dimensioned and designed in such a way that the first wear protection elements 16 form an axially flush surface with the remaining part 4c of the axial annular surface 4a that is not covered by the wear protection elements 16. In addition, according to a variant, it can advantageously be provided that the ring clearance 4b extends to the groove 15 into which the sealing ring 14 is inserted.

According to a preferred embodiment, the first wear protection elements 16 can also be designed so that they protrude a (defined) piece radially beyond the inner edge of the upper drum part 4 into the interior of the drum 1. This means that despite the solid F being emptied, a residual amount of this solid F always remains in the drum in front of the edge described, which acts like a protective layer on the upper part of the drum 4. The solid F slides on this layer during further emptying, which reduces abrasion of the affected area in the upper part of the drum.

Alternatively or optionally, it can be provided that the piston slide 11 has at least one, two or more second wear protection elements 17 on its upper axial annular surface 11a facing the annular gap RS.

The second wear protection elements 17 can be designed so that they cover the entire axial annular surface 11a of the piston slide. You can alternatively but also be designed so that they extend radially only over part of the axial annular surface 11a and only partially cover it.

It can be provided that the piston slide has a step-like ring clearance 11b at the top with an outer peripheral edge 18 into which the second wear protection elements 17 are inserted. The ring clearance 11b can be dimensioned and designed in such a way that the second wear protection elements 17 protrude axially slightly beyond the remaining partial surface 11c of the upper axial annular surface 11a of the piston slide 11, which is not covered by the wear protection elements 17. In this way, in the closed state, only the first and second wear protection elements 16, 17 lie axially against one another. In this way, the annular gap RS can continue to be closed well in this area.

The second wear protection elements 17 are designed here in such a way that they abut the peripheral edge 18. The second wear protection elements 17 can also protrude a defined distance radially beyond the inner edge of the piston slide 11 into the interior of the drum 1. This means that despite the solid F being emptied, a residual amount of this solid F always remains in the drum in front of the edge described, which acts like a protective layer on the piston slide 11. The solid F slides on this layer during further emptying, which reduces the abrasion of the affected surface in the piston slide 11.

The first and second wear protection elements 16, 17 can be designed like a plate so that they can be produced inexpensively and easily assembled.

In the closed state of the outlet opening(s) 2, the first wear protection elements 16 preferably contact the second wear protection elements 17.

Furthermore, the seal 14 rests on the second plate-like wear protection elements 17 and thus seals the interior of the drum 1 against the outlet opening(s) 2.

In Fig. 2b the outlet opening(s) 2 is/are shown in an open state. Two areas can be seen in the interior of the drum 1, to which solid F still adheres despite the outlet opening(s) 2 being open. The solid F slides on this layer during further emptying. This is advantageous because the affected surfaces of the upper drum part 4 or the piston slide 11 are additionally protected against abrasive wear, since the adhering solid layer covers the surfaces and thereby creates an advantageous protective effect.

This advantageous adhesion of solid F is achieved by the edges of the first plate-like wear protection element(s) 16 and the second plate-like wear protection element(s) 17 which protrude by a defined amount into the interior of the drum 1.

In Fig. 3a alternative embodiment of the invention is shown. Different from the version according to Fig. 2a or 2b, it is provided here that (only) the second plate-like wear protection elements 17 cover the entire outlet opening-side end of the piston slide 11 or the entire axial annular surface 11a. In this case, the second plate-like wear protection elements 17 are positively secured in the radial direction by an annular shoulder 19, 20, which is formed by the piston slide 11 and the second plate-like wear protection elements 17.

In Fig. 3b is/are the outlet opening(s) shown in an open state. Two areas can be seen in the interior of the drum 1, to which solid F still adheres despite the outlet opening(s) 2 being open. This advantageous adhesion of solid F is achieved by the edges of the first plate-like wear protection element(s) 16 and the second plate-like wear protection element(s) 17 which protrude by a defined amount into the interior of the drum 1. This causes the affected surfaces of the Drum upper part 4 or the piston slide 11 are additionally protected against abrasive wear, since the adhering solid layer covers the surfaces and thereby creates an advantageous protective effect.

