EP2726740B1 - Micropompe, élément palier pour une micropompe et procédé pour la faire fonctionner - Google Patents

Micropompe, élément palier pour une micropompe et procédé pour la faire fonctionner Download PDF

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Publication number
EP2726740B1
EP2726740B1 EP12728264.8A EP12728264A EP2726740B1 EP 2726740 B1 EP2726740 B1 EP 2726740B1 EP 12728264 A EP12728264 A EP 12728264A EP 2726740 B1 EP2726740 B1 EP 2726740B1
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EP
European Patent Office
Prior art keywords
rotor
bearing element
bearing
shaft
fluid
Prior art date
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Active
Application number
EP12728264.8A
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German (de)
English (en)
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EP2726740A2 (fr
Inventor
Sven Reimann
Gerald Voegele
Thomas Weisener
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HNP Mikrosysteme GmbH
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HNP Mikrosysteme GmbH
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Publication of EP2726740A2 publication Critical patent/EP2726740A2/fr
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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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof

Definitions

  • the invention relates to a micropump, in particular of small and smallest size.
  • a micropump serves to convey fluid or medium from a low-pressure inlet to a high-pressure outlet and has a size of less than 30 mm, preferably less than 20 mm and particularly preferably less than 10 mm (maximum dimension of a micropump, in particular maximum dimension of the outer diameter of the outer rotor).
  • a generic micropump works on the principle of a gear pump. It has an inner rotor with external teeth and an outer rotor with internal teeth. The external teeth of the inner rotor are in meshing engagement with the internal teeth of the outer rotor. The two axes of the inner and outer rotor are offset from one another by an eccentricity. Due to this axial offset, the two engaged rotors form a pump chamber or several pump chambers between them, which cyclically change in size and position due to the rotation of the rotors.
  • Such a micropump is, for example, from WO 00/17523 A1 known.
  • An inner rotor and an outer rotor are designed and arranged to mesh with one another; both the inner rotor and the outer rotor are rotatably arranged in a sleeve.
  • the inner rotor is coupled to a shaft in a torsionally rigid manner.
  • the axis of the outer rotor is offset from the axis of this shaft, so that an eccentric rolling of the inner rotor with its outward-facing teeth takes place on the inward-facing tooth structure of the outer rotor and axial sealing lines are formed, each in pairs, depending on the number of teeth Define delivery chamber.
  • Generic pumps and micropumps are housed in a housing that protects the pump and seals it from the environment.
  • a possible housing shape for accommodating such a micropump is made of one Data sheet “Pump head mzr ® 4600” from HNP Mikrosysteme GmbH. This pump head has a shaft that protrudes from the front to connect a motor. Five disc-shaped elements form a housing structure as cylinder elements, starting with a housing shaft seal, a compensating kidney plate and a rotor receiving plate, followed by a fluid guide and a closure cover.
  • a hole is provided in the rotor mounting plate, which is eccentrically offset relative to the axis of the shaft for driving the inner wheel, so that the outer rotor is mounted off-center in the rotor mounting plate.
  • the compensating kidney plate and on the opposite side the fluid guide plate rests directly on the front side. Both plates have an input and output kidney directed towards the rotor on the fluid supply side and compensating kidneys arranged in mirror image to create a hydraulic balance on the opposite side. This results in a U-shaped fluid flow from the inlet via the inlet kidney to the rotating pump chambers, to the outlet and back to the outlet that is led out radially in the mzr ® 4600 data sheet.
  • DE B 33 10 593 (White ) shows a housing structure for a pump arrangement, which, together with a swash rod, creates an eccentrically operating gerotor. At the end not penetrated by the shaft, an outlet is centrally provided and, on the other hand, an inlet is radially offset, while intermediate plates having several channel segments are provided in between. It works with only three plate-shaped structures DE A 24 08 824 (McDermott ), which shows the gerotor principle in connection with compensation for wear of the meshing teeth, with channel segments being provided in the directly adjacent area between an inner disk and the two outer bearing disks for the shaft.
  • DE 10 2011 001 041 A1 shows a micropump for conveying fluid from a low-pressure inlet to a high-pressure outlet, having an inner rotor with external teeth, an outer rotor with internal teeth and a bearing element, the external teeth of the inner rotor meshing with the internal teeth of the outer rotor, the inner rotor being arranged in a rotationally fixed manner on a shaft , the outer rotor is mounted eccentrically to the inner rotor in a rotor holder in the radial direction, so that fluid chambers are formed as delivery chambers between the inner and outer rotors.
  • a delivery channel is provided on the pressure side, from which a return flow (there F ') to the suction side through the two Bearing of the shaft can be done.
  • DE 2008 054 755 A1 shows a comparable gear pump with a one-sided bearing on a shaft with two bearing surfaces, there paragraph [056], which have the same diameter.
  • US 2004/0228744 shows a cooling pump with a hollow channel, which is also the drive shaft.
  • the present invention is based on the object of providing a micropump that can be realized in a production-optimized and cost-effective manner with a minimized number of precision parts and simple assembly with high precision requirements.
  • the pump seal should be simplified and, in particular, should do without dynamic seals.
  • lubrication, flushing and temperature control of the bearings of the micropump should be implemented safely and easily despite their small dimensions.
  • Claim 1 solves this problem.
  • the claimed micropump for conveying fluid from a low-pressure inlet to a high-pressure outlet has an inner rotor with external teeth, an outer rotor with internal teeth and a bearing element, the external teeth of the inner rotor meshing with the internal teeth of the outer rotor.
  • the inner rotor is arranged on a shaft in a rotationally fixed manner
  • the outer rotor is mounted eccentrically to the inner rotor in a rotor holder in the radial direction, so that fluid chambers are formed as delivery chambers between the inner and outer rotor fluid chambers
  • the bearing element has a fluid passage for delivered fluid leading from the delivery chambers to the high-pressure outlet and the bearing element forms two radial bearings for the shaft and an axial bearing for the inner and outer rotors in at least one axial direction.
  • the inner and outer rotors form a gear ring or gerotor pump or an internal gear pump.
  • the externally toothed inner rotor is accommodated in the internally toothed outer rotor.
  • the axes of rotation of the inner rotor and outer rotor are offset by an eccentricity in the radial direction. This is preferably done by appropriately positioning the shaft carrying the inner rotor relative to the rotor holder supporting the outer rotor.
  • the bearing element, and thus also the shaft mounted radially therein, and the rotor holder can be centered in the axial direction relative to one another.
  • a recess in the rotor holder that accommodates and supports the outer rotor is then not arranged centrally in the rotor holder, but is shifted by the aforementioned eccentricity.
  • the axial centering or positioning of the bearing element and rotor receptacle relative to one another can take place via a housing, in particular an annular or sleeve-like housing, arranged at least partially around it. This can also align and center other elements of the pump relative to the bearing element and rotor holder, for example the kidney plate.
  • An alignment of the angular position of the bearing element, rotor holder and, if applicable, kidney plate to one another around the axial direction can preferably be done by means of a pin element or similar protruding through them.
  • the thickness of the inner and outer rotor in the axial direction is matched to the thickness of the rotor holder in the axial direction.
  • it can have a slight undersize, preferably in a range of 2 to 10 ⁇ m.
  • the inner rotor can be driven via the shaft and in turn drive the outer rotor.
  • the inner and outer rotors Due to the eccentric arrangement of the inner and outer rotors to one another, there is a free volume between them, which forms one or more delivery chambers. These expand or expand in the direction of rotation on the suction side, take up fluid there and convey it over to the pressure side, on which the delivery chamber or chambers steadily shrink or shrink in the course of further rotation. The delivery chamber is then guided back to the suction side. Here it begins to open again steadily with the rotational movement, so that the cycle closes.
  • the inner and outer rotors have different numbers of teeth. The teeth roll on one another and thereby form sealing lines on each side of an interdental space, so that each interdental space represents a delivery chamber.
  • a delivery chamber applies simultaneously to all existing delivery chambers of a gerotor pump, which at a given time each have a different volume between a respective pair of sealing lines, so that when the pump is in operation, there is a highly uniform delivery flow with a high ability to miniaturize the entire microsystem structure.
  • a gear ring pump there is usually a space in the free volume between the inner and outer rotor that seals the spaces between the teeth during rotation crescent-shaped sealing element arranged.
  • the delivery chambers formed between the inner and outer rotors deliver fluid from a low pressure fluid inlet or inlet kidney to a high pressure fluid outlet or outlet kidney.
  • Individual parts of the pump such as the inner and outer rotor, rotor holder, bearing element and, if necessary, kidney plate, are designed in such a way that the necessary but cost-intensive precision is concentrated on the smallest possible number of parts.
