EP2726740B1 - Micropump, bearing element for a micropump, and working method - Google Patents
Micropump, bearing element for a micropump, and working method Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- bearing element
- bearing
- shaft
- fluid
- 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.)
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Links
- 239000012530 fluid Substances 0.000 claims description 59
- 210000003734 kidney Anatomy 0.000 claims description 49
- 238000001816 cooling Methods 0.000 claims description 8
- 238000011010 flushing procedure Methods 0.000 claims description 5
- 230000001050 lubricating effect Effects 0.000 claims description 3
- 238000007789 sealing Methods 0.000 description 8
- 238000005461 lubrication Methods 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 5
- 239000002184 metal Substances 0.000 description 4
- 239000000919 ceramic Substances 0.000 description 3
- 239000002826 coolant Substances 0.000 description 3
- 230000010354 integration Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 239000004810 polytetrafluoroethylene Substances 0.000 description 3
- 229920001343 polytetrafluoroethylene Polymers 0.000 description 3
- 239000007787 solid Substances 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 230000003746 surface roughness Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005538 encapsulation Methods 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 229910001172 neodymium magnet Inorganic materials 0.000 description 1
- 239000011225 non-oxide ceramic Substances 0.000 description 1
- 229910052575 non-oxide ceramic Inorganic materials 0.000 description 1
- 239000011224 oxide ceramic Substances 0.000 description 1
- 229910052574 oxide ceramic Inorganic materials 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 229920003023 plastic Polymers 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 229910000938 samarium–cobalt magnet Inorganic materials 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Images
Classifications
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- 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.
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Description
Die Erfindung betrifft eine Mikropumpe, insbesondere von kleiner und kleinster Baugröße. Eine solche Pumpe dient einer Förderung von Fluid oder Medium von einem Niederdruckeinlass zu einem Hochdruckauslass und besitzt eine Größenordnung von weniger als 30mm, vorzugsweise von weniger als 20 mm und besonders bevorzugt von weniger als 10 mm (Höchstmaß einer Abmessung einer Mikropumpe, insbesondere Höchstmaß des Außendurchmessers des Außenrotors).The invention relates to a micropump, in particular of small and smallest size. Such a pump 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).
Eine gattungsgemäße Mikropumpe arbeitet nach dem Prinzip einer Zahnradpumpe. Sie weist einen Innenrotor mit einer Außenverzahnung und einen Außenrotor mit einer Innenverzahnung auf. Die Außenverzahnung des Innenrotors steht mit der Innenverzahnung des Außenrotors in kämmendem Eingriff. Die beiden Achsen von Innen- und Außenrotor sind gegeneinander um eine Exzentrizität versetzt angeordnet. Aufgrund dieses Achsversatzes bilden die beiden in Eingriff stehenden Rotoren zwischen sich eine Pumpkammer oder mehrere Pumpkammern aus, die sich aufgrund von Rotation der Rotoren hinsichtlich ihrer Größe und Lage zyklisch ändert bzw. ändern.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.
Eine solche Mikropumpe ist beispielsweise aus der
Gattungsgemäße Pumpen und Mikropumpen, insbesondere der vorbeschriebenen Art, sind in einem Gehäuse aufgenommen, das die Pumpe schützt und gegenüber der Umgebung abdichtet. Eine mögliche Gehäuseform zur Aufnahme einer solchen Mikropumpe ist aus einem Datenblatt "Pumpenkopf mzr® 4600" der HNP Mikrosysteme GmbH bekannt. Dieser Pumpenkopf besitzt eine Welle, die stirnseitig zur Ankopplung eines Motors hervorsteht. Fünf scheibenförmige Elemente bilden als Zylinderelemente einen Gehäuseaufbau, beginnend mit einer Gehäusewellendichtung, einer Ausgleichsnierenplatte und einer Rotoraufnahmeplatte, gefolgt von einer Fluidführung und einem Verschlussdeckel. In der Rotoraufnahmeplatte ist eine Bohrung vorgesehen, die gegenüber der Achse der Welle zum Antrieb des Innenrades exzentrisch versetzt ist, so dass der Außenrotor in der Rotoraufnahmeplatte außermittig gelagert ist. Auf einer Seite von Außenrotor und Innenrotor liegt die Ausgleichsnierenplatte und auf der gegenüberliegenden Seite die Fluidführungsplatte jeweils stirnseitig direkt daran an. Beide Platten besitzen zum Rotor gerichtet eine Eingangs- und Ausgangsniere auf der Seite der Fluidzuführung und spiegelbildlich angeordnete Ausgleichsnieren zur Schaffung eines hydraulischen Gleichgewichts auf der gegenüberliegenden Seite. Damit ergibt sich ein U-förmiger Fluidstrom vom Einlass über die Einlassniere zu den rotierenden Pumpenkammern, hin zum Auslass und zurück zu dem in dem Datenblatt mzr® 4600 radial herausgeführten Auslass.Generic pumps and micropumps, in particular of the type described above, 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. On one side of the outer rotor and inner rotor, 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.