In Fig. 4 1 shows how the second plate-like wear protection elements 17 are arranged along the circumference of the axial end of the piston slide 11.

Analogously, the following also applies to the first plate-like wear protection elements 16, which are arranged along the circumference of the upper drum part 4 (not shown here).

In order to be able to follow the annular contour of the piston slide 11 or the upper drum part 4, the wear protection elements have the shape of circular ring segments. When lined up together, they form a circular ring. As a result, the wear protection elements 17 can advantageously be produced cost-effectively without large amounts of waste.

Each wear protection element 17 has abutting edges 21 together with the respective adjacent wear protection elements 17.

The abutting edge 21 is designed in such a way that the abutting edge 21 follows the first radial R1 starting from a tangent point T, which forms a first radial R1 with the circular arc of the circumference of the outlet opening-side end of the piston slide 11, and thus forms at least a first radial section r1. The first radial section r1 is adjoined by at least a first angle section w1 which extends at an angle α to the first radial section r1.

The abutting edge 21 is further designed such that each further radial section r is part of a further radial R, which runs through the respective end point E of the preceding angular section w or is a parallel to the first radial R1.

In the example the abutting edge 21 follows Fig. 4 the abutting edge 21 each has three radial sections r1, r2, r3 and two angular sections w1, w2. The number of radial sections r and angular sections w can also differ.

The length of the respective sections r, w results from the length of the abutting edge 21 and the choice of the amount and the opening direction - here clockwise Angle α and is therefore variable, with an abutting edge 21 with at least two angle sections w being preferred.

The abutting edge 21 therefore has an alternating arrangement of one or more radial section(s) r and angular section(s) w.

The respective abutting edge 21 therefore has a wavy or zigzag-like contour, in such a way that adjacent wear protection elements 17 can be lined up in a form-fitting manner.

This has the effect that the radially emerging abrasive solid particles do not follow a joint that forms the respective abutting edge 21 between two wear protection elements 17, but are advantageously braked by the wavy or zigzag-like course of the abutting edge 21 and thus do not expand the joint can be further polished.

The wave or zigzag shape of the abutting edge 21 also enables the abrasive solid particles to settle in the joint, which results in further advantageous protection of the abutting edge 21 from further abrasive expansion of the joint.

The wear protection elements 16, 17 are made of a hard, wear-resistant material. However, the choice of materials is limited with regard to the acting centrifugal forces, so technical ceramics or hard metal are preferred.

The wear protection elements 16, 17 are each fastened to the piston slide 11 or to the upper drum part 4 by a cohesive joining process. Preferred joining methods are welding, soldering or gluing.

Reference symbol list

1

drum

2

Exhaust opening

3

drum base

4

Drum top

4a

Axial ring surface

4b

Ring clearance

4c

partial area

5

Hood

6

Drive spindle

7

Product inflow

8th

Sequence

9

Plate package

10

Solids collection room

11

Piston valve

11a

Axial ring surface

11b

Ring clearance

11c

partial area

12

solids catcher

13

poetry

14

poetry

15

Nut

16

Wear protection element

17

Wear protection element

18

Circumferential edge

19

Ring heel

20

Ring heel

21

abutting edge

22

supply line

23

Valve arrangement

24

Dosing arrangement

25

Hydraulic line

26

Sensor device

27

Sensor device

28

Data Connection

29

Data Connection

30

Control unit

31

Data Connection

32

Controllable device

33

Data Connection

CP

Clear phase

AP

Starting product

F

solid

D

Axis of rotation

RS

Annular gap

R, R1, R2

Radial

R, r1, r2, r3

Radial section

T

Tangent point

E

end point

w, w1

angle section

α

angle

U

Direction of rotation

Claims (18)