  • the short tolerance chains due to the compact structure enable the tolerances of the individual components to be increased, which further simplifies production and reduces manufacturing effort and production costs.
  • the core of the pump is the bearing element, the shaft, the rotor set consisting of the inner and outer rotors and the rotor holder, possibly supplemented by the kidney plate.
  • the precision required for sufficient hydraulic efficiency is achieved through precise bearing design and high-precision manufactured rotors.
  • the bearing element is the component with the greatest functional integration. According to the invention, it simultaneously forms a radial bearing for the shaft, an axial bearing for the inner and outer rotors in at least one axial direction and a fluid passage for fluid conveyed by the rotors. This functional integration allows the number of components and thus also the number of joints between them to be reduced in an advantageous manner compared to pumps known from the prior art.
  • the shaft and thus the inner rotor arranged thereon are radially supported by or in the bearing element.
  • the shaft is supported in the radial direction exclusively and directly by the bearing element.
  • the radial bearing or bearings is or are preferably placed on one side of the rotor arrangement and designed as a plain bearing. In particular, they can be arranged outside the actual micropump, so that the bearing diameters can be made correspondingly large. In particular, this or The radial bearings of the shaft can be formed outside the fluid guide formed in the bearing element, which in turn limits the diameter of the bearing or bearings to little. Overall, larger bearing diameters are possible and the bearing forces that occur are minimized and, as a result, the pump has a longer service life and reliability.
  • the lubricating film in the bearing builds up more quickly due to higher sliding speeds due to the larger bearing circumference.
  • the bearing element has a first radial bearing and a second radial bearing, the diameter of the first radial bearing being larger than the diameter of the second radial bearing.
  • the diameter of the first radial bearing is at least 6 mm, preferably at least 6.5 mm, and the diameter of the second radial bearing is at most 5 mm. Due to the different bearing diameters, one of the two bearings can be tailored to the small dimensions of the micropump and in particular to the diameter of the inner rotor.
  • the bearing diameter (of the smaller radial bearing) is determined by the dimensions of the inner rotor arranged on the shaft. Due to the installation, it is larger than the inner diameter or the inner dimension of the inner rotor arranged on the shaft.
  • the inner rotor In order to enable the inner rotor to rest and seal on the bearing element, it must be smaller than the root diameter of the inner rotor. Because of the small dimensions of the inner rotor in micropumps, the bearing diameter of the bearing on the inner rotor side is therefore limited.
  • the other bearing namely the one with a larger bearing diameter, is suitable for absorbing relatively high bearing forces.
  • the fluid passage is fluidly connected to at least one radial bearing.
  • the radial bearings are preferably designed in the form of depressions or bores, in particular through openings or through bores, in the bearing element. Their radial inner surfaces form bearing surfaces of appropriate surface quality and accuracy for the shaft.
  • the radial bearings formed in the bearing element and the fluid passage are designed and arranged so that they partially cross and overlap one another. The shaft then protrudes through the fluid passage. It is surrounded by fluid conveyed by the micropump. The fluid advantageously penetrates into the bearing gap of the radial bearings designed as plain bearings and serves here as a sliding, lubricating and/or flushing agent.
  • the fluid conveyed by the pump and guided through the bearing element can, in addition to the lubrication of the bearing surfaces described above, be subjected to temperature control (cooling or heating). the bearing element, the bearing surfaces and other functional units, such as magnets described below for driving the shaft.
  • the active lubrication and cooling and the better pressure distribution in the radial bearings result in low wear and an increased service life.
  • a kidney plate can be arranged on the side of the rotor receptacle opposite the bearing element, which has a fluid supply to and/or a fluid removal from the rotor receptacle (claim 3).
  • the kidney plate for the inner rotor or the outer rotor or both can form an axial bearing in the other axial direction.
  • the end face of the bearing element facing the rotor receptacle can serve as an axial bearing and sealing surface for the inner rotor and/or the outer rotor.
  • the end face of the kidney plate facing the rotor receptacle can serve as an axial bearing and sealing surface for the inner rotor and/or the outer rotor. Adequate storage of the rotor(s) in the axial direction is achieved through high-precision manufacturing of the rotors and the rotor holder.
  • the pump can have a ceramic or hard metal element which is arranged on the side of the bearing element opposite the rotor holder and forms an axial floating bearing for the shaft.
  • This particularly pin-shaped ceramic or hard metal element can be arranged in a particularly mushroom-shaped PTFE element, which acts as a spacer between the shaft and/or magnet on the one hand and the upper housing part on the other.
  • the shaft is preferably pushed towards the kidney plate by the fluid pressure generated by the micropump. There is therefore a positive shaft-hub connection between the shaft and the inner rotor, which allows the inner rotor to be axially displaced on the shaft.
  • At least one kidney-shaped cavity can be formed on the rotor-side end face of the bearing element. This serves to empty the delivery chamber on the high pressure side of the delivery chamber formed between the inner and outer rotors.
  • at least one kidney-shaped cavity can be formed on the rotor-side end face of the bearing element, which serves to fill the delivery chamber on the low-pressure side of the delivery chamber formed between the inner and outer rotors.
  • the cavities are used for fluidic control.
  • the end face advantageously has a low surface roughness and a closely tolerated flatness. It can serve in particular as a bearing and/or sealing surface for the rotor set.
  • Bearing element, shaft, rotor set consisting of inner and outer rotor and rotor holder as well as possibly other elements or units in contact with the shaft and the rotor set, such as the kidney plate, are preferably accommodated in a hermetically sealed housing and do not protrude from it.
  • a hermetic structure means that wear-prone dynamic seals (shaft seals) can be dispensed with. This results in a long service life, a long overall service life and increased product safety.
  • the pump can be operated with advantage in long-term applications and in chemistry with dangerous or volatile media.
  • Complete encapsulation of the functional components of the pump can be achieved by a two-part or multi-part housing with a lower housing and a housing cover.
  • the housing cover can in particular be arranged on the lower housing by means of a hold-down device. All moving functional parts or parts that come into direct contact with it and with the conveyed fluid are preferably completely accommodated in the housing and do not protrude from it. It is particularly advantageous for the individual components of the housing to be sealed against one another by means of a static seal, for example O-ring seals. It is not necessary to seal moving parts protruding from the housing with a complex and wear-prone dynamic seal.
  • the housing is designed so that medium can flow in through the lower housing and is then sucked in flowing through the kidney plate by the delivery chamber or chambers formed between the rotors.
  • the medium is then guided back to the lower housing via the fluid guide formed in the bearing element through the rotor holder and the kidney plate.
  • the fluid preferably flows through a cavity surrounded by the housing cover, in which the bearing element is at least partially arranged and, if necessary, further functional units of the micropump.
  • the conveyed fluid flows around the bearing element and, if necessary, these functional units, in particular the internal magnet system. It is particularly advantageous for fluid to reach the area of and onto the radial bearings of the shaft, where it causes lubrication and additionally or optionally flushing.
  • the fluid can also bring about temperature control of the bearing element and other functional units, in particular the internal magnet system.
  • the fluid preferably flows through a cavity surrounded by the housing cover, in which the bearing element is at least partially arranged and, if necessary, further functional units of the micropump.
  • the conveyed fluid flows around the bearing element and, if necessary, these functional units, in particular the internal magnet system. It is particularly advantageous for fluid to reach the area of the radial bearings and the radial bearings of the shaft, where it causes lubrication and additionally or optionally flushing.
  • the fluid can also bring about a temperature control of the bearing element and other functional units, such as in particular the housing cover.
  • the lower housing part can advantageously have fluid passages as inlet and outlet lines and be aligned in the radial direction with respect to the rotor receptacle, preferably by means of a pin element.
  • the bearing element can also be centered by the upper housing part relative to the lower housing part and the housing.
  • the pump can have a heating and/or cooling device, in particular a coolant guide for cooling the upper housing part surrounding the magnet.
  • a heating and/or cooling device in particular a coolant guide for cooling the upper housing part surrounding the magnet.
  • the pump can comprise an outer housing, which is provided in addition to the housing and, together with the upper part of the housing, forms a gap therebetween through which coolant flows, so that a temperature control medium can flow between the housing and the outer housing.
  • the pump can preferably be driven via a magnet system.
  • a magnet can be arranged or formed on the shaft or can interact with it.
  • This magnet hereinafter referred to as an internal magnet for easier understanding, since according to one form of the invention it is arranged in the housing of the pump, interacts with an external, impressed rotating magnetic field, so that the shaft can be driven in rotation. If there is any misalignment of the inner and outer magnet system, forces can be absorbed particularly well in the bearing element due to the shaft bearings described above.
  • the external magnet system is preferably located outside the housing and creates a rotating magnetic field, which in turn causes the internal magnet to rotate together with the shaft. With such a drive via a rotating magnetic field, the functional units of the pump surrounding the internal magnet, such as. B.
  • the bearing element and the housing cover are made of metal, since undesirable heating, for example due to eddy currents, can be avoided by the fluid conveyed by the pump and / or an additional coolant.
  • the rotation of the external magnet system outside the housing can be achieved by a permanent magnet system.
  • the internal magnet system located on the shaft and any external magnets are/are preferably made of higher-quality magnetic materials such as NdFeB or SmCo.
  • the internal magnet system can also be encapsulated so that aggressive media can also be conveyed.
  • Oxide ceramics, non-oxide ceramics or hard metal are preferably used as the material for the bearing element, the rotor holder, the kidney plate, the shaft and the rotors. This achieves a high level of stability.
  • the use of hardened steels or plastics is also possible.
  • Micropump 1 shown according to the invention is designed for a pressure range of 0 bar to 60 bar.
  • the pump 1 is a gear ring pump and comprises a shaft 2, on the lower end of which an inner rotor 3 is arranged in the figure (in Fig. 1 not shown).
  • the lower end of the shaft 2 is designed with a polygon-shaped receptacle 35 on which the inner rotor 3 is arranged in a rotationally fixed manner.
  • the shaft 2 is received in a bearing element 6 by means of a first radial bearing 4 and a second radial bearing 5 and stored in the radial direction.
  • a rotor receiving plate 10 is arranged as a rotor holder.
  • a kidney plate 11 is arranged on the side of the rotor receiving plate 10 opposite the bearing element 6.
  • the bearing element 6 is essentially cylindrical and has at its lower end in the figure an area 7 that is widened compared to its remaining diameter, so that an annular circumferential contact shoulder 8 is formed.
  • Bearing element 6, rotor receiving plate 10 and kidney plate 11 are aligned and centered in the radial direction via a sleeve 12 forming a housing.
  • the shaft 2 In the area of the first radial bearing 4 near the rotor, the shaft 2 has a first diameter. In the area of the second radial bearing 5 remote from the rotor, the shaft 2 has a diameter that is wider than the first diameter. Due to the large bearing diameter on the radial bearing 5 remote from the rotor, the bearing forces that occur are low.
  • the recess in the bearing element 6 that accommodates the shaft 2 is centered relative to its expanded area 7.
  • the rotor receiving plate 10 which is centered on the bearing element 6 and the shaft 2 by the sleeve 12, a recess which is uncentric by an eccentricity E is formed, in which an outer rotor 13 (in Fig. 1 not shown) also recorded off-center and in is mounted in the radial direction.
  • the inner rotor 3 which is arranged in a rotationally fixed manner on the shaft 2 and is eccentric relative to the recess in the rotor receiving plate 10 and the outer rotor 13, lies within the outer rotor 13.
  • the inner rotor 3 is provided with external teeth and the outer rotor 13 with internal teeth. These teeth are in meshing engagement with one another. Due to the eccentricity mentioned, a conveying cavity is formed between the inner and outer rotors, which cannot be seen in the figures.
  • the end face 9 of the bearing element 6 facing the inner rotor 3 is designed as an axial bearing for the inner rotor 3 and the outer rotor 10.
  • the end face 9 has a low surface roughness, for example in a range Ra 0.1, and a closely tolerated flatness.
  • a pin 36 is accommodated in a PTFE sleeve 37 in a containment shell 15 as a housing cover. Pin 36 and PTFE sleeve 37 form an axially floating bearing for the shaft 2 and serve as a spacer for an internal magnet 32 described below.
  • the height of the sleeve 12 in the axial direction of the shaft 2 is matched to the thicknesses of the kidney plate 11, the rotor receiving plate 10 and the expanded area 7 and is slightly smaller than the sum of the thicknesses of these components, so that they are centered over the sleeve 12 and over a lower housing part 14 and a containment pot 15 can be clamped in a defined manner as a housing cover in the axial direction.
  • the thickness of the inner and outer rotor in the axial direction of the shaft 2 is matched to the thickness of the rotor receiving plate 10, so that the inner and outer rotor in this and between the end face 9 of the bearing element 6 and the kidney plate 11 act as an axial bearing with the required smoothness and tightness at the same time can rotate.
  • the lower housing part 14 has an inlet passage 16 (low-pressure connection) and an outlet passage 17 (high-pressure outlet).
  • the containment pot 15 is in the in Fig. 2
  • the high-pressure variant of the pump shown is relatively solid and is clamped to the lower housing part 14 via a flange screw connection 18.
  • the containment pot 15 is less solid and is not arranged directly, but rather via a hold-down device 38 on the lower housing part 14 and clamped against the sleeve 12.
  • the hold-down device 38 is not in contact with fluid and can therefore be made of a less high-quality material.
  • the lower housing part 14 On its side facing the containment can 15, the lower housing part 14 has a recess in which the sleeve 12 and the elements kidney plate 11 and rotor receiving plate 10 accommodated therein are accommodated.
  • the lower housing part 14 is centered via this recess by the sleeve 12. It is also positioned angularly to the kidney plate 11 via a pin, not shown in the figures.
  • the kidney plate 11 is made of ceramic and has a low-pressure side inlet kidney 19 and a high-pressure side outlet opening 20. Due to the radial alignment of the kidney plate 11 to the lower housing part 14, the low-pressure side inlet passage 16 of the lower housing part 14 opens into the inlet kidney 19, while the outlet opening 20 is connected to the high-pressure side outlet passage 17.
  • the inlet kidney 19 is further designed in such a way that it overlaps and is fluidly connected to the central recess of the rotor receiving plate and in particular to the delivery chamber formed therein by the inner rotor 3 and the outer rotor 13.
  • two passages are formed in the rotor receiving plate 10, an inlet opening 21 on the low-pressure side and an outlet opening 22 on the high-pressure side.
  • An inlet kidney 23 is formed in the end face 9 of the bearing element 6.
  • the inlet kidney 19 of the kidney plate 11 and the inlet kidney 23 of the bearing element 6 overlap with the inlet opening 21 and are connected to one another.
  • the inlet kidney 23 of the bearing element 6 overlaps with the central recess of the rotor receiving plate and in particular with the delivery chamber formed therein by the inner rotor 3 and the outer rotor 13 and is fluidly connected to them.
  • a first low-pressure-side supply line to the delivery chamber is formed via the inlet passage 16 and the inlet kidney 19 and a second low-pressure-side supply line to the delivery chamber is formed via the inlet passage 16, the inlet kidney 19, the inlet opening 21 and the inlet kidney 23.
  • This second low-pressure-side supply line creates a hydraulic balance or a hydraulic compensation on the rotor set as well as a large low-pressure-side inflow. Furthermore, there is less cavitation.
  • a high-pressure-side fluid passage is formed in the bearing element 6. This essentially consists of an outlet kidney 24, a blind depression 25 introduced in the radial direction, a first edge recess 26 and a second edge recess 27 with an adjoining high-pressure outlet 28.
  • the high-pressure outlet 28 overlaps with the outlet opening 22 of the rotor receiving plate 10 and is connected via this and the outlet opening 20 fluidly connected to the high-pressure side outlet passage 17.
  • the first and second edge recesses 26, 27 are introduced into the bearing element 6 at the edge and are open towards the outside of the bearing element 6 in the axial direction (upwards in the figures) and in the radial direction.
  • a compensating kidney 39 is formed in the kidney plate 11 opposite the outlet kidney 24. This creates a hydraulic balance on the high pressure side or a hydraulic compensation on the rotor set.
  • the containment pot 15 is clamped to the lower housing part 14 via the screw connection 18 and is sealed from it via two O-ring seals 29, 30 in the sleeve 12.
  • the containment pot 15 has a central recess 31 in which the bearing element together with the shaft 2 mounted therein is accommodated with an internal magnet 32 described in more detail below.
  • the fluid is distributed via the gap 34 around the entire head area of the bearing element 6 into the space between the bearing element 6 and the containment can 15. Out This gap, the fluid subsequently flows via the second edge recess 27, the high-pressure outlet 28, the outlet opening 22 of the rotor receiving plate 10 and is the outlet opening 20 to the high-pressure side outlet passage 17.
  • both the bearing element 6 with all the functional units contained therein e.g. radial bearing 5 remote from the rotor
  • both the bearing element 6 with all the functional units contained therein e.g. radial bearing 5 remote from the rotor
  • the internal magnet 32 and the containment are tempered, in particular cooled.
  • the radial bearings 4, 5 are lubricated and/or flushed.
  • the internal magnet 32 is arranged in a rotationally fixed manner on the end of the shaft 2 remote from the rotor. It interacts with an external magnet system, not shown in the figures, which is arranged outside the hermetic housing of the pump formed by the lower housing part 14 and containment can 15.
  • the external magnet system generates a rotating magnetic field that causes the internal magnet 32, which is designed as a permanent magnet, to rotate about the axis of rotation of the shaft 2. This rotates together with the inner rotor 3 arranged on it, which meshes with the outer rotor 13 and sets it in rotation in the recess in the rotor receiving plate 10 that receives it. Due to the rotating magnetic field of the magnets, depending on the type of material used for the containment shell 15 and the bearing element 6, inductive heating occurs, with the resulting heat being able to be dissipated via the fluid flowing through the containment shell.
  • Another advantage of conveying the medium through the cavity surrounded by the containment can 15 is that failure of the pump due to collected gas bubbles can be ruled out. Dead space is minimized by the active flow through the entire pump including the containment can.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (12)

  1. Micropompe pour le transport d'un fluide d'une entrée basse pression (16) à une sortie haute pression (17), la pompe comprenant
    - un rotor intérieur (3) avec une denture extérieure ;
    - un rotor extérieur (13) avec une denture intérieure et
    - un élément de palier (6) ; la denture extérieure du rotor intérieur (3) s'engrenant avec la denture intérieure du rotor extérieur (13) et le rotor intérieur (3) étant disposé de manière solidaire en rotation sur un arbre (2) supporté par l'élément de palier (6) ;
    - le rotor extérieur (13) étant monté de manière excentrée par rapport au rotor intérieur (3) dans un logement de rotor (10) dans une direction radiale, afin d'ouvrir et de fermer de manière cyclique des chambres de transport entre le rotor intérieur et le rotor extérieur ;
    - l'élément de palier (6)
    - un passage de fluide (24, 25, 26, 27, 28) menant des chambres de refoulement à la sortie haute pression (17) pour le fluide refoulé ;
    - l'arbre (2) est logé radialement (4, 5) et forme un palier axial (9) pour le rotor intérieur et le rotor extérieur (3, 13), l'élément de palier (6) présentant un premier palier radial (5) éloigné du rotor et un deuxième palier radial (4) proche du rotor,
    - l'arbre (2) étant logé dans la direction radiale exclusivement par l'élément de palier (6) avec les deux paliers radiaux (4, 5) ;
    - caractérisé en ce que
    - l'arbre (2) présente un premier diamètre dans la zone du palier radial (4) proche du rotor, mais présente par contre un diamètre plus large ou plus grand que le premier diamètre dans la zone du palier radial (5) éloigné du rotor ;
    - et en ce que le passage de fluide dans l'élément de palier (6) est relié en termes d'écoulement aux paliers radiaux (4, 5) et l'arbre (2) fait saillie à travers une section (25) du passage de fluide.
  2. Micropompe selon la revendication 1, dans laquelle le diamètre du premier palier radial (5) est d'au moins 6 mm, de préférence d'au moins 6,5 mm, et le diamètre du deuxième palier radial (4) est d'au plus 5 mm.
  3. Micropompe selon l'une des revendications précédentes, dans laquelle, sur le côté du logement de rotor (10) opposé à l'élément de palier (6), est disposée une plaque réniforme (11) qui présente une amenée de fluide (19) vers et/ou une évacuation de fluide (20) depuis le logement de rotor (10).
  4. Micropompe selon l'une des revendications précédentes, dans laquelle l'élément de palier (6) et le logement de rotor (10), en particulier également une plaque de rein (11), sont centrés axialement l'un par rapport à l'autre, de préférence par un boîtier (12) disposé autour.
  5. Micropompe selon la revendication 3 ou 4, dans laquelle la plaque rénale (11) forme un palier axial pour le rotor interne et/ou le rotor externe et/ou l'arbre (2).
  6. Micropompe selon l'une quelconque des revendications précédentes, dans laquelle seul ou exclusivement l'élément de palier (6) comprend les deux paliers radiaux (4, 5) pour l'arbre (2).
  7. Micropompe selon l'une quelconque des revendications précédentes, dans laquelle
    - au moins une cavité (24) en forme de haricot est formée sur la surface frontale (9) côté rotor de l'élément de palier (6), pour une vidange côté haute pression des chambres de transport formées en continu entre le rotor intérieur (3) et le rotor extérieur (13) ;
    et/ou
    - au moins une cavité (23) en forme de haricot est formée sur la surface frontale côté rotor de l'élément de palier (6), pour un remplissage côté basse pression des chambres de transport formées en continu entre le rotor intérieur (3) et le rotor extérieur (13).
  8. Micropompe selon la revendication 1, dans laquelle il est prévu un pot à fente (15) qui entoure une cavité et, avec le fluide s'écoulant dans la cavité, l'élément de palier (6) avec toutes les unités fonctionnelles qu'il contient peut être mis en température, en particulier peut être refroidi.
  9. Micropompe selon la revendication 8, dans laquelle les unités fonctionnelles sont le palier radial (5) éloigné du rotor, un aimant intérieur (32) et le pot à entrefer (15).
  10. Micropompe selon la revendication 8 ou 9, dans laquelle le fluide s'écoulant dans la cavité pour le refroidissement, le rinçage et/ou la lubrification est entouré par le pot à fente (15).
  11. Micropompe selon l'une des revendications 8 à 10, dans laquelle le fluide s'écoulant dans l'espace intermédiaire entre l'élément de palier (6) et le pot arrière (15) tempère, notamment refroidit, l'élément de palier (6) avec toutes les unités fonctionnelles qu'il contient.
  12. Micropompe selon l'une des revendications précédentes, dans laquelle il est prévu comme entraînement un système magnétique.
EP12728264.8A 2011-06-30 2012-06-15 Micropompe, élément palier pour une micropompe et procédé pour la faire fonctionner Active EP2726740B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011051486.4A DE102011051486B4 (de) 2011-06-30 2011-06-30 Pumpenanordnung mit Mikropumpe und Lagerelement
PCT/EP2012/061514 WO2013000745A2 (fr) 2011-06-30 2012-06-15 Micropompe, élément palier pour une micropompe et procédé pour la faire fonctionner

Publications (2)

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EP2726740A2 EP2726740A2 (fr) 2014-05-07
EP2726740B1 true EP2726740B1 (fr) 2023-10-11

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US (1) US9404492B2 (fr)
EP (1) EP2726740B1 (fr)
CN (1) CN103732921B (fr)
DE (1) DE102011051486B4 (fr)
WO (1) WO2013000745A2 (fr)

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DE102016121240A1 (de) * 2016-11-07 2018-05-09 Nidec Gpm Gmbh Elektrische Gerotorpumpe und Herstellungsverfahren für dieselbe
FR3060669B1 (fr) * 2016-12-20 2020-11-27 Coutier Moulage Gen Ind Pompe a engrenage a plaques et pions de centrage hydrauliques.
IT201700067423A1 (it) * 2017-06-16 2018-12-16 Gkn Sinter Metals Ag Disposizione di pompa e procedimento per la produzione di una disposizione di pompa.
US11448211B2 (en) * 2018-08-31 2022-09-20 Toyoda Gosei Co., Ltd. Oil pump including gap between flange portion of tubular core and flange-opposing portion of resin housing
DE102019101455A1 (de) 2019-01-21 2020-07-23 Hnp Mikrosysteme Gmbh Selbstspülende Mikropumpe
DE102019102073A1 (de) * 2019-01-28 2020-07-30 Fresenius Medical Care Deutschland Gmbh Zahnradpumpe
CN117605678B (zh) * 2023-12-26 2024-06-14 苏州帕夫尔流体科技有限公司 一种齿轮腔与泵盖一体式结构

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CA1217089A (fr) 1982-03-23 1987-01-27 Hollis N. White, Jr. Dispositif hydraulique tournant a couloirs de circulation de fluide dans le corps du rotor
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Also Published As

Publication number Publication date
EP2726740A2 (fr) 2014-05-07
CN103732921B (zh) 2017-08-11
US9404492B2 (en) 2016-08-02
WO2013000745A2 (fr) 2013-01-03
CN103732921A (zh) 2014-04-16
WO2013000745A4 (fr) 2013-12-19
DE102011051486B4 (de) 2023-06-01
US20150132172A1 (en) 2015-05-14
DE102011051486A1 (de) 2013-01-03
WO2013000745A3 (fr) 2013-10-24

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