EP2565454B1 - Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität - Google Patents

Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität Download PDF

Info

Publication number
EP2565454B1
EP2565454B1 EP11179881.5A EP11179881A EP2565454B1 EP 2565454 B1 EP2565454 B1 EP 2565454B1 EP 11179881 A EP11179881 A EP 11179881A EP 2565454 B1 EP2565454 B1 EP 2565454B1
Authority
EP
European Patent Office
Prior art keywords
liner
rotor
displacement pump
rotary displacement
scraper gate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11179881.5A
Other languages
English (en)
French (fr)
Other versions
EP2565454A1 (de
Inventor
Sven-Eric Will
Eric Mayer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Watson Marlow GmbH
Original Assignee
Watson Marlow GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Watson Marlow GmbH filed Critical Watson Marlow GmbH
Priority to EP11179881.5A priority Critical patent/EP2565454B1/de
Priority to PCT/EP2012/066193 priority patent/WO2013030025A2/en
Priority to US14/241,225 priority patent/US20140301878A1/en
Publication of EP2565454A1 publication Critical patent/EP2565454A1/de
Application granted granted Critical
Publication of EP2565454B1 publication Critical patent/EP2565454B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/22—Rotary-piston machines or pumps of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth-equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F04C13/002—Pumps for particular liquids for homogeneous viscous liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C2/3568—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member with axially movable vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/40—Properties
    • F04C2210/44—Viscosity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/02—Glass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08—Thermoplastics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/14—Self lubricating materials; Solid lubricants