1. Centrifuge in which a flowable starting product (AP) can be clarified of solids F in a continuous operation in a centrifugal field in a rotating drum (1), wherein the drum (1) has a drum top part (4) and a drum bottom part (3), and wherein the drum top part (4) or the drum bottom part (3) has a movable piston valve (11) through which outlet openings (2) in the drum (1) can be opened or closed, wherein furthermore one or more wear protection elements are provided for protection against abrasive wear, characterized by one or both of the following features a) or b) and by feature c):

   a. the drum is provided with two or more first wear protection elements (16) on an axial annular surface (4a) of the drum top part (4) or the drum bottom part, wherein the first wear protection elements (16) have the shape of circular ring segments, and/or

   b. the piston valve (11) is provided with two or more second wear protection elements (17) on a corresponding axial annular surface (11a), wherein the second wear protection elements (17) are in the shape of circular ring segments,

   c. wherein each of the wear protection elements (16 or 17), together with one or two respectively adjacent wear protection elements (16 or 17), has a respective abutting edge (21), so that a joint is formed between abutting edges resting against one another.
2. Centrifuge according to claim 1, characterized in that the first and/or second wear protection element(s) (16, 17) is/are designed to cover the entire axial annular surface (4a, 11a) of the component on which they are arranged.
3. Centrifuge according to claim 1, characterized in that the first and/or second wear protection element(s) (16, 17) is/are designed to cover only a part of the axial annular surface (4a, 11a) of the component on which they are arranged.
4. Centrifuge according to claim 3, characterized in that the first and/or second wear protection element(s) (16, 17) is/are designed to cover only a radial part of the axial annular surface (4a, 11a) of the component on which they are arranged.
5. Centrifuge according to claim 2 or 3, characterized in that the first and/or second wear protection element(s) (16, 17) is/are designed to cover only individual circumferential sections of the axial annular surface (4a, 11a) of the component on which they are arranged, so that they do not form a circumferentially closed ring.
6. Centrifuge according to one of the preceding claims 1 to 5, characterized in that the first and/or second wear protection element(s) (16, 17) jointly form in interaction a circumferentially closed ring.
7. Centrifuge according to one of the preceding claims 1 to 6, characterized in that the first and/or second wear protection element(s) (16, 17) is/are arranged in a positive-locking manner on the component whose surface they cover completely or partially.
8. Centrifuge according to one of the preceding claims 1 to 7, characterized in that the component is the drum top part (4) and/or the piston valve (11) or both.
9. Centrifuge according to one of the preceding claims, characterized in that the wear protection elements (16, 17) are designed in the form of plates.
10. Centrifuge according to one of the preceding claims, characterized in that the drum top part (3) has at least two first wear protection elements (16) and/or the piston valve (11) has at least two second wear protection elements (17).
11. Centrifuge according to one of the preceding claims, characterized in that the one or more joints extend radially in sections in any case.
12. Centrifuge according to one of the preceding claims, characterized in that the one or more joints do not extend radially in sections or in their entirety.
13. Centrifuge according to one of the preceding claims, characterized in that the respective abutting edge (21) between two wear protection elements (16 or 17) has a wave-like or zigzag-like contour in such a way that adjacent wear protection elements (16 or 17) can be arranged in a row in a positive-locking manner.
14. Centrifuge according to one of the preceding claims, characterized in that the first wear protection elements (16) and the second wear protection elements (17) are designed in such a way that they each project a defined amount radially over the inner edge of the drum top part (4) or piston valve (11) into the interior of the drum (1).
15. Centrifuge according to one of the preceding claims, characterized in that the wear protection elements (16, 17) are made of a hard, wear-resistant material.
16. Centrifuge according to one of the preceding claims, characterized in that the wear protection elements (16, 17) are made of technical ceramics or hard metal.
17. Centrifuge according to one of the preceding claims, characterized in that the wear protection elements (16, 17) are each fixed to the piston valve (11) or to the drum top part (4) by a material-bonding joining process.
18. Centrifuge according to one of the preceding claims, characterized in that a disk stack (9) is arranged in the drum (1) and/or that it has a vertical axis of rotation (D).

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