Bei aus dem Stand der Technik bekannten Pumpen mit Gehäuse ist es von Nachteil, dass diese zahlreiche Einzelbauteile aufweisen, insbesondere solche, die für einen zuverlässigen Betrieb der Pumpe mit besonderer Präzision gefertigt sein müssen. Es muss mit sehr engen Toleranzen gefertigt werden, damit die durch die zahlreichen Einzelteile letztlich bestimmte Aufnahme der Rotoren im Gehäuse mit ausreichender Dichtigkeit bei gleichzeitig guter Lagerung erfolgen kann. Des Weiteren muss jedes an ein anderes Einzelteil gefügte Bauelement hinreichend gedichtet sein, insbesondere, wenn es mit bewegten Elementen der Pumpe in Kontakt steht oder von diesen durchgriffen ist. Wellendichtungen müssen dynamisch ausgeführt sein, was zu einem erhöhtem Wartungsaufwand und Kosten führt. Die Montage ist durch die hohe Teilezahl erschwert.The disadvantage of pumps with housings known from the prior art is that they have numerous individual components, in particular those that must be manufactured with particular precision for reliable operation of the pump. It must be manufactured with very tight tolerances so that the rotors in the housing, which are ultimately determined by the numerous individual parts, can be accommodated with sufficient tightness and at the same time good storage. Furthermore, every component joined to another individual part must be sufficiently sealed, especially if it is in contact with moving elements of the pump or is penetrated by them. Shaft seals must be designed dynamically, which leads to increased maintenance effort and costs. Assembly is difficult due to the high number of parts.
Ausgehend von dem zuvor beschriebenen Stand der Technik liegt der vorliegenden Erfindung die Aufgabe zugrunde, Mikropumpe vorzusehen, die mit einer minimierten Anzahl von Präzisionsteilen und einfacher Montage mit hohen Präzisionsanforderungen fertigungsoptimiert und kostengünstig realisiert werden kann. Die Dichtung der Pumpe soll vereinfacht sein und insbesondere ohne dynamische Dichtungen auskommen. Schließlich soll eine Schmierung, Spülung und Temperierung der Lager der Mikropumpe trotz deren kleinen Abmessungen sicher und einfach realisiert werden.Based on the prior art described above , 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. Ultimately, lubrication, flushing and temperature control of the bearings of the micropump should be implemented safely and easily despite their small dimensions.
Die beanspruchte Mikropumpe zur Förderung von Fluid von einem Niederdruckeinlass zu einem Hochdruckauslass, hat einen Innenrotor mit einer Außenverzahnung, einen Außenrotor mit einer Innenverzahnung und ein Lagerelement, wobei die Außenverzahnung des Innenrotors mit der Innenverzahnung des Außenrotors kämmt. Der Innenrotor ist drehfest auf einer Welle angeordnet, der Außenrotor ist exzentrisch zum Innenrotor in einer Rotoraufnahme in radialer Richtung gelagert, so dass zwischen Innen- und Außenrotor-Fluidkammern als Förderkammern ausgebildet werden, das Lagerelement einen von den Förderkammern zum Hochdruckauslass führenden Fluiddurchlass für gefördertes Fluid aufweist und das Lagerelement zwei Radiallager für die Welle und ein Axiallager für den Innen- und den Außenrotor in wenigstens einer axialen Richtung ausbildet.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.
Innen- und Außenrotor bilden in einer Ausführungsform der Erfindung eine Zahnring- oder Gerotorpumpe oder eine Innenzahnradpumpe aus. Der außenverzahnte Innenrotor ist in dem innenverzahnten Außenrotor aufgenommen. Die Drehachsen von Innenrotor und Außenrotor sind in radialer Richtung um eine Exzentrizität versetzt. Dies geschieht vorzugsweise über eine entsprechende Positionierung der den Innenrotor tragenden Welle relativ zu der den Außenrotor lagernden Rotoraufnahme. Beispielsweise können das Lagerelement, und damit auch die darin radial gelagerte Welle, und die Rotoraufnahme in axialer Richtung zueinander zentriert sein. Eine den Außenrotor aufnehmende und lagernde Ausnehmung in der Rotoraufnahme ist dann nicht zentrisch in dieser angeordnet, sondern um die genannte Exzentrizität verschoben. Die axiale Zentrierung oder Lagepositionierung von Lagerelement und Rotoraufnahme zueinander kann über ein zumindest teilweise darum angeordnetes Gehäuse, insbesondere ringförmiges oder hülsenartiges Gehäuse, erfolgen. Dieses kann außerdem weitere Elemente der Pumpe relative zu Lagerelement und Rotoraufnahme ausrichten und zentrieren, beispielsweise die Nierenplatte. Eine Ausrichtung der Winkelposition von Lagerelement, Rotoraufnahme sowie ggf. Nierenplatte zueinander um die axiale Richtung kann vorzugsweise mittels eines sie durchragenden Stiftelements oder ähnlichem erfolgen. Die Dicke von Innen- sowie Außenrotor in axialer Richtung ist nach der Erfindung auf die Dicke der Rotoraufnahme in axialer Richtung abgestimmt. Sie kann insbesondere ein geringes Untermaß aufweisen, vorzugsweise in einem Bereich von 2 bis 10 µm. Der Innenrotor kann nach einer besonderen Form der Erfindung über die Welle angetrieben sein und seinerseits den Außenrotor antreiben.In one embodiment of the invention, 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. For example, 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. According to the invention, 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. In particular, it can have a slight undersize, preferably in a range of 2 to 10 μm. According to a special form of the invention, the inner rotor can be driven via the shaft and in turn drive the outer rotor.