Definitions

  • the present invention relates to a rotary displacement pump for pumping flowable, relatively viscous materials.
  • a rotary displacement pump which allows for pumping flowable, relatively viscose materials in the food stuff industry, the chemical and biochemical industry, the medical industry and the cosmetic industry.
  • materials that can be pumped by such rotary displacement pump are yoghurt, soup, sauce, mayonnaise, fruit juice, cheese material, chocolate, paint, cosmetic cream, and lipstick material.
  • a rotary displacement pump shall be capable for pumping flowable, relatively viscose materials in the food stuff industry, the chemical and biochemical industry, the medical industry and the cosmetic industry.
  • MANUAL - TECHNICAL DOCUMENTATION MASO-SINE-PUMP MR 160 ANNOUNCEMENT SUNDYNE, 1 January 2003 (2003-01-01)
  • XP001219572 discloses a special kind of pump, namely a Maso-Sine-pump MR 160.
  • this document shows the assembly steps of such pump by means of a number of pictures on pages 16 and 17, and on the following two pages it shows a sectional view and a part and number list for such pump.
  • US 4 226 762 discloses a plastic material of molecular weight from about 1x10 6 to about 6x10 6 mixed together with glass micro-beads in order to reduce friction.
  • a rotary displacement pump is for pumping flowable, relatively viscous materials and comprises a liner ; a rotor configured to be driven by a shaft; said rotor including a shaft portion and a radially protruding web having a configuration of an undulatory disk type; a scraper gate having an engagement slot of predetermined radial height and predetermined axial width, said engagement slot engaging said protruding web of said rotor; said scraper gate being supported by a scraper gate guide so as to be retained in circumferential direction and to allow a reciprocating movement in a substantially axial direction; a pump housing comprising a front end part and a rear end part, said pump housing enclosing said liner, said rotor, said scraper gate and said scraper gate guide, said shaft extending through said rear end part of said pump housing; said liner including a first liner element and a second liner element, said first and second liner elements abutting to each other laterally along a radially outer
  • the inventors have found out that the material to be pumped often collects at the scraper gate and/or the liner which results in dead areas and a loss in efficiency during pumping operation. Moreover, the inventors have discovered that the material that is pumped may not be treated with a rough surface, the material to be pumped rather has to be treated carefully by a smooth surface having a very low frictional coefficient. Resulting therefrom the inventors have identified the need to select a material for the surfaces coming into contact with the material to be pumped that provides for very low friction.
  • the inventors have found out that it is the scraper gate and/or the liner that is prone and liable to wear and have/has to be replaced first and that there is a need for a very hard surface material for the scraper gate and/or the liner.
  • scraper gate and/or liner material must have an excellent resistance against chemicals, since pumps that are used especially in the chemical and biochemical industry, the medical industry and the cosmetic industry have to withstand coming into contact with such chemicals under high pressure.
  • scraper gate and/or the liner material must be permitted to be used in the food industry since many rotary displacement pumps of the scraper gate type, and particularly the rotary displacement pumps of the present invention are used for pumping food like yoghurt, soup, sauce, mayonnaise, fruit juice, cheese material, chocolate and the like.
  • scraper gate and/or liner material comprises 85 to 95 Vol-% of a Polyethylene basis material of ultra-high molecular weight and 5 to 15 Vol-% of glass particles having a rounded shape distributed within said Polyethylene basis material.
  • the surface comprising the Polyethylene basis material of ultra-high molecular weight and rounded surface portions formed by the glass particles that protrude out constitutes a hard slide face for the flowable, relative viscous materials to be pumped which leads to a very long operating time and significantly longer replacement intervals.
  • Such material has a very low frictional coefficient and treats the material to be pumped very carefully, contrary to e.g. fibre class reinforced plastics materials. It has an excellent resistance against chemicals and is harmless for health which means it can be used in the food industry.
  • the glass particles are embedded within the Polyethylene basis material of the high molecular weight and can be spread evenly within the Polyethylene basis material of high molecular weight.
  • Such material is perfectly suited for high pressure operating conditions that exist during pumping operation of the rotary displacement pump according to the present invention.
  • the rounded surface portions of the glass particles are to be understood as continuous surface portions avoiding sharp edges or spikes and they comprise portions of an oval basic shape, a spherical basic shape, an egg-like basic shape or any other non-symmetric rounded basic shape.
  • the liner can also be called stator, which terms are synonyms, and, likewise, the liner element(s) can also be called stator element(s), which terms are synonyms.
  • stator which terms are synonyms
  • stator element(s) which terms are synonyms
  • the rotary displacement pump further comprises a ring-formed front sliding insert arranged in axial direction between said shaft portion of said rotor and a front shaft sleeve/bearing element being secured to the front end portion of said shaft.
  • This ring-formed front sliding insert provides for a reliable sealing between the shaft portion of said rotor and the front shaft sleeve/bearing element and prevents material to be pumped from getting to the shaft.
  • the front shaft sleeve/bearing element has an annular groove in its rear side facing said shaft portion of said rotor, said ring-formed front sliding insert being placed with an anchoring portion thereof in such annular groove.
  • the rotary displacement pump further comprises a ring-formed rear sliding insert arranged in axial direction between a rear shaft sleeve sealing element being secured to said shaft and said shaft portion of said rotor.
  • This ring-formed rear sliding insert provides for a reliable sealing between the shaft portion of said rotor and the rear shaft sleeve sealing bearing element and prevents material to be pumped from getting to the shaft.
  • the rear shaft sleeve sealing element has an annular groove in its front side facing said shaft portion of said rotor, said ring-formed rear sliding insert having a substantially rectangular cross-section or a T-shaped cross-section being placed with an anchoring portion thereof in such annular groove.
  • At least one of the front and rear sliding inserts has a T-shape with an anchoring portion being placed in the respective annular groove and with an abutment portion abutting against the respective shaft portion of said rotor.
  • T-shape a particularly good positioning and sealing function of such front and/or rear sliding insert can be attained.
  • the ring-formed front and rear sliding inserts and the front shaft sleeve/bearing element having such annular groove and said rear shaft sleeve sealing element having such annular groove can be manufactured and assembled easily and at reasonable costs.
  • Such front and rear sliding inserts can also come into contact with the materials to be pumped.
  • At least one element of the front sliding insert, the rear sliding insert and the front shaft sleeve/bearing element comprises 85 to 95 Vol-% of a Polyethylene basis material of ultra-high molecular weight and 5 to 15 % Vol-% of glass particles having a rounded shape evenly distributed within said Polyethylene basis material, such that surface of said sliding insert comprising said Polyethylene basis material and glass particles protruding out of the same forms a rounded and hard slide face for the flowable, relatively viscous materials to be pumped.
  • said glass particles are of spherical or oval shape.
  • Such glass particles of spherical or oval shape contribute to providing a surface with good hardness and durability and a low frictional coefficient.
  • the diameter of said glass particles is 10 - 40 ⁇ m, particularly 20 - 30 ⁇ m, and more particularly around 24 ⁇ m.
  • Such diameter of glass particles has been proven to further improve the surface properties, in particular the excellent hardness, the excellent durability and the low frictional coefficient.
  • the molecular weight of said Polyethylene basis material is 1.0 * 10 6 g/mol to 1.2 * 10 6 g/mol, particularly close to and above 1.0 * 10 6 g/mol.
  • the Polyethylene basis material having such molecular weight provides for an excellent hardness and durability of the scraper gate, liner and, if applicable, of the front and rear sliding inserts, and guarantees a long lifetime of such parts and considerably longer maintenance intervals or intervals between points in time when the parts have to be replaced.
  • the Polyethylene basis material withstands operating temperatures of up to 100°C without softening.
  • the rotary displacement pump can be used for pumping materials that require higher operating temperatures or for pumping materials where the operating temperatures get that high which enables the rotary displacement pumps to be used for a wider variety of applications.
  • the first liner element and the second liner element are generally semi-circular arc-formed.
  • the semi-circular arc-formed liner elements only occupy part of the inner space of the pump housing, in particular the lower half of the inner space of the pump housing, and the inlet and outlet chambers are formed by the liner, the pump housing, the scraper gate and the scraper gate guide.
  • the enclosure that encircles a portion of said radially protruding web of said rotor is generally semi-circular arc-formed.
  • the material is actually pumped through such channel or enclosure from the inlet to the outlet chamber.
  • the first liner element and the second liner element are generally cup shaped and define a circumferential wall.
  • These generally cup-shaped first and second liner elements mainly occupy the entire circumferential space within the pump housing, and the inlet chamber adjacent to the inlet port is formed by said liner elements and the outlet chamber adjacent to the outlet port is formed by such liner elements, with the inlet and the outlet port separated from each other by the scraper gate and the scraper gate guide.
  • said scraper gate and/or said scraper gate guide are completely arranged within said liner.
  • said scraper gate guide is supported by said liner.
  • the liner elements comprise appropriate fixing means, especially cavities, limit stops and the like.
  • Fig. 1 shows an entire rotary displacement pump 2 comprising a pump part 4 or pump proper 4 and a support part 6.
  • a shaft 8 protrudes from the support part 6.
  • a drive motor typically an electric motor serves to apply torque to the shaft 8, either by being directly or through a coupling coupled to the shaft 8 or for example through a gear or a pulley etc.
  • the support part 6 comprises a support part housing 10 in which appropriate roller bearings (not shown) for the shaft 8 can be provided.
  • the support part housing 10 has a substantially cylindrical shape, and the front end of the support part housing 10 is encircled and fixed by a mounting frame 12 that has a lower mounting plate in order to fix the entire rotary displacement pump 2 to an appropriate base.
  • a pump housing 14 having the following main parts: a tubular cylindrical body 14, the rear end of which is mounted by appropriate mounting pins or the like (not shown) to the front side of the mounting frame 12, a rear end plate (not shown) having a central aperture through which the shaft 8 extends and which rear end plate is either formed by the front side of the mounting frame 12 itself, by a bottom plate integral with the tubular cylindrical body 14 or by a separate rear end plate provided before the front side of the mounting frame 12, a circular front end plate 52 that can be tightly attached to the front side of the tubular cylindrical body 14 by means of mounting pins 20 protruding out from the annular front side of the tubular cylindrical body 14 and through corresponding through-holes disposed in appropriate locations of the front end plate 52 and by means of nuts 54 that engage with corresponding threads of the mounting pins 20 in order to fix the pump housing 14 and the front end plate 52 tightly together, an inlet pipe socket/inlet port 16 provided with an inlet port flange, and an outlet
  • the inlet pipe socket/inlet port and the outlet pipe socket/outlet port can also be arranged the other way round with the inlet pipe socket/inlet port being situated on the right (closer to the viewer) and with the outlet pipe socket/outlet port being situated on the left (farther from the viewer).
  • the scraper gate and the scraper gate guide would have to be turned around as compared to Fig. 1 with their inlet chamber sides being situated on the right (closer to the viewer) and with their outlet chamber sides being situated on the left (farther from the viewer).
  • the axes of the inlet and outlet ports 16 and 18 intersect at 90°.
  • the inlet and outlet ports 16 and 18 can also be arranged such that their axes intersect at another angle, for example at an angle of 180°.
  • the tubular cylindrical body 14 has two openings corresponding to the diameter of the inlet and outlet ports 16 and 18.
  • the tubular cylindrical body and the inlet and outlet port 16, 18 as well as the front end plate 52 can consist of stainless steel.
  • the middle to front portion of the shaft 8 is provided with axially extending recesses that engage with the corresponding protrusions of the rotor 28, particularly with the shaft portion 30 of the rotor 28 to be described in further detail below, and, if appropriate, with other rotating parts of the pump part 4.
  • the tip of the shaft 8 is tapering.
  • the rotor 28 is keyed to the shaft 8 and rotates with it.
  • An inner portion of the rear shaft sleeve sealing element 22 rotates together with the shaft 8, an outer cylindrical portion of the rear shaft sleeve sealing element 22 that can well be seen in Fig. 1 surrounds the inner portion circumferentially and remains standing still in operation, and dynamic sealing means are provided between the rotating inner portion and the non-rotating outer cylindrical portion of the rear shaft sleeve sealing element 22.
  • the hub of the rotor 28 is clamped by means of the locking screw 48 in axial direction against the rear shaft sleeve sealing element 22 and against the front shaft sleeve 42.
  • the shaft 8 rotate and form a rotor assembly together.
  • the outer cylindrical portion of the rear shaft sleeve sealing element 22, the rear sliding insert 24, the front sliding insert 41, and the front shaft sleeve/bearing 42 do not rotate, but stand still in operation.
  • the rotor 28 comprises a shaft portion 30 of basically cylindrical shape surrounding the shaft 8.
  • the radially inner substantially ring-formed face of the shaft portion 30 engaging in the assembled state with the shaft 8.
  • the rotor 28 further comprises a radially protruding web 32 having a axial thickness and a predetermined outer diameter.
  • the web 32 has a rear surface and a front surface. If one follows, for example with a finger tip, the front surface along the circular line of the outer diameter, the finger tip will describe a curved sinus-type line seen in radial view (not necessarily in the strict mathematical sense), undulating with respect to a middle plane intersecting the axis of the shaft 8 at a right angle.
  • a 360° circle there are two full periods of the sine curve, i. e. the first time from completely left-hand in Fig. 1 to completely right-hand in Fig. 1 and back.
  • the same description as made with respect to the front face applies to the rear face as well.
  • this undulating form of the radially protruding web 32 of the rotor 28 is only depicted schematically in the figures.
  • a liner lines the lower part of the inside of the housing 14.
  • the liner consists of a generally semi-circular arc-formed rear liner element 26 and of a generally semi-circular arc-formed front liner element 36, that can be formed separately, as in Fig. 1 , or integrally with the front end plate 52 and, respectively the rear end plate.
  • the liner elements can be formed as liner elements fixed in the pump housing 14. In the assembled state of the rotary displacement 2, the front liner element 36 abuts with its front face against the corresponding circular section of the rear face of the front end plate 52.
  • the rear liner element 26 is a mirror-image to the front liner element 26, and the rear liner element 26 abuts with its outer surface against a corresponding portion of an inner face of the rear end plate (not shown) of the pump housing 14.
  • the front liner element 36 has the profile of a reversed "L" with the radially oriented portion of the profile forming a radial wall for the radially protruding web 32 and with the axially oriented portion of the profile forming a circumferential wall for the radially protruding web 32.
  • the rear/inner end (term “inner” is to be understood opposite to the term “outer”, see below) of the circumferential wall forms a lateral abutment face that abuts in the mounted state to the opposite lateral abutment face of the rear liner element 26.
  • the face of the circumferential wall that is oriented towards the shaft axis forms a liner channel bottom face and the inner face of the radial wall forms a lateral liner channel face.
  • the rear liner element 26 has the profile of an "L" with the radially oriented portion of the profile forming a radial wall for the radially protruding web 32 and with the axially oriented portion of the profile forming a circumferential wall for the radially protruding web 32.
  • the front/inner end (term “inner” is to be understood opposite to the term “outer”, see below) of the circumferential wall forms a lateral abutment face that abuts in the mounted state to the opposite lateral abutment face of the front liner element 36.
  • the face of the circumferential wall that is oriented towards the shaft axis forms a liner channel bottom face and the inner face of the radial wall forms a lateral liner channel face.
  • an inlet chamber adjacent to the inlet port 16 and an outer chamber adjacent to the outlet port 18.
  • the inlet chamber is provided in the upper right quadrant of the inside of the pump housing 14 that is located farther from the viewer of Fig. 1
  • the outlet chamber is provided in the upper left quadrant of the inside of the pump housing 14 that is located closer to the viewer in Fig. 1 .
  • a rear shaft sleeve sealing element 22 has a cylindrical outer shape the diameter of which correspond to the outer diameter of the shaft portion 30 of the rotor 28 and the diameter of the central recess in the rear liner element 26.
  • the front end of the rear shaft sleeve sealing element 22 is sealingly connected to the rear end of the rotor 28, particularly to the rear end of the shaft portion 30 thereof by means of the rear sliding insert 24, that can be formed as an O-ring.
  • the rear sliding insert 24 has, in a radial sectional cut the form of a "T" lying in axial direction, with its T-bar forming an anchoring portion extending rearwards and being inserted, in the mounted state, in a corresponding annular groove in the front face of the rear shaft sleeve sealing element 22 and abutting with its planar annular front face against a corresponding portion of the rear face of the shaft portion 30 of the rotor 28.
  • the rear sliding insert 24 can have a rectangular cross-section.
  • the front shaft sleeve/bearing 42 also has a substantially cylindrical shape, the outer diameter of which corresponds to the outer diameter of the shaft portion 30 of the rotor 28 and to the diameter of the recess in the front liner element 36.
  • the front shaft sleeve/bearing 42 is sealingly connected to the rotor 28, particularly to the shaft portion 30 thereof by means of the front sliding insert 41, that can be formed as an O-ring.
  • the front sliding insert 41 also has, in a radial sectional cut, the form of a "T" lying in axial direction, with its T-bar forming an anchoring portion extending forwards.
  • the T-bar of the front sliding insert 41 is inserted into a corresponding annular groove in the rear side of the front shaft sleeve 42 and it abuts with its planar annular rear face to a corresponding annular portion of the front face of the shaft portion 30 of the rotor 28.
  • the front sliding insert 41 can have a rectangular cross-section.
  • the rear shaft sleeve sealing element 22, the rear sliding insert 24, the rotor 28, the front sliding insert 41 and the front shaft sleeve 42 are fixed to the shaft 8 such that they rotate together with it by means of a locking nut 44 and a front locking screw 48 engaging in axial direction into a corresponding hole at the tip of the shaft 8, said hole being provided with a thread.
  • a sealing ring 46 provided between the locking nut 44 and the locking screw 48 the tip portion is also reliably sealed against material entering from the front.
  • the inlet chamber is confined by the straight upper inlet chamber faces of the liner elements 26 and 36 located to the right in Fig. 1 , by the parts of the rear shaft sleeve sealing element 22 and the front shaft sleeve 42 and the sliding inserts 24 and 41 lying in the upper right quadrant of the inside of the pump housing 14, by the right-hand sides of the scraper gate 38 and the scraper gate guide 40 and by the inner face of the tubular cylindrical body 14 within the upper right quadrant.
  • the outlet chamber is confined by the straight upper outlet chamber faces of the liner element 26 and 36 located to the left in Fig. 1 , by the parts of the rear shaft sleeve sealing element 22 and the front shaft sleeve 42 and the sliding inserts 24 and 41 lying in the upper left quadrant of the inside of the pump housing 14, by the left-hand sides of the scraper gate 38 and the scraper gate guide 40 and by the inner face of the tubular cylindrical body 14 within the upper left quadrant.
  • the scraper gate 38 has generally the configuration of a rectangular plate, but has an engagement slot of a predetermined radial height and predetermined axial width into which the radially protruding web 32 of the rotor 28 engages.
  • the transitions between the narrowest portion of the engagement slot and the inlet and outlet chamber-facing surfaces are curved.
  • the axial dimension of the engagement slot at its smallest portion is just a little wider than the axial dimension of the radially protruding web 32 of the rotor 28, so that the engagement slot can be placed over the radially protruding web 28, the scraper gate 38 straddling the web 32.
  • the curved transitions take into account the curved or undulatory configuration of the web 32 as contrasted to a plane configuration.
  • the scraper gate 38 is supported by a scraper gate guide 40 that is firmly mounted in the pump housing 14 especially in an upper position of the pump housing 14 extending in an axial direction and in particular between the front end plate 52 and the rear end plate which can be formed integrally with the pump housing 14.
  • the scraper gate guide 40 in the exemplary embodiment of Fig. 1 , has a basically cylindrical outer shape with an axial guiding recess extending from its bottom to a portion just below its top end, the scraper gate 38 being inserted, in the assembled state of the pump, in such axial recess and being held there in circumferential direction and being guided so as to allow a reciprocating movement following the reciprocating back and forth movement of the radially protruding web 32.
  • the side of the scraper gate guide 40 being positioned in the outlet chamber, in Fig. 1 located to the left, has, in the exemplary embodiment of Fig. 1 , openings/breakthroughs at the front and the rear sides thereof.
  • Fig. 2 shows an entire rotary displacement pump 62 comprising a pump part 4 or pump proper 4 and a support part 6.
  • the second displacement pump 62 also comprises a pump part or pump proper 4 and a support part 6, and the pump housing 14 with inlet and outlet ports 16 and 18 and front end plate 52 and rear end plate 12 correspond to those in Fig. 1 .
  • the rotor 28 with its shaft portion 30 and its radially protruding web 32 corresponds to the rotor 28 of Fig. 1 . Therefore these elements are provided with corresponding reference numerals, and the description thereof is not repeated, but omitted for brevity.
  • the liner of the second rotary displacement pump 62 also consists of two liner elements, namely a rear liner/liner element 70 and a front liner/liner element 80, however, different than the liner 26, 36 of the first rotary displacement pump 2, the liner 70, 80 lines completely the inner surface of the housing 14, and the rear liner element 70 is generally cup-shaped and the front liner element 80 is also generally cup-shaped with the plane faces of the liner elements 70, 80 being oriented in an outer axial direction and the cup portions of the liner elements 70, 80 being oriented in an inner direction, the terms "inner” and “outer” being understood with respect to the rotor 28.
  • the rear liner element 70 has, in its lower portion (constituting approximately the lower half of the rear liner element 70), a lower bottom wall portion having a substantially larger thickness than the thickness of the upper bottom wall portion.
  • the rear liner element 70 comprises, in its central portion, a cylindrical opening that is confined in its lower portion by the thicker lower bottom wall portion and in its upper portion by a cylindrical wall having the same thickness as the lower bottom wall portion.
  • the front faces of the thicker lower bottom wall portion and of the cylindrical wall form a radial, and the thinner upper bottom wall portion also forms a radial plane being set back with respect to the front faces of the thicker lower bottom wall portion and of the cylindrical wall.
  • the rear face of the rear liner element 70 (not visible in Fig.
  • the rear liner element 70 is surrounded by a circumferential cylindrical wall having in its lower half a higher wall thickness than in its upper half.
  • the upper part of the thinner cylindrical circumferential wall is provided with two rounded recesses at positions corresponding to the inlet and outlet ports 16 and 18, and the diameter of these rounded recesses also correspond to the diameter of the inlet and outlet port 16 and 18.
  • the front liner/liner element 80 is a mirror-image to the rear liner element 70 with a first relevant exception that instead of a central opening there is a closed bottom wall in the front liner element 80 provided with a circular recess in the middle that accommodates the end portion of the rotor assembly, namely the locking screw 76.
  • the front liner element 80 comprises in its lower portion (constituting approximately the lower half of the front liner element 80), a bottom wall of a substantially larger thickness the front face of which forms a radial plane together with a cylindrical wall confining the central recess, and in its upper portion a bottom wall portion also forming a substantially radial plane, which is set back with respect to the inner face of the thicker lower bottom wall portion and of the cylindrical wall.
  • the front liner element 80 is also surrounded by a circumferential cylindrical wall having in its lower half a higher wall thickness than in its upper half. Rounded recesses are formed in the thinner upper circumferential wall portion at positions and having diameters corresponding to those of the inlet and outlet ports 16 and 18.
  • the rear liner element 70 abuts with its rear face towards the front face of the rear end plate 12, and the front liner element 80 abuts with its front face against the rear face of the front end plate 52.
  • the front face of the cylindrical wall of the the rear liner element 70 abuts against the rear face of the cylindrical wall of the front liner element 80.
  • the openings that are formed by the corresponding recesses of the rear and front liner elements 70 and 80 align with the inlet and outlet ports 16 and 18.
  • element 64 comprising a number of sealing rings, a rear shaft sleeve sealing element 66, the rotor 28 with its shaft portion 30 and its radially protruding web 32 and a front locking screw 76 fixed to a corresponding hole in the tip of the shaft 8 provided with a thread, and a sealing ring 74 that can be an O-ring sitting on the outer diameter of the locking screw 76.
  • a sealing ring 68 can be provided that can be an O-ring sitting on the outer diameter of the rear shaft sleeve sealing element 66, and the rear face of the shaft portion 30 of the rotor 28 that can also be provided with a recess the diameter of which corresponds to the outer diameter of the front face of the rear shaft sleeve sealing element 66 (not shown).
  • the second rotary displacement pump 62 also comprises a scraper gate element 82 and a scraper gate guide 84, and the scraper gate 82 has an engagement slot of predetermined radial height and predetermined axial width into which, in the assembled state, the protruding web 32 of the rotor 28 engages.
  • the scraper gate guide 84 also supports the scraper gate 82 such that the scraper gate 82 is retained in a circumferential direction and a reciprocating movement in a substantially axial direction following the sinusoidal back and forth movement of the web 32 of the rotor 28 is allowed.
  • the scraper gate guide 84 is a plate with a generally rectangular recess in its middle portion.
  • the scraper gate guide 84 is fixed in the liner 70, 80 by means of grooves in the liner elements 70, 80, a part of the groove can be seen on top of the circular wall of the rear liner element 70.
  • the scraper gate element 82 itself has a guiding groove in axial direction at its upper side and guiding grooves in radial direction at its front and rear sides, and the scraper gate element 82 is inserted such that the bottom of its groove in its upper side abuts against the lower edge of the rectangular recess of the scraper gate guide 84.
  • the scraper gate element 82 can be held in circumferential direction by the scraper gate guide 84, and a reciprocating movement of the scraper gate element 82 in a back and forth direction following the sinusoidal movement of the radially protruding web 32 of the rotor 28 is allowed.
  • the inlet chamber is formed is in the upper right quadrant within the liner 70, 80, and the outlet chamber is formed in the upper left quadrant within the liner 70, 80, with the inlet and the outlet chambers being separated from each other by the scraper gate guide 84 and the scraper gate element 82.
  • the bottoms of the inlet and outlet chambers are formed by the substantially straight horizontal portion connecting the thicker lower bottom wall portion to the thinner upper bottom wall portion, by the parts of the cylindrical wall lying in the upper right/upper left quadrant, by the right/left sides of the scraper gate element 82 and the scraper gate guide 84 and by the inner face of the thinner upper cylindrical wall portion of the liner 70, 80.
  • the liner channel is formed by the upper face of the thicker lower cylindrical wall portion, by the radially extending inner faces of the thicker bottom wall portion and by the cylindrical outer face of the shaft portion 30 of the rotor 28.
  • material to be pumped that has entered the inlet chamber through the inlet port 16 is pumped through the liner channel by means of the radially protruding web 32 of the rotor 28 to the outlet chamber from which it is discharged through the outlet port 18.
  • the liner elements 26, 36; 70, 80 and/or the scraper gate elements 38; 82 can be made of a material that the inventors of the present subject-matter have newly developed, namely a material comprising 85 to 95 Vol-% of a Polyethylene basis material of ultra-high molecular weight and 5 to 15 % Vol-% of glass particles having a rounded shape distributed within said Polyethylene basis material.
  • the sliding inserts 24 and 41 and the front shaft sleeve/bearing 42 can be made of such material.
  • the surfaces of these elements and in particular the surfaces of the inlet and outlet chambers and the liner channel that are formed by these elements and come into contact with the material to be pumped comprise rounded surface portions formed by such glass particles and they constitute a hard slide face for the flowable, relatively viscous materials to be pumped.
  • These elements and the surfaces thereof exhibit excellent material properties, in particular a very low friction coefficient that improves the material flow and the efficiency of the entire pump and avoids packing and collecting material at those surface portions, very high hardness and durability which enhances the lifetime of these elements which are actually the elements that are subjected to the highest stress during pumping operation and regularly suffer wear and material loss.
  • These parts are made of the material that the inventors of the present subject-matter have newly developed and therefore withstand this stress much better and have to be replaced much less frequently.
  • the rotary displacement pump according to the present invention can be used for a very wide variety of applications including pumping flowable, relatively viscous materials in the food stuff industry, the chemical and biochemical industry, the medical industry and the cosmetic industry.

Claims (13)

  1. Rotations-Verdrängerpumpe (2; 62) zum Pumpen von fließfähigen viskosen Materialien, wobei die Rotations-Verdrängerpumpe Folgendes aufweist:
    einen Einsatz (26, 36; 70, 80);
    einen Rotor (28), der dazu ausgebildet ist, von einer Welle (8) angetrieben zu werden;
    wobei der Rotor (28) einen Wellenbereich (30) und einen radial vorstehenden Flansch (32) mit einer Konfiguration vom Typ einer Wellscheibe aufweist;
    einen Streifelement-Schieber (38; 82) mit einer Eingriffsaussparung mit vorbestimmter radialer Höhe und vorbestimmter axialer Breite, wobei die Eingriffsaussparung mit dem vorstehenden Flansch (32) des Rotors (28) zusammenwirkt;
    wobei der Streifelement-Schieber (38; 82) von einer Streifelement-Schieber-Führung (44; 84) derart abgestützt ist, dass es in Umfangsrichtung festgehalten ist und eine Hin- und Herbewegung in einer im Wesentlichen axialen Richtung ermöglicht ist;
    ein Pumpengehäuse (14) mit einem vorderen Endteil (52) und einem hinteren Endteil, wobei das Pumpengehäuse (14) den Einsatz (26, 36; 70, 80),
    den Rotor (26), den Streifelement-Schieber (38; 82) und die Streifelement-Schieber-Führung (40; 84) umschließt, wobei sich die Welle (8) durch das hintere Endteil des Pumpengehäuses (14) hindurch erstreckt;
    wobei der Einsatz (26, 36; 70, 80) ein erstes Einsatzelement (26; 70) und ein zweites Einsatzelement (36; 80) aufweist, wobei das erste und das zweite Einsatzelement (26, 36; 70, 80) seitlich entlang eines radial äußeren Anlagebereichs aneinander anliegen, um einen Einsatz-Kanal zu bilden, durch den sich der radial vorstehende Flansch (32) des Rotors (28) erstreckt, und um eine Umschließung zu bilden, die einen Bereich des radial vorstehenden Flansches (32) des Rotors (28) umschließt;
    wobei von dem Einsatz (26, 36), dem Streifelement-Schieber (38) und der Streifelement-Schieber-Führung (40) oder von dem Einsatz (70, 80), dem Pumpengehäuse (14), dem Streifelement (82) und der Streifelement-Schieber-Führung (84) eine Einlasskammer und eine Auslasskammer gebildet werden;
    wobei der Streifelement-Schieber (38; 82) zusammen mit der Streifelement-Schieber-Führung (40; 84) eine Trennwand zwischen der Einlasskammer und der Auslasskammer bildet;
    wobei die Einlass- und die Auslasskammer mit jeweiligen Einlass- und Auslassöffnungen (16, 18) versehen sind;
    wobei sich der Einsatz-Kanal von der Einlasskammer zu der Auslasskammer erstreckt;
    wobei der Flansch (32) des Rotors (42) durch die Einlasskammer, den Einsatz-Kanal, die Auslasskammer und die Aussparung des Streifelement-Schiebers (38; 82) hindurch drehbar ist;
    dadurch gekennzeichnet, dass der Streifelement-Schieber (38; 82) und/oder der Einsatz (26, 36) aus 85 bis 95 Vol.-% eines Materials auf Polyethylenbasis mit ultrahohem Molekulargewicht und aus 15 bis 5 Vol.-% Glaspartikeln mit kugelförmiger oder ovaler Formgebung bestehen, die innerhalb des Materials auf Polyethylenbasis verteilt sind, so dass die Oberfläche des Streifelement-Schiebers (38; 82) und/oder des Einsatzes (26, 36; 70, 80), die durch nach außen ragende Glaspartikel gebildete abgerundete Oberflächenbereiche aufweisen, eine harte Gleitfläche für die zu pumpenden fließfähigen viskosen Materialien bilden.
  2. Rotations-Verdrängerpumpe (2) nach Anspruch 1,
    die weiterhin einen ringförmigen vorderen Gleiteinsatz (41) aufweist, der in Axialrichtung zwischen dem Wellenbereich (30) des Rotors (28) und einem vorderen Wellenhülsen-/Lagerelement (42) angeordnet ist, das an dem vorderen Endbereich der Welle (8) befestigt ist.
  3. Rotations-Verdrängerpumpe (2) nach Anspruch 2,
    wobei das vordere Wellenhülsen-/Lagerelement (42) eine ringförmige Nut in seiner dem Wellenbereich (30) des Rotors (28) zugewandten Rückseite aufweist, wobei der ringförmige vordere Gleiteinsatz (41) mit einem Verankerungsbereich in dieser ringförmigen Nut angeordnet ist.
  4. Rotations-Verdrängerpumpe (2) nach einem der vorhergehenden Ansprüche,
    die ferner einen ringförmigen hinteren Gleiteinsatz (24) aufweist, der in Axialrichtung zwischen einem an der Welle (8) befestigten hinteren Wellenhülsen-Dichtungselement (22) und dem Wellenbereich (30) des Rotors (28) angeordnet ist.
  5. Rotations-Verdrängerpumpe (2) nach Anspruch 4,
    wobei das hintere Wellenhülsen-Dichtungselement (22) eine ringförmige Nut in seiner dem Wellenbereich (30) des Rotors (28) zugewandten Vorderseite aufweist, wobei der ringförmige hintere Gleiteinsatz (24) einen im Wesentlichen rechteckigen Querschnitt oder einen T-förmigen Querschnitt aufweist und mit einem Verankerungsbereich in dieser ringförmigen Nut angeordnet ist.
  6. Rotations-Verdrängerpumpe (2) nach einem Ansprüche 2 bis 5,
    wobei zumindest einer von dem vorderen und dem hinteren Gleiteinsatz (24, 41) T-förmig ausgebildet ist und mit einem Verankerungsbereich in der jeweiligen ringförmigen Nut angeordnet ist sowie mit einem Anlagebereich an dem jeweiligen Wellenbereich (30) des Rotors (28) anliegt.
  7. Rotations-Verdrängerpumpe (2) nach einem Ansprüche 2 bis 6,
    wobei mindestens ein Element von dem vorderen Gleiteinsatz (24), dem hinteren Gleiteinsatz (24, 41) und dem vorderen Wellenhülsen-/Lagerelement (42) aus 85 bis 95 Vol.-% eines Materials auf Polyethylenbasis mit ultrahohem Molekulargewicht und aus 15 bis 5 Vol.-% Glaspartikeln mit kugelförmiger oder ovaler Formgebung besteht, die innerhalb des Materials auf Poly-ethylenbasis gleichmäßig verteilt sind, so dass die Oberfläche des Gleiteinsatzes (24, 41), der das Material auf Polyethylenbasis und aus diesem heraus ragende Glaspartikel aufweist, eine abgerundete und harte Gleitfläche für die zu pumpenden fließfähigen viskosen Materialien bildet.
  8. Rotations-Verdrängerpumpe (2; 62) nach einem der vorhergehenden Ansprüche,
    wobei der Durchmesser der Glaspartikel 10 - 40 µm, insbesondere 20 - 30 µm und im Spezielleren etwa 24 µm beträgt.
  9. Rotations-Verdrängerpumpe (2) nach einem der vorhergehenden Ansprüche,
    wobei das erste Einsatzelement (26) und das zweite Einsatzelement (36) im Allgemeinen halbkreis-bogenförmig ausgebildet sind.
  10. Rotations-Verdrängerpumpe (2) nach Anspruch 9,
    wobei die Umschließung, die einen Bereich des radial vorstehenden Flansches (32) des Rotors (28) umschließt, im Allgemeinen halbkreis-bogenförmig ausgebildet ist.
  11. Rotations-Verdrängerpumpe (62) nach einem der Ansprüche 1 bis 8, wobei das erste Einsatzelement (70) und das zweite Einsatzelement (80) im Allgemeinen becherförmig ausgebildet sind und eine Umfangswand bilden.
  12. Rotations-Verdrängerpumpe (62) nach Anspruch 11,
    wobei der Streifelement-Schieber (82) und oder die Streifelement-Schieber-Führung (84) vollständig innerhalb des Einsatzes (70, 80) angeordnet sind.
  13. Rotations-Verdrängerpumpe nach Anspruch 11 oder 12,
    wobei die Streifelement-Schieber-Führung (84) von dem Einsatz (70, 80) abgestützt ist.
EP11179881.5A 2011-09-02 2011-09-02 Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität Active EP2565454B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP11179881.5A EP2565454B1 (de) 2011-09-02 2011-09-02 Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität
PCT/EP2012/066193 WO2013030025A2 (en) 2011-09-02 2012-08-20 Rotary displacement pump for pumping flowable viscous materials
US14/241,225 US20140301878A1 (en) 2011-09-02 2012-08-20 Rotary Displacement Pump for Pumping Flowable Viscous Materials

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11179881.5A EP2565454B1 (de) 2011-09-02 2011-09-02 Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität

Publications (2)

Publication Number Publication Date
EP2565454A1 EP2565454A1 (de) 2013-03-06
EP2565454B1 true EP2565454B1 (de) 2016-12-14

Family

ID=46704665

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11179881.5A Active EP2565454B1 (de) 2011-09-02 2011-09-02 Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität

Country Status (3)

Country Link
US (1) US20140301878A1 (de)
EP (1) EP2565454B1 (de)
WO (1) WO2013030025A2 (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015116770A1 (de) 2015-10-02 2017-04-06 Watson-Marlow Gmbh Pumpe und Sperrvorrichtung
DE102015116768A1 (de) 2015-10-02 2017-04-20 Watson-Marlow Gmbh Pumpe
DE102015116769A1 (de) * 2015-10-02 2017-04-06 Watson-Marlow Gmbh Pumpe und Sperrelement
EP3483440B1 (de) 2017-11-08 2020-05-27 Oina VV AB Peristaltische pumpe
CN107956688B (zh) * 2017-12-13 2024-04-16 杭州电子科技大学 一种具有轴向端面面密封转子型线容积泵
CN108561307B (zh) * 2017-12-13 2024-04-12 杭州电子科技大学 一种左右对称平面扭曲叶片偏摆泵
CN108087267A (zh) * 2017-12-13 2018-05-29 杭州电子科技大学 一种具有轴向端面面密封结构转子

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2319662A1 (fr) * 1975-11-26 1977-02-25 Bourrin Gilbert Perfectionnements aux materiaux anti-friction
US6808374B2 (en) * 2000-10-20 2004-10-26 Niagara Pump Corporation Sanitary design gear pump
EP1637740A1 (de) * 2004-09-20 2006-03-22 Sundyne Corporation Rotationsverdrängerpumpe mit einem Schieber und seiner Führung
EP1892418A3 (de) * 2006-08-12 2014-08-27 INDUSTRA Industrieanlagen - Maschinen und Teile GmbH Zahnradmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20140301878A1 (en) 2014-10-09
WO2013030025A3 (en) 2013-12-19
WO2013030025A2 (en) 2013-03-07
EP2565454A1 (de) 2013-03-06

Similar Documents

Publication Publication Date Title
EP2565454B1 (de) Drehbare Verdrängerpumpe zum Pumpen von fließfähigen Materialien hoher Viskosität
CA2580385C (en) Vane pump comprising a two-part stator
CA2580387C (en) Rotary displacement pump comprising scraper and guide of the scraper
RU2530677C1 (ru) Роторный насос вытеснения для перекачивания эмульсий с твердыми веществами, в частности, жидких взрывчатых веществ
US9011122B2 (en) Stator seal structure in uniaxial screw pump
US20150090345A1 (en) Rotary selection valve
CN107995939B (zh) 用于离心泵的工作轮和离心泵
EP1474624B1 (de) Einzeldichtung mit elastischem glied
WO2002070897A2 (en) A vane pump
ZA200306875B (en) A vane pump

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20130816

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

17Q First examination report despatched

Effective date: 20131030

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602011033325

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F04C0002356000

Ipc: F04C0002220000

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 2/22 20060101AFI20160601BHEP

Ipc: F04C 13/00 20060101ALI20160601BHEP

Ipc: F01C 21/10 20060101ALI20160601BHEP

Ipc: F04C 2/356 20060101ALI20160601BHEP

Ipc: F01C 21/08 20060101ALI20160601BHEP

INTG Intention to grant announced

Effective date: 20160620

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 853852

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602011033325

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170315

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170314

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 853852

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602011033325

Country of ref document: DE

Representative=s name: SCHMITT-NILSON SCHRAUD WAIBEL WOHLFROM PATENTA, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170414

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170414

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170314

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602011033325

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20170915

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170902

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170930

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170930

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170902

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170902

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110902

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161214

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230524

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20230920

Year of fee payment: 13

Ref country code: GB

Payment date: 20230921

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20230918

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230929

Year of fee payment: 13

Ref country code: DE

Payment date: 20231129

Year of fee payment: 13