EP1831570B1 - Pump, especially slurry pump - Google Patents

Description

The invention relates to a pump, in particular sludge pump, with a rotating in a housing driven rotor.

For pumping thick materials with contained large-grained, abrasive fractions such. B. concrete so far mainly piston pumps with two delivery cylinders are used, in which run by hydraulic cylinder delivery piston reciprocally perform suction and pressure strokes, with each change from suction to pressure stroke dependent on the switching time and the degree of filling of the delivery cylinder interruption of promotion takes place.

For the mutual connection of the delivery cylinder with a supply container or with the delivery line slides of different types are used, which are also moved by hydraulic cylinders. The coordination of the pumping process requires a comparatively large control effort in this type of pump. Due to the unsteady movement of the hydraulic cylinder and consequently also the pump elements driven therewith, an unsteady conveyance of the conveyed material, which is interrupted with each change from the suction to the printing stroke, necessarily takes place. The discontinuity also results in an impulsive acceleration and deceleration of the moving pumping elements and of the pumped conveyed material taking place in accordance with the pumping cycle, in constant change. As a result, all components incorporated and connected in the pumping train are subjected to a cyclic impact load.

Concrete is usually pumped on construction sites via so-called concrete distribution booms, which are stationary or mounted on roads suitable chassis, pumped to the point of application. Here, the pumping characteristic described causes a swinging of the boom, from which at the end, ie at the exit point of the concrete, movements arise whose extent, increasing with increasing mast length, endanger the working in this area people and the introduction of the concrete to the utmost make it difficult, even impossible. By running according to the pumping cycle accelerations results mainly from the mass of the conveyed Increasing length of the delivery line increasingly increased energy consumption for the drive.

Various devices have been disclosed which reduce the described disadvantages of piston pumps. However, this is always associated with considerable additional effort and also increases the risk of malfunction.

Another type of pump used to convey such thick materials as concrete is the so-called peristaltic pump. It is characterized by a simple, rotationally continuous drive. Due to the design results for the peristaltic pump a considerably lower discontinuity in the promotion than in the previously described piston pump. However, their use is limited to comparatively low discharge pressures (up to 30 bar), which severely restricts their use in the pumping of thick materials.

The EP 0 799 996 shows a pump in the manner of a Wankel engine with a rotary piston. In this case, two suction openings and two discharge openings are provided on the circumference of a trochoidal housing having at the narrowest point stationary sealing or separating strips to separate the suction from the discharge openings. The rotary piston in this case has a curved outer surface to ensure the required seal. As a result, however, the production is complicated, especially since the stationary sealing strips are required, which are also exposed to high wear.

The invention is based on the object, a new positive displacement pump, in particular for use as a slurry pump for pumping non-homogeneous, abrasive media such. As concrete, with the simple construction of the adverse properties of the pump types described above can be repealed or largely avoided and additional benefits are given for use.

The object is achieved by a pump according to the features of claim 1.

The designed as a prism-like body rotor, in which at least the connecting lines of the corners of the bases form an equilateral polygon, generated with its longitudinal edges during its rotation about its, simultaneously moved on a circular path center axis, the longitudinal inner wall surface of the housing.

If a rigid longitudinal housing wall is assumed, the rotor, whose center axis passes through a full circle, must be rotated about the central angle of the equilateral polygon formed by the connecting straight lines of the corners of the base areas of the prismatic body. It follows that the shape of the longitudinal inner wall surface of the housing is determined by the number of longitudinal edges of the prismatic body.

By the continuous contact of the longitudinal edges of the prismatic body with the longitudinal inner wall surface of the housing are thereby with the longitudinal inner wall surface of the housing and the longitudinal outer wall surfaces of the prismatic body, in conjunction with the inner wall surfaces of the two end walls of the housing, constantly changing Formed spaces in which the media to be pumped, especially thick materials such as concrete, are promoted.

The circular motion of the center axis of the rotor is generated by its storage on the eccentric of the, mounted in the end walls of the housing, driven eccentric shaft. The rotation of the rotor about its center axis according to the described regularity can be enforced with various gears.

• Das erste Getriebe wird durch ein, auf der Zentrumsachse des Rotors rotorfest angeordnetes Hohlzahnrad, das mit einem, auf der Achse der Exzenterwelle angeordneten, an einer Stirnwand des Gehäuses festen Zahnritzel kämmt, gebildet. Bei diesem Getriebe ist das Maß für die Exzentrizität durch die beschriebene Getriebestufe und deren Gesetzmäßigkeit festgelegt.
• Das zweite Getriebe besteht aus einem, auf der Zentrumsachse des Rotors angeordneten Planetengetriebe, dessen Sonnenrad rotationsfest auf dem Exzenter der Exzenterwelle befestigt ist, dessen Planetenräder rotationsfrei auf dem rotorfesten Planetenträger gelagert sind, dessen Hohlrad rotationsfrei auf dem Exzenter der Exzenterwelle gelagert und über eine Kreuzkoppel rotationsfest an einer Stirnwand des Gehäuses abgestützt ist. Durch die Abstützung des Hohlrades über die Kreuzkoppel am Gehäuse wird erreicht, dass das Hohlrad nur noch eine "Kreisschiebung" genannte Bewegung ausführt. Das Getriebe entspricht so einem Planetengetriebe mit Antrieb über Sonnenrad, Abtrieb über Planetenträger, und gehäusefestem Hohlrad. Bei diesem Getriebe kann das Maß für die Exzentrizität vom Prinzip her frei gewählt werden.

Here are two examples of gears to be described:

• The first gear is formed by a, on the center axis of the rotor rotorfest arranged hollow gear, which meshes with a, arranged on the axis of the eccentric shaft, fixed to an end wall of the housing pinion. In this gear, the measure of the eccentricity is determined by the gear stage described and its legality.
• The second transmission consists of one, arranged on the center axis of the rotor planetary gear, the sun gear is fixed rotationally fixed to the eccentric of the eccentric shaft, the planet gears are rotatably mounted on the rotorfesten planet carrier, the ring gear rotatably mounted on the eccentric of the eccentric shaft and rotationally fixed via a cross coupling is supported on an end wall of the housing. By supporting the ring gear on the cross coupling on the housing is achieved that the ring gear only performs a "circular shift" movement mentioned. The gear corresponds to a planetary gear with drive via sun gear, output via planet carrier, and fixed housing ring gear. In this gear, the degree of eccentricity principle can be chosen freely.

For the control of the supply and the delivery of the conveyed no valves are required. On the longitudinal side wall of the housing are alternately provided at least one opening for the supply and one for the delivery of the conveyed material. there must be given that on the longitudinal inner wall surface of the housing in each case the end of a feed opening and the beginning of a discharge opening and the end of a discharge opening and the beginning of a feed opening, with respect to the respective center of the rotor to the central angle of, from the connecting line of the Corners of the base surfaces of the prismatic body formed, equilateral polygon are offset. Maintaining the above law for the arrangement of the feed and discharge openings to each other, their position on the longitudinal inner wall surface of the housing can be chosen freely in principle.

The location of the feed and discharge ports, in conjunction with the length of the prismatic body, determines the geometric displacement of the pump. Therefore, in order to obtain the largest possible flow rate, it is necessary to set the position of the supply and discharge openings so that the value for the geometric displacement becomes maximum.

In a reversal of the direction of rotation of the rotor, the direction of the flow is reversed. Thus, the possibility of return promotion is given. If a pentagonal prism is selected for the rotor, two supply and discharge openings can alternately be provided on the longitudinal housing wall. It then results in accordance with two pump cycles at a full rotation of the rotor.

As the number of corners for the prismatic body of the rotor increases, so does the number of possible supply and discharge openings and, correspondingly, the number of pumping cycles for a full rotation of the rotor according to a certain law. The pulsation of the delivery stream decreases as the number of pump cycles present during a full rotation of the rotor increases.

Due to the above fact, the application of this pump principle is also for the pumping of homogeneous liquids in other applications such. interesting in the chemical industry. Furthermore, the application in hydrostatics in hydraulic pumps and hydraulic motors offers.

In the application of the pump principle for positive displacement pumps, which is used to pump thick materials containing large-particle abrasive particles such as concrete are provided, it is appropriate to achieve a maximum geometric volume with the smallest possible dimensions to provide the rotor a triangular or square prism. Because of the law for the arrangement of the supply and discharge openings only one pumping cycle is possible here with one full rotation of the rotor.

An uninterrupted flow with only slight accelerations and delays for the conveyed material is achieved here by the arrangement of at least two pump units parallel to each other, which are coupled via their eccentric shafts offset by a certain angular extent.

On the sludge pump, in particular in its execution as a concrete pump, a feed container angeaut.sein, wherein the sludge pump is arranged so that their feed opening (s) in the feed container are below the lowest level of the filled conveyed.

Arranged in the rotor, preferably on the center axis thereof, is a preferably cylindrical intermediate wall which radially surrounds the gear described and which extends to the inner wall surfaces of the two end walls of the housing. It is advantageous to determine the radial position of the intermediate wall in connection with the definition of the rotor dimensions so that swept over by the end faces of the intermediate wall surfaces outside of the end faces of the, the longitudinal outer wall surfaces of the prismatic body forming outer walls of the rotor swept Areas lie.

The space formed by the long-side inner wall surfaces of the outer walls of the prism-like body and the long-side outer wall surfaces of the intermediate wall in communication with the inner wall surfaces of the two end walls of the housing is provided as a washing chamber. The supply and removal of the rinsing liquid can be done either via the frontal walls of the housing or over, through the eccentric shaft and the rotor leading lines.

On the front side of the outer walls of the longitudinal outer wall surfaces of the prism-like body forming outer walls are rubber-elastic elements with high

Provided wear resistance, which touch the inner wall surfaces of the two end walls of the housing. Thereby, the entire inner space, which is formed by the longitudinal inner wall surfaces of the outer walls of the prismatic body in connection with the inner wall surfaces of the two end walls of the housing, sealed against the ever-changing delivery chambers.

The rubber-elastic elements are preferably vulcanized or glued. For the strength of the connection between the rubber-elastic elements and the surfaces of the metallic walls, it is advantageous if the size of the connecting surfaces is increased by the fact that the rubber-elastic elements extend beyond the end faces on the longitudinal outer wall surfaces of the outer walls of the prismatic body. In addition, this eliminates a high wear resistance of the longitudinal outer wall surfaces of the metallic outer walls. With such a design, there is also the possibility for a better, tailored to the overall function shaping of rubber-elastic elements.

On the rotor, on the longitudinal edges of the prism-like body sealing strips separate by their constant contact with the longitudinal inner wall surface of the housing, the pumping chambers from each other or seal against each other. The sealing strips are preferably held interchangeably on the longitudinal edges of the prismatic body. They are made of highly wear-resistant and hard material, as they also run over the feed and discharge openings on the longitudinal inner wall surface of the housing with their end faces and thereby cut through the fluid.

In particular, the weather strips may be received and held in a groove machined in the longitudinal edges of the prismatic body. For this purpose, on the longitudinal edges of the prismatic body additionally reciprocally incorporated and filled with vulcanized or glued rubber elastic material recesses may be present, so that when they are acted upon by the pressure of the pumped medium held in the grooves incorporated sealing strips are pressure-dependent pressed against the longitudinal side inner wall surface of the housing ,

On the rotor and on the end faces of the preferably cylindrical intermediate wall sealing elements and in particular also guide elements are provided which the touch inner wall surfaces of the two end walls of the housing. Characterized the, radially enclosed by the inner wall surface of the intermediate wall, formed in connection with the inner wall surfaces of the two end walls of the housing space is sealed against the space used as a rinsing chamber.

The sealed spaces facing sides of the sealing elements are expediently equipped with very good wiping action, so that on the inner wall surfaces of the frontal walls of the housing adhering fine-grained and abrasive particles are reliably stripped off. On the rotor, the longitudinal outer walls of the prism-like body are formed by a plurality of, preferably identical, individual elements, which are releasably secured to a base body, which is composed of the other elements of the rotor. For the arrangement of the intended sealing elements, it is advantageous to assemble the outer walls of angle elements.

In a further embodiment for the rotor, the longitudinal outer walls of the prism-like body are formed by an undivided element, which is releasably secured to a base body composed of the remaining elements of the rotor. In the one-piece design of the longitudinal outer walls of the prismatic body no separation points are present, which complicate the seal between the delivery chambers and the interior of the rotor. Furthermore, a simpler assembly of the rotor is given by the one-piece element.

At the pump housing, the inner wall surface of the longitudinal housing wall is formed wear-resistant and / or equipped with a wear-resistant coating, so that the removal in the promotion of abrasive media such. B. concrete is kept as low as possible. On the inner sides of the two end walls of the housing, releasably secured plates are provided, at least in the area of swept by the front-side sealing elements and guide elements of the rotor surfaces. The inside surfaces of the plates serve as a mating surface for the sealing elements and guide elements of the rotor and at the same time form the frontal boundaries of the constantly changing delivery chambers and the rinsing chamber. This requires a very smooth and wear-resistant surface, which is preferably produced by a coating, in particular by hard chrome plating. The pump housing is formed from a longitudinal wall and two detachably connected end walls.

With the above division of the pump housing results in a simple construction. The shape of the inner surface of the longitudinal housing wall results from the path of the longitudinal edges of the prismatic body during its movement in accordance with the described regularity. In the longitudinal housing wall, the supply and discharge openings for the conveyed material are arranged.

The front-side housing walls are preferably screwed via a flange with the longitudinal housing wall. In the center of the frontal housing walls, the bearings for the eccentric shaft are arranged. On the eccentric shaft, the diameter of the eccentric is expediently made larger than the, increased by twice the amount of eccentricity, the largest shaft diameter. With such an embodiment, a simple production for the eccentric shaft and also a simple assembly for the rotor is given.

The bearings and the gear teeth, as well as the front-side sealing elements and guide elements on the rotor are supplied to minimize the wear of at least one central lubrication system with lubricants. At all lubrication points on the rotor, the lubricants are supplied via lines guided by the eccentric shaft.

In a preferred embodiment of the pump as a thick matter pump, the rotor is designed as a prism-like body, in which at least the connecting straight lines of the corners of the base surfaces form an equilateral triangle. With a rotor designed in this way, compared to rotors with a polygonal prism-like body, the largest possible delivery volume with comparable rotor dimensions or with a given delivery volume results in the lowest comparable rotor dimensions. As a comparison measure here the diameter of the circumference of, formed from the connecting lines of the corners of the base surfaces of the prismatic body apply.

If arc-shaped bulges are preferably provided on the rotor on the longitudinal outer walls of the prism-like body in their middle region, the space for the gear arranged in the rotor can be greater than through the connecting straight line of the rotor Defined corners of the prism-like body, trained. Due to the described bulges and the ineffective for the delivery volume proportion of space is reduced in the delivery areas.

• einfacher Aufbau ohne Ventile (Schieber);
  keine Steuerung für den Pumpprozess;
  einfacher rotatorisch kontinuierlicher Antrieb;
• nahezu vollständige Füllung der Förderräume;
• ununterbrochener Förderstrom mit vergleichsweise geringen Beschleunigungen für das Fördergut;
  geringerer zusätzlicher Energieaufwand als bei Kolbenpumpen;
• Förderdrücke wie bei den Kolbenpumpen;
• Kompakte Bauweise für die Pumpeneihheit, dadurch geringerer kompakter Einbauraum

As an advantage over the prior art arise for the pump described above:

• simple construction without valves (slide);
  no control for the pumping process;
  simple rotary continuous drive;
• almost complete filling of the pumping rooms;
• uninterrupted flow with comparatively low accelerations for the conveyed material;
  lower additional energy expenditure than with piston pumps;
• Delivery pressures as with the piston pumps;
• Compact design for the pumping, thus less compact installation space

When used as a concrete pump resulting in their construction together with a distribution boom on a roadworthy chassis through the compact design and lower weight of the pump unit better options for the design of the distribution boom substructure and a larger proportion of the gross weight for the entire distribution boom.

Fig. 1

eine Dickstoffpumpe im Querschnitt;

Fig. 2

eine Dickstoffpumpe im Längsschnitt;

Fig. 3

eine besondere Ausführungsform des Rotors im Querschnitt;

Fig. 4

eine Detaildarstellung des Eckbereiches eines Rotors im Querschnitt;

Fig. 5

schematische Darstellung des Getriebes nach Anspruch 3 (Längsschnitt)

Fig. 6

schematische Darstellung des Getriebes nach Anspruch 4 (Längsschnitt, Draufsicht auf Kreuzkoppel)

Hereinafter, several embodiments are explained and described with reference to the drawings. Hereby show:

Fig. 1

a slurry pump in cross section;

Fig. 2

a sludge pump in longitudinal section;

Fig. 3

a particular embodiment of the rotor in cross section;

Fig. 4

a detailed representation of the corner region of a rotor in cross section;

Fig. 5

schematic representation of the transmission according to claim 3 (longitudinal section)

Fig. 6

schematic representation of the transmission according to claim 4 (longitudinal section, top view of cross coupling)

Fig. 1 shows a slurry pump 1 with a designed as a triangular prism rotor 4 and the longitudinal side wall of the housing 2 in cross-section shown schematically.

Several rotor positions are indicated, wherein it can be seen that the longitudinal edges of the triangular rotor prism 4 'always touch the longitudinal inner wall surface 2' of the housing 2. By the longitudinal side inner wall surface 2 'of the housing 2 and the longitudinal outer wall surfaces of the rotor prism 4 "are formed in conjunction with the inner wall surfaces of the two end walls of the housing 2, the steadily changing with the rotor position delivery chambers (F).

In the center of the rotor 4, a transmission 5 is arranged. The longitudinal wall of the housing 2 is interrupted once each by an opening for the supply (Z) and an opening for the delivery (A) of the conveyed. Furthermore, it is shown how the thick matter pump 1 immersed in its installed position with the feed opening in the pumping medium (possibly in a feed container). Upon rotation of the rotor 4 in a clockwise direction results here a promotion of the feed opening to the discharge opening; with opposite rotation, the promotion results from the discharge opening to the feed opening.

In Fig. 2 is a slurry pump according to Fig. 1 shown in longitudinal section. In the center of the housing 2, an eccentric shaft 3 is mounted with its eccentric 3a in the front-side housing walls 2b. It is powered by a motor. On the eccentric 3a of the eccentric shaft 3, the rotor 4 is mounted. It is made up of, arranged in the center hub for receiving the bearing 4a, a web 4a with a centrally arranged intermediate wall 6 and the also centrally arranged, at the web via screw fastened element 4b, with the longitudinal outer walls of the rotor Prismas are formed, together.

Through the inner wall surfaces of the longitudinal outer walls of the rotor prism and the longitudinal outer wall surfaces of the intermediate wall, the flushing chamber (S) is formed in connection with the inner wall surfaces of the two end walls of the housing. On the end faces and outer wall surfaces of the longitudinal outer walls of the rotor prism 4 'rubber-elastic elements 7a are vulcanized. On the longitudinal edges of the rotor prism 4 'also sealing strips 4c are arranged. In the end faces of the partition sealing elements and guide elements 7b are inserted into correspondingly incorporated grooves.

The intermediate wall 6 also serves to receive and fix the likewise centrally arranged in the rotor 4 ring gear 5b, which engages in the, arranged on the axis of rotation of the eccentric shaft 3, attached to the frontal housing wall 2b pinion 5a. In the hub of the housing-fixed pinion 5a here a bearing for the eccentric shaft 3 is arranged.

The housing 2 is composed of a longitudinal side wall 2a and two end walls 2b. The end walls 2b are bolted to the longitudinal side wall 2a via a flange connection. The inside wall surface of the longitudinal housing wall 2a is here equipped with a particularly hard and wear-resistant lining, on the surface of the front surfaces of the, arranged on the longitudinal edges of the rotor prism sealing strips 4c slide. The lining is replaceable fastened. On the inner sides of the front-side housing walls 2b wear plates 8 are mounted interchangeable with a hard surface and high surface quality, they serve as mating surfaces for the end-side sealing elements and guide elements 7a, 7b on the rotor 4th

In Fig. 3 the contour of the longitudinal outer walls of a triangular rotor prism for a preferred embodiment of the rotor 4 is shown. The advantage of formed with such bulges, longitudinal outer walls in a triangular rotor prism is in the enlargement of the space for the enclosed therein gear 5 while reducing the ineffective for the volume volume space in the delivery chambers.

Fig. 4 shows in a detailed representation of a possible embodiment for the corner region in a triangular rotor prism. The sealing strip 4c is held here in a, in the longitudinal edge of the rotor prism 4 'incorporated groove. On one side is shown in cross-section one of the mutually incorporated, filled with elastomeric material recesses 4 '"and one of the vulcanized on the longitudinal outer walls of the rotor prism 4' rubber-elastic elements 7a.

In Fig. 5 is a pump according to Fig. 1 with a transmission 5 according to claim 3 shown schematically in longitudinal section. The diagram shows all the main parts of the pump such as the housing 2, the eccentric shaft 3, the rotor 4 and in particular the elements of the transmission 5 according to claim 3. It can be seen that on the axis of the Eccentric shaft 3 arranged in the center of the housing 2 fixed housing pinion 5a with the arranged on the center axis of the eccentric 3a and the mounted on the eccentric 3a rotor 4, rotor-fixed ring gear 5b meshes (as in Fig. 2 shown).

In Fig. 6 is a pump according to Fig. 1 with a transmission according to claim 4 in longitudinal section and partially in plan view shown schematically. The schematic diagram contains as in Fig. 5 all main parts of the pump 1 and in particular here the elements of the transmission 5 according to claim 4. In this case, the planetary gear arranged on the center axis of the eccentric 3a and of the eccentric 3a mounted rotor 4 can be seen. The sun gear 5c is rotationally fixed on the eccentric 3a of the eccentric shaft 3; the planet gears 5d are rotatably mounted on the rotor-fixed planetary carrier 5e. The ring gear 5f is rotatably mounted on the eccentric 3a of the eccentric shaft 3 and connected via its hub with the guide rod of a cross coupling 5g. It can not perform rotation about the center axis of the eccentric 3a by this connection and is supported by the cross coupling 5g on the housing 2. The cross coupling (5g) is separate in the right half of Fig. 6 also shown schematically in a plan view.

Claims (24)

1. Pump, in particular a slurry pump, comprising a rotor (4) driven so as to rotate in a case (2), wherein the rotor (4) is constructed as a polygonal prismatic body in which at least the connecting lines of the corners of the base surfaces form an equilateral polygon, and which performs a rotational movement about an orbiting centre axis, with the longitudinal edges of the prismatic body (4') touching the longitudinal inner wall surface (2') of the case (2),
   characterised in that the rotor (4) is mounted on the eccentric (3a) of an eccentric shaft (3) so as to be rotation-free, such that the centre line of the eccentric (3a) coincides with the centre axis of the rotor (4) and when the eccentric shaft (3) revolves is rotated by a gearing (5) about an angle which corresponds to the central angle of the equilateral polygon formed by the connecting lines of the corners of the base surfaces of the prismatic body, and alternately provided on the longitudinal wall of the case (2) are at least one respective opening for supplying the material to be conveyed (Z) and one opening for discharging the material (A) to be conveyed, wherein arranged on the longitudinal inner wall surface of the case (2') are in each case the end of a supply opening (Z) and the start of a discharge opening (A) and the end of a discharge opening (A) and the start of a supply opening (Z) offset in relation to the respective centre of the rotor (4) by the central angle of the equilateral polygon formed by the connecting lines of the corners of the base surfaces of the prismatic body.
2. Pump according to claim 1, characterised in that the gearing (5) is formed by a rotor-secured hollow toothed wheel (5b) which is arranged on the centre axis of the rotor (4) and a case-secured pinion (5a) arranged on the rotational axis of the eccentric shaft (3).
3. Pump according to claim 1, characterised in that the gearing (5) is formed by a planetary gearing arranged on the centre axis of the rotor (4), and of which the sun wheel (5c) is fastened to the eccentric (3a) of the eccentric shaft (3) so as to be rotation-free, of which the planetary wheels (5d) are mounted on the rotor-secured planet carrier (5e) so as to be rotation-free, of which the internal gear (5f) is mounted on the eccentric (3a) of the eccentric shaft (3) so as to be rotation-free and is supported by a cross coupler (5g) on an end wall of the case (2) so as to be secured against rotation.
4. Pump according to any one of claims 1 to 3, characterised in that a plurality of pump units (1) are arranged parallel and side-by-side and, coupled to each other by their eccentric shafts (3), are driven by one or more drive(s) via the free ends of the eccentric shafts (3).
5. Pump according to any one of claims 1 to 3, characterised in that two pump units (1) are arranged parallel and side-by-side and are coupled and driven by a drive arranged between the pump units, via the eccentric shafts (3).
6. Pump according to claim 4 or 5, characterised in that a plurality of pump units (1) are arranged parallel and side-by-side and their eccentric shafts (3) are coupled so as to be offset by a specific angular measurement.
7. Pump according to any one of claims 1 to 6, characterised in that in the rotor (4), preferably on the centre axis thereof, there is arranged a partition wall (6) which radially surrounds the gearing (5) and extends to the inner wall surfaces of the two end walls of the case (2).
8. Pump according to any one of claims 1 to 7, characterised in that provided on the rotor (4), on the end faces of the outer walls forming the longitudinal outer wall surfaces of the prismatic body, are elastic, wear-resistant elements (7a) which touch the inner wall surfaces of the two end walls of the case (2).
9. Pump according to claim 8, characterised in that the elastic, wear-resistant elements (7a) provided on the end faces of the outer walls of the rotor (4) forming the longitudinal outer wall surfaces of the prismatic body are vulcanised or glued on and extend beyond the end faces of the outer walls even on the longitudinal outer wall surfaces of the outer walls.
10. Pump according to any one of claims 1 to 9, characterised in that sealing strips (4c) are arranged on the rotor (4) on the longitudinal edges of the prismatic body (4').
11. Pump according to claim 10, characterised in that the sealing strips (4c) on the longitudinal edges of the prismatic body (4') are replaceable and are made from a highly wear-resistant, hard material.
12. Pump according to claims 10 and 11, characterised in that the sealing strips (4c) are received and held in a groove worked into the longitudinal edges of the prismatic body (4').
13. Pump according to claim 12, characterised in that alternating recesses (4") are also worked into the longitudinal edges of the prismatic body (4') and are filled with vulcanised-on or glued-on, elastic, wear-resistant material.
14. Pump according to claim 7, characterised in that provided on the rotor (4) at the end faces of the partition wall (6) are sealing elements (7b) and in particular also guide elements which touch the inner wall surfaces of the two end walls of the case (2).
15. Pump according to any one of claims 1 to 14, characterised in that on the rotor (4) the longitudinal outer walls of the prismatic body (4') are formed by individual elements (4b) releasably fastened to a base body (4a).
16. Pump according to any one of claims 1 to 14, characterised in that on the rotor (4) the longitudinal outer walls of the prismatic body (4') are formed by an element (4b) which is releasably fastened to a base body (4a).
17. Pump according to any one of claims 1 to 16, characterised in that the inner wall surface (2') of the longitudinal wall of the case (2) is wear-resistant and/or is equipped with a wear-resistant coating.
18. Pump according to any one of claims 1 to 17, characterised in that provided on the inner sides of the two end walls of the case (2), at least in the region of the surfaces brushed over by the end-face sealing elements (7a, 7b), are releasably fastened plates (8) which have a wear-resistant surface.
19. Pump according to claim 18, characterised in that the plates (8) are coated, in particular hard-chromium plated.
20. Pump according to any one of claims 1 to 19, characterised in that the case (2) is formed by a longitudinal wall (2a) and two end walls (2b) releasably connected thereto.
21. Pump according to any one of claims 1 to 20, characterised in that at the eccentric shaft (3) the diameter of the eccentric (3a) is at least as large as the largest shaft diameter enlarged by twice the amount for the eccentricity (e).
22. Pump according to any one of claims 1 to 21, characterised in that the bearings and the gear teeth as well as the sealing and guide elements (7a, 7b) are fed by a central lubricating unit, in particular with conduits (9) leading through the eccentric shaft (3) and the rotor (4).
23. Pump according to any one of claims 1 to 22, characterised in that the rotor (4) is constructed as a prismatic body (4'), in which at least the connecting lines of the corners of the base surfaces form an equilateral triangle.
24. Pump according to claim 23, characterised in that the longitudinal outer walls of the prismatic body (4') have arc of a circle-shaped bulges in their middle region.

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