Aufgrund der exzentrischen Anordnung von Innen- und Außenrotor zueinander liegt zwischen diesen ein freies Volumen vor, das eine Förderkammer oder mehrere Förderkammern bildet. Diese erweitert oder erweitern sich in Drehrichtung auf der Saugseite, nehmen dort Fluid auf und fördern es herüber auf die Druckseite, auf der sich die Förderkammer oder -kammern im Zuge der weiteren Drehung stetig verkleinert bzw. verkleinern. Nachfolgend wird die Förderkammer wieder zurück auf die Saugseite geführt. Hier beginnt sie sich wieder stetig mit der Drehbewegung zu öffnen, so dass sich der Zyklus schließt. Bei einer Gerotorpumpe weisen Innen- und Außenrotor unterschiedliche Zahnzahlen auf. Die Zähne wälzen aufeinander ab und bilden dabei auf jeder Seite eines Zahnzwischenraums Dichtlinien aus, so dass jeder Zahnzwischenraum eine Förderkammer darstellt. Die für eine Förderkammer vorstehend beschriebene Bewegung gilt simultan für alle bestehenden Förderkammern einer Gerotorpumpe, die zu einem momentanen Zeitpunkt jeweils ein unterschiedliches Volumen zwischen einem jeweiligen Paar von Dichtlinien haben, so dass sich bei Betrieb der Pumpe ein höchst gleichmäßiger Förderstrom bei hoher Fähigkeit zur Miniaturisierung des gesamten Mikrosystemaufbaus ergibt. Im Falle einer Zahnringpumpe ist in dem freien Volumen zwischen Innen- und Außenrotor ein deren Zahnzwischenräume bei Rotation abdichtendes, meist sichelförmiges Dichtelement angeordnet. Die zwischen Innen- und Außenrotor gebildeten Förderkammern fördern Fluid von einem Niederdruckfluideinlass oder einer Einlassniere zu einem Hockdruckfluidauslass oder einer Auslassniere.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. In a gerotor pump, 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. The movement described above for 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. In the case of 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.
Durch die der Erfindung innewohnende Integration zahlreicher Funktionen in das Lagerelement als ein einziges Bauteil wird in vorteilhafter Weise die Toleranzkette verkürzt. Einzelteile der Pumpe, wie beispielsweise Innen- und Außenrotor, Rotoraufnahme, Lagerelement und ggf. Nierenplatte sind so gestaltet, dass die notwendige aber kostenintensive Präzision auf eine möglichst geringe Anzahl von Teilen konzentriert ist. Die durch den kompakten Aufbau kurzen Toleranzketten ermöglichen eine Vergrößerung der Toleranzen der einzelnen Bauteile, was zu einer weiteren Vereinfachung der Fertigung und Senkung des Fertigungsaufwands und der Produktionskosten führt.The integration of numerous functions into the bearing element as a single component, which is inherent in the invention, advantageously shortens the tolerance chain. 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.
Kernstück der Pumpe bildet das Lagerelement, die Welle, der Rotorsatz aus Innen- und Außenrotor und die Rotoraufnahme ggf. ergänzt durch die Nierenplatte. Die für einen ausreichenden hydraulischen Wirkungsgrad benötigte Präzision wird durch eine präzise Lagerausführung sowie hochpräzise gefertigte Rotoren erreicht. Das Lagerelement ist das Bauteil mit der größten Funktionsintegration. Es bildet nach der Erfindung gleichzeitig ein Radiallager für die Welle, ein Axiallager für den Innen- und Außenrotor in wenigstens einer axialen Richtung sowie einen Fluiddurchlass für von den Rotoren gefördertes Fluid aus. Durch diese Funktionsintegration kann im Vergleich zu aus dem Stand der Technik bekannten Pumpen die Anzahl von Bauelementen und damit auch die Anzahl von zwischen diesen liegenden Fügestellen in vorteilhafter Weise verringert werden. Des Weiteren sind mit Vorteil alle pumpenspezifischen Toleranzen in einer geringen Anzahl von Präzisionsteilen, nämlich dem Lagerelement, der Rotoraufnahme, der Welle und dem Rotorsatz sowie ggf. Gehäuse vereint. Durch die Verlagerung der Präzision in eine begrenzte Anzahl von Teilen wird der Fertigungsaufwand wesentlich verringert, da weniger Teile hochpräzise zu fertigen sind und es werden für die Fertigung der Einzelteile und deren Montage Kosten eingespart. Schließlich ist durch die Erfindung eine kurze Toleranzkette realisiert. Diese erstreckt sich von dem auf der Welle sitzenden Innenrotor über den Außenrotor und die Rotoraufnahme. Durch den kompakten Aufbau sind kurze Kraftflusswege realisiert.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. Furthermore, all pump-specific tolerances are advantageously combined in a small number of precision parts, namely the bearing element, the rotor holder, the shaft and the rotor set and, if necessary, the housing. By shifting precision to a limited number of parts, the manufacturing effort is significantly reduced because fewer parts have to be manufactured with high precision and costs are saved for the production of the individual parts and their assembly. Finally, the invention achieves a short tolerance chain. This extends from the inner rotor sitting on the shaft over the outer rotor and the rotor holder. The compact structure ensures short power flow paths.
Die radiale Lagerung der Welle und damit des darauf angeordneten Innenrotors erfolgt nach der Erfindung durch das bzw. im Lagerelement. Die Welle ist in radialer Richtung ausschließlich und direkt durch das Lagerelement gelagert. Das oder die Radiallager ist bzw. sind vorzugsweise auf einer Seite der Rotoranordnung platziert und als Gleitlager ausgebildet. Sie können insbesondere außerhalb der eigentlichen Mikropumpe angeordnet sein, so dass die Lagerdurchmesser entsprechend groß ausgeführt sein können. Insbesondere kann das bzw. können die Radiallager der Welle außerhalb der im Lagerelement ausgebildeten Fluidführung ausgebildet sein, wodurch wiederum der Durchmesser des Lagers oder der Lager wenig beschränkt ist. Insgesamt sind größere Lagerdurchmesser möglich und es kommt zu einer Minimierung von auftretenden Lagerkräften und infolgedessen zu größerer Standzeit und Verlässlichkeit der Pumpe. Der Schmierfilm im Lager baut sich durch höhere Gleitgeschwindigkeiten infolge größeren Lagerumfangs schneller auf.According to the invention, 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.
Das Lagerelement weist ein erstes Radiallager und ein zweites Radiallager auf, wobei der Durchmesser des ersten Radiallagers größer ist als der Durchmesser des zweiten Radiallagers. Nach einer besonderen Ausführungsform beträgt der Durchmesser des ersten Radiallagers wenigstens 6 mm, vorzugsweise wenigstens 6,5 mm, und der Durchmesser des zweiten Radiallagers höchstens 5 mm. Durch die unterschiedlich großen Lagerdurchmesser kann eines der beiden Lager auf die kleinen Abmessungen der Mikropumpe und insbesondere auf den Durchmesser des Innenrotors abgestimmt sein. Der Lagerdurchmesser (des kleineren Radiallagers) ist durch die Abmessungen des auf der Welle angeordneten Innenrotors bestimmt. Er ist montagebedingt größer als der Innendurchmesser oder die Innenabmessung des auf der Welle angeordneten Innenrotors. Um eine Anlage und Abdichtung des Innenrotors am Lagerelement zu ermöglichen, muss er kleiner als der Fußkreisdurchmesser des Innenrotors sein. Wegen der bei Mikropumpen kleinen Abmessungen des Innenrotors ist der Lagerdurchmesser des innenrotorseitigen Lagers daher beschränkt. Das andere Lager, nämlich das mit größerem Lagerdurchmesser, ist hingegen geeignet, verhältnismäßig hohe Lagerkräfte aufzunehmen.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. According to a particular embodiment, 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. 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.
Gemäß der Erfindung ist der Fluiddurchlass strömungstechnisch mit wenigstens einem Radiallager verbunden. Vorzugsweise sind die Radiallager in Form von Vertiefungen oder Bohrungen, insbesondere Durchgangsöffnungen bzw. Durchgangsbohrungen in dem Lagerelement ausgebildet. Deren radiale Innenflächen bilden Lagerflächen entsprechender Oberflächengüte und Genauigkeit für die Welle aus. Die im Lagerelement ausgebildeten Radiallager und der Fluiddurchlass sind erfindungsgemäß so ausgebildet und angeordnet, dass sie einander teilweise kreuzen und überlappen. Die Welle ragt dann durch den Fluiddurchlass hindurch. Sie wird von durch die Mikropumpe geförderten Fluid umspült. Das Fluid dringt mit Vorteil in den Lagerspalt der als Gleitlagerlager ausgebildeten Radiallager ein und dient hier als Gleit-, Schmier- und/oder Spülmittel.According to the invention, 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. According to the invention, 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.
Es ist von Vorteil, dass außerhalb oder entfernt der eigentlichen Funktionseinheiten der Pumpe große Lagerflächen mit aktiver Schmierung realisiert werden können. Das von der Pumpe geförderte und durch das Lagerelement geführte Fluid kann nämlich neben der vorstehend beschriebenen Schmierung der Lagerflächen einer Temperierung (Kühlung oder Erwärmung) des Lagerelements, der Lagerflächen und weiterer Funktionseinheiten, wie beispielsweise nachfolgend noch beschriebene Magnete zum Antrieb der Welle, dienen. Aus der aktiven Schmierung und Kühlung und der besseren Druckverteilung in den Radiallagern resultieren geringer Verschleiß sowie eine erhöhte Lebensdauer.It is advantageous that large bearing surfaces with active lubrication can be realized outside or away from the actual functional units of the pump. 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.
Mit Vorteil kann nach einer besonderen Ausführungsform der Erfindung auf der dem Lagerelement gegenüberliegenden Seite der Rotoraufnahme eine Nierenplatte angeordnet sein, die eine Fluidzuführung zur und/oder eine Fluidabführung von der Rotoraufnahme aufweist (Anspruch 3).Advantageously, according to a special embodiment of the invention, 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).
Während das Lagerelement ein Axiallager in eine Richtung ausbildet, kann die Nierenplatte für den Innenrotor oder den Außenrotor oder beide ein Axiallager in die andere Axialrichtung ausbilden. Nach einer Ausführungsform der Erfindung kann die der Rotoraufnahme zugewandte Stirnfläche des Lagerelements als Axiallager- und Dichtfläche für den Innenrotor und/oder den Außenrotor dienen. Zusätzlich oder alternativ kann die der Rotoraufnahme zugewandte Stirnfläche der Nierenplatte als Axiallager - und Dichtfläche für den Innenrotor und/oder den Außenrotor dienen. Eine adäquate Lagerung des oder der Rotoren in axialer Richtung wird durch eine hochpräzise Fertigung der Rotoren und der Rotoraufnahme erzielt. Zusätzlich oder alternativ zu der Axiallagerung an der Nierenplatte kann die Pumpe ein Keramik- oder Hartmetallelement aufweisen, das auf der der Rotoraufnahme gegenüber liegenden Seite des Lagerelements angeordnet ist und ein axiales Loslager für die Welle ausbildet. Dieses insbesondere stiftförmige Keramik- oder Hartmetallelement kann in einem insbesondere pilzförmigen PTFE-Element angeordnet sein, das als Abstandshalter zwischen Welle und/oder Magnet einerseits und dem Gehäuseoberteil andererseits wirkt. Die Welle wird vorzugsweise durch den durch die Mikropumpe erzeugten Fluiddruck in Richtung der Nierenplatte gedrückt. Zwischen Welle und Innenrotor besteht daher eine formschlüssige Welle-Naben-Verbindung, die eine axiale Verschiebung des Innenrotors auf der Welle zulässt.While the bearing element forms an axial bearing in one direction, the kidney plate for the inner rotor or the outer rotor or both can form an axial bearing in the other axial direction. According to one embodiment of the invention, 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. Additionally or alternatively, 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. In addition or as an alternative to the axial bearing on the kidney plate, 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.
Nach einer anderen Ausführungsform der Erfindung kann an der rotorseitigen Stirnfläche des Lagerelements wenigstens eine nierenförmige Kavität ausgebildet sein. Diese dient der hochdruckseitigen Entleerung der Förderkammer der zwischen Innen- und Außenrotor ausgebildeten Förderkammer. Alternativ oder zusätzlich kann an der rotorseitigen Stirnfläche des Lagerelements wenigstens eine nierenförmige Kavität ausgebildet sein, die der niederdruckseitigen Befüllung der Förderkammer der zwischen Innen- und Außenrotor ausgebildeten Förderkammer dient. Die Kavitäten dienen der fluidischen Steuerung. Die Stirnfläche hat mit Vorteil eine geringe Oberflächenrauheit und eine eng tolerierte Ebenheit. Sie kann insbesondere als Lager- und/oder Dichtfläche für den Rotorsatz dienen. Lagerelement, Welle, Rotorsatz aus Innen- und Außenrotor und Rotoraufnahme sowie ggf. weitere mit der Welle und dem Rotorsatz in Kontakt stehende Elemente oder Einheiten wie z.B. die Nierenplatte sind vorzugsweise in einem hermetisch dichten Gehäuse aufgenommen und ragen aus diesem nicht heraus. Durch einen solchen hermetischen Aufbau kann auf verschleißanfällige dynamische Dichtungen (Wellendichtungen) verzichtet werden. Es ergeben sich hohe Standzeiten, eine hohe Gesamtlebensdauer und eine erhöhte Produktsicherheit. Die Pumpe kann mit Vorteil in Langzeitanwendungen und in der Chemie mit gefährlichen oder leicht flüchtigen Medien betrieben werden. Eine vollständige Kapselung der Funktionsbauteile der Pumpe, insbesondere von Lagerelement, Rotoraufnahme, Nierenplatte, Welle und Rotorsatz kann durch ein zwei- oder mehrteiliges Gehäuse mit einem Untergehäuse und einem Gehäusedeckel erzielt werden. Der Gehäusedeckel kann insbesondere mittels eines Niederhalters am Untergehäuse angeordnet sein. Alle bewegten Funktionsteile oder damit und mit dem geförderten Fluid direkt in Kontakt gelangende Teile sind vorzugsweise vollständig in dem Gehäuse aufgenommen und ragen aus diesem nicht heraus. Mit besonderem Vorteil können die einzelnen Bestandteile des Gehäuses durch statische Dichtung, z.B. O-RingDichtungen, gegeneinander abgedichtet sein. Eine Abdichtung aus dem Gehäuse ragender bewegter Teile mit aufwändiger und verschleißanfälliger dynamischer Dichtung ist nicht notwendig. Bei einer Form der Erfindung ist das Gehäuse so gestaltet, dass Medium durch das Untergehäuse einströmen kann und dann durch die Nierenplatte fließend von der zwischen den Rotoren ausgebildeten Förderkammer oder den Förderkammern angesaugt wird. Das Medium wird anschließend über die im Lagerelement ausgebildete Fluidführung durch die Rotoraufnahme und die Nierenplatte zurück zum Untergehäuse geführt. Vorzugsweise strömt das Fluid dabei durch einen vom Gehäusedeckel umgebenen Hohlraum, in dem das Lagerelement zumindest teilweise sowie gegebenenfalls weitere Funktionseinheiten der Mikropumpe angeordnet sind. Dabei umströmt das geförderte Fluid das Lagerelement und gegebenenfalls diese Funktionseinheiten, insbesondere das Innenmagnetsystem. Mit besonderem Vorteil gelangt Fluid in den Bereich der und an die Radiallager der Welle und bewirkt dort eine Schmierung und zusätzlich oder optional eine Spülung. Auch kann das Fluid eine Temperierung des Lagerelements und weiterer Funktionseinheiten wie insbesondere des Innenmagnetsystems bewirken. Vorzugsweise strömt das Fluid dabei durch einen vom Gehäusedeckel umgebenen Hohlraum, in dem das Lagerelement zumindest teilweise sowie gegebenenfalls weitere Funktionseinheiten der Mikropumpe angeordnet sind. Dabei umströmt das geförderte Fluid das Lagerelement und gegebenenfalls diese Funktionseinheiten, insbesondere das Innenmagnetsystem. Mit besonderem Vorteil gelangt Fluid in den Bereich der Radiallager und in die Radiallager der Welle und bewirkt dort eine Schmierung sowie zusätzlich oder optional eine Spülung. Auch kann das Fluid eine Temperierung des Lagerelements und weiterer Funktionseinheiten wie insbesondere des Gehäusedeckels bewirken. Das Gehäuseunterteil kann mit Vorteil Fluiddurchlässe als Zu- und Ableitung aufweisen und gegenüber der Rotoraufnahme in radialer Richtung ausgerichtet sein, vorzugsweise mittels eines Stiftelements. Das Lagerelement kann des Weiteren durch das Gehäuseoberteil gegenüber dem Gehäuseunterteil und dem Gehäuse zentriert sein.According to another embodiment of the invention, 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. Alternatively or additionally, 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. Such 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, in particular the bearing element, rotor holder, kidney plate, shaft and rotor set, 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. In one form of the invention, 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.
Nach einer anderen Ausführungsform der Erfindung kann die Pumpe eine Heiz- und/oder Kühleinrichtung aufweisen, insbesondere eine Kühlmittelführung zur Kühlung des den Magneten umgebenden Gehäuseoberteils. Durch die Integration einer Heizung/Kühlung im Pumpengehäuse kann die bspw. Kaltstartfähigkeit der Pumpe bzw. deren temperierter Betrieb sichergestellt werden. Das begünstigt den Einsatz der Pumpe in der Chemischen Industrie sowie dem Maschinen- und Anlagenbau. Beispielsweise kann die Pumpe ein Außengehäuse umfassen, das zusätzlich zu dem Gehäuse vorgesehen ist und zusammen mit dem Gehäuseoberteil einen Spaltraum dazwischen ausbildet, der von Kühlmittel durchströmt ist, so dass zwischen Gehäuse und Außengehäuse ein Temperierungsmedium strömen kann.According to another embodiment of the invention, the pump can have a heating and/or cooling device, in particular a coolant guide for cooling the upper housing part surrounding the magnet. By integrating heating/cooling in the pump housing, the cold start capability of the pump or its temperature-controlled operation can be ensured. This favors the use of the pump in the chemical industry as well as mechanical and plant engineering. For example, 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.
Der Antrieb der Pumpe kann bevorzugt über ein Magnetsystem erfolgen. Insbesondere kann auf der Welle ein Magnet angeordnet oder ausgebildet sein oder mit dieser zusammenwirken. Dieser Magnet, im Folgenden zum einfacheren Verständnis als Innenmagnet bezeichnet, da er nach einer Form der Erfindung in dem Gehäuse der Pumpe angeordnet ist, wirkt mit einem äußeren aufgeprägten rotierenden Magnetfeld zusammen, so dass die Welle rotatorisch antreibbar ist. Bei einem etwaigen Versatz von Innen- und Außenmagnetsystem können Kräfte aufgrund der vorstehend beschriebenen Lager der Welle im Lagerelement besonderes gut aufgefangen werden. Das Außenmagnetsystem befindet sich vorzugsweise außerhalb des Gehäuses und erzeugt ein rotierendes Magnetfeld, das wiederum den Innenmagneten zusammen mit der Welle rotieren lässt. Bei einem solchen Antrieb über ein rotierendes Magnetfeld können nach der Erfindung ohne Weiteres die den Innenmagneten umgebenden Funktionseinheiten der Pumpe, wie z. B. das Lagerelement sowie der Gehäusedeckel, aus Metall bestehen, da durch das durch die Pumpe geförderte Fluid und/oder ein zusätzliches Kühlmittel eine unerwünschte Erwärmung zum Beispiel durch Wirbelströme vermieden werden kann. Die Drehung des äußeren Magnetsystems außerhalb des Gehäuses kann durch ein Permanentmagnetsystem erreicht werden. Das auf der Welle sitzende Innenmagnetsystem sowie gegebenenfalls Außenmagnete ist/sind vorzugsweise aus höherwertigen Magnetwerkstoffen wie NdFeB bzw. SmCo. Das Innenmagnetsystem kann zusätzlich gekapselt sein, so dass auch aggressive Medien gefördert werden können.The pump can preferably be driven via a magnet system. In particular, 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.
Als Werkstoff für das Lagerelement, die Rotoraufnahme, die Nierenplatte, die Welle und die Rotoren werden vorzugsweise Oxidkeramiken, nichtoxidische Keramiken oder Hartmetall eingesetzt. Hierdurch wird eine hohe Standfestigkeit erreicht. Die Verwendung von gehärteten Stählen oder Kunststoffen ist ebenfalls möglich.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.
Weitere Vorteile und Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter und nicht einschränkender Ausführungsbeispiele als Mikropumpe anhand der Figuren. Dabei zeigt:
- Fig. 1
- eine erste Ausführungsform einer erfindungsgemäßen Pumpe in einer perspektivischen schematischen und teilgeschnittenen Ansicht (Niederdruckvariante),
- Fig. 2
- eine zweite Ausführungsform einer Pumpe nach der Erfindung in einer Schnittansicht (Hochdruckvariante) und
- Fig. 3
- eine perspektivische Schnittansicht des Lagerelements der Pumpe nach
Fig. 1 und 2 .
- Fig. 1
- a first embodiment of a pump according to the invention in a perspective schematic and partially sectioned view (low-pressure variant),
- Fig. 2
- a second embodiment of a pump according to the invention in a sectional view (high-pressure variant) and
- Fig. 3
- a perspective sectional view of the bearing element of the pump
Fig. 1 and2 .
Die in
Die Welle 2 ist mittels eines ersten Radiallagers 4 und eines zweiten Radiallagers 5 in einem Lagerelement 6 aufgenommen und in radialer Richtung gelagert. An die in den
Im Bereich des ersten rotornahen Radiallagers 4 weist die Welle 2 einen ersten Durchmesser auf. Im Bereich des zweiten rotorfernen Radiallagers 5 weist die Welle 2 einen gegenüber dem ersten Durchmesser breiteren Durchmesser auf. Durch den großen Lagerdurchmesser am rotorfernen Radiallager 5 sind die auftretenden Lagerkräfte gering. Die die Welle 2 aufnehmende Ausnehmung im Lagerelement 6 ist gegenüber dessen aufgeweiteten Bereich 7 zentriert. In der Rotoraufnahmeplatte 10, die zum Lagerelement 6 und der Welle 2 durch die Hülse 12 zentriert ist, ist eine um eine Exzentrizität E unzentrische Ausnehmung ausgebildet, in der ein Außenrotor 13 (in
Die zum Innenrotor 3 zugewandte Stirnfläche 9 des Lagerelements 6 ist als Axiallager für den Innenrotor 3 und den Außenrotor 10 ausgebildet. Die Stirnfläche 9 hat zu diesem Zweck eine geringe Oberflächenrauheit beispielsweise in einem Bereich Ra 0,1 und eine eng tolerierte Ebenheit. An der dem Rotorsatz gegenüberliegenden Seite (in den Figuren oben) ist in einem Spalttopf 15 als Gehäusedeckel ein Stift 36 in einer PTFE-Hülse 37 aufgenommen. Stift 36 und PTFE-Hülse 37 bilden ein Axialloslager für die Welle 2 aus und dienen als Abstandshalter für einen nachfolgend beschriebenen Innenmagneten 32.The
Die Höhe der Hülse 12 in Achsrichtung der Welle 2 ist auf die Dicken von Nierenplatte 11, Rotoraufnahmeplatte 10 und aufgeweiteten Bereich 7 abgestimmt und ist leicht kleiner als die Summe der Dicken dieser Bauelemente, so dass diese über die Hülse 12 zentriert und über ein Gehäuseunterteil 14 und einen Spalttopf 15 als Gehäusedeckel in axialer Richtung definiert geklemmt werden. Die Dicke von Innen- sowie Außenrotor in Achsrichtung der Welle 2 ist dabei auf die Dicke der Rotoraufnahmeplatte10 abgestimmt, so dass Innen- und Außenrotor in dieser und zwischen der Stirnfläche 9 des Lagerelements 6 und der Nierenplatte 11 als Axiallager mit der erforderlichen Leichtläufigkeit bei gleichzeitiger Dichtheit rotieren können.The height of the
Das Gehäuseunterteil 14 weist einen Einlassdurchlass 16 (Niederdruckanschluss) und einen Auslassdurchlass 17 (Hochdruckauslass) auf. Der Spalttopf 15 ist in der in
Die Nierenplatte 11 besteht aus Keramik und weist eine niederdruckseitige Einlassniere 19 sowie eine hochdruckseitige Auslassöffnung 20 auf. Durch die radiale Ausrichtung von Nierenplatte 11 zum Gehäuseunterteil 14 mündet der niederdruckseitige Einlassdurchlass 16 des Gehäuseunterteils 14 in die Einlassniere 19, während die Auslassöffnung 20 mit dem hochdruckseitigen Auslassdurchlass 17 verbunden ist. Die Einlassniere 19 ist des Weiteren derart ausgebildet, dass sie mit der zentralen Ausnehmung der Rotoraufnahmeplatte und insbesondere der darin durch den Innenrotor 3 und den Außenrotor 13 gebildeten Förderkammer überlappt und strömungstechnisch verbunden ist.The
In der Rotoraufnahmeplatte 10 sind neben der zentralen Ausnehmung für den Außenrotor 13 zwei Durchlässe ausgebildet, niederdruckseitig eine Einlassöffnung 21 und hochdruckseitig eine Auslassöffnung 22. In der Stirnseite 9 des Lagerelements 6 ist eine Einlassniere 23 ausgebildet. Die Einlassniere 19 der Nierenplatte 11 sowie die Einlassniere 23 des Lagerelements 6 überdecken sich mit der Einlassöffnung 21 und sind miteinander verbunden. Des Weiteren überlappt die Einlassniere 23 des Lagerelements 6 mit der zentralen Ausnehmung der Rotoraufnahmeplatte und insbesondere mit der darin durch den Innenrotor 3 und den Außenrotor 13 gebildeten Förderkammer und ist mit diesen strömungstechnisch verbunden. Insgesamt ist über den Einlassdurchlass 16 und die Einlassniere 19 eine erste niederdruckseitige Zuleitung zur Förderkammer und über den Einlassdurchlass 16, die Einlassniere 19, die Einlassöffnung 21 und die Einlassniere 23 eine zweite niederdruckseitige Zuleitung zur Förderkammer gebildet. Durch diese zweite niederdruckseitige Zuleitung wird ein hydraulisches Gleichgewicht oder ein hydraulischer Ausgleich am Rotorsatz sowie ein großer niederdruckseitiger Zufluss gebildet. Des Weiteren kommt es zu weniger Kavitation.In addition to the central recess for the
Im Lagerelement 6 ist ein hochdruckseitiger Fluiddurchlass ausgebildet. Dieser besteht im Wesentlichen aus einer Auslassniere 24, einer in radialer Richtung eingebrachten Sacksenkung 25, einer ersten Randausnehmung 26 sowie einer zweiten Randausnehmung 27 mit anschließendem Hochdruckauslass 28. Der Hochdruckauslass 28 überlappt mit der Auslassöffnung 22 der Rotoraufnahmeplatte 10 und ist über diese sowie die Auslassöffnung 20 strömungstechnisch mit dem hochdruckseitigen Auslassdurchlass 17 verbunden. Die erste und die zweite Randausnehmung 26, 27 sind randseitig in das Lagerelement 6 eingebracht und in axialer Richtung (in den Figuren nach oben) sowie in radialer Richtung zur Außenseite des Lagerelements 6 hin offen. Gegenüber der Auslassniere 24 ist in der Nierenplatte 11 eine Ausgleichsniere 39 ausgebildet. Diese erzeugt hochdruckseitig ein hydraulisches Gleichgewicht oder einen hydraulischen Ausgleich am Rotorsatz.A high-pressure-side fluid passage is formed in the
Der Spalttopf 15 ist, wie bereits dargelegt, über die Verschraubung 18 mit dem Gehäuseunterteil 14 verspannt und gegenüber diesem über zwei O-Ringdichtungen 29, 30 in der Hülse 12 abgedichtet. Der Spalttopf 15 weist eine zentrale Ausnehmung 31 auf, in der das Lagerelement nebst der darin gelagerten Welle 2 mit einem im nachfolgenden näher beschriebenen Innenmagneten 32 aufgenommen ist. Zwischen der radialen Außenfläche 33 des Lagerelements 6 und der dem Lagerelement 6 zugewandten Innenwand der Ausnehmung 31 liegt ein Spalt 34 vor, der einen Teil des hochdruckseitigen Fluiddurchlasses bildet. Aus der Förderkammer strömt verdichtetes Fluid über die Auslassniere 24 und die Sacksenkung 25 in die erste Randausnehmung 26. Von dort aus verteilt sich das Fluid über den Spalt 34 um den gesamten Kopfbereich des Lagerelements 6 herum in den Zwischenraum zwischen Lagerelement 6 und Spalttopf 15. Aus diesem Zwischenraum strömt das Fluid nachfolgend über die zweite Randausnehmung 27, den Hochdruckauslass 28, die Auslassöffnung 22 der Rotoraufnahmeplatte 10 und ist die Auslassöffnung 20 zum hochdruckseitigen Auslassdurchlass 17. Durch das in dem vom Spalttopf 15 umgebenen Hohlraum, insbesondere das in dem Zwischenraum zwischen Lagerelement 6 und Spalttopf 15, strömende Fluid werden sowohl das Lagerelement 6 mit allen darin enthaltenen Funktionseinheiten (z.B. rotorfernes Radiallager 5) als auch der Innenmagnet 32 und der Spalttopf temperiert, insbesondere gekühlt. Insbesondere werden die Radiallager 4, 5 geschmiert und/oder gespült.As already explained, the
Diese Kühlung ist insbesondere in Anbetracht des Antriebs der Pumpe über den Innenmagneten 32 vorteilhaft. Der Innenmagnet 32 ist drehfest auf dem rotorfernen Ende der Welle 2 angeordnet. Er wirkt mit einem in den Figuren nicht dargestellten Außenmagnetsystem zusammen, das außerhalb des durch Gehäuseunterteil 14 und Spalttopf 15 gebildeten hermetischen Gehäuses der Pumpe angeordnet ist. Das Außenmagnetsystem erzeugt ein rotierendes Magnetfeld, das den als Permanentmagneten ausgebildeten Innenmagneten 32 in Rotation um die Drehachse der Welle 2 versetzt. Diese rotiert zusammen mit dem darauf angeordneten Innenrotor 3, der mit dem Außenrotor 13 kämmt und diesen in Rotation in der ihn aufnehmenden Ausnehmung in der Rotoraufnahmeplatte 10 versetzt. Durch das rotierende Magnetfeld der Magnete kommt es je nach Art des für den Spalttopf 15 und das Lagerelement 6 verwendeten Werkstoffs zu induktiver Erwärmung, wobei die entstehende Wärme über das den Spalttopf durchströmende Fluid abgeführt werden kann.This cooling is particularly advantageous in view of the drive of the pump via the
Ein weiterer Vorteil der Förderung des Mediums durch den vom Spalttopf 15 umgebenen Hohlraum ist, dass ein Versagen der Pumpe durch gesammelte Gasblasen ausgeschlossen werden kann. Totraum ist durch die aktive Durchströmung der gesamten Pumpe einschließlich Spalttopf minimiert.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.
Claims (12)
- Micropump for conveying a fluid from a low pressure inlet (16) to a high pressure outlet (17), the pump having- an internal rotor (3) with external teeth;- an outer rotor (13) with internal teeth, and- a bearing element (6); wherein the external toothing of the inner rotor (3) meshes with the internal toothing of the outer rotor (13) and the inner rotor (3) is arranged in a rotationally fixed manner on a shaft (2) supported by the bearing element (6);- wherein the outer rotor (13) is mounted eccentrically to the inner rotor (3) in a rotor receptacle (10) in a radial direction in order to cyclically open and close conveying chambers between the inner rotor and the outer rotor;- wherein the bearing element (6)- has a fluid passage (24, 25, 26, 27, 28) for conveyed fluid leading from the conveying chambers to the high pressure outlet (17);- radially supports (4, 5) the shaft (2) and forms an axial bearing (9) for the inner rotor and the outer rotor (3, 13), the bearing element (6) having a first radial bearing (5) remote from the rotor and a second radial bearing (4) close to the rotor,- wherein the shaft (2) is supported in the radial direction exclusively by the bearing element (6) with the two radial bearings (4, 5);- characterized in that- the shaft (2) has a first diameter in the region of the radial bearing (4) near the rotor, but has a wider or larger diameter than the first diameter in the region of the radial bearing (5) far from the rotor;- and in that the fluid passage in the bearing element (6) is fluidically connected to the radial bearings (4, 5) and the shaft (2) projects through a portion (25) of the fluid passage.
- Micropump according to claim 1, wherein the diameter of the first radial bearing (5) is at least 6 mm, preferably at least 6.5 mm, and the diameter of the second radial bearing (4) is at most 5 mm.
- Micropump according to any one of the preceding claims, wherein a kidney plate (11) is arranged on the side of the rotor holder (10) opposite the bearing element (6), which kidney plate (11) has a fluid supply (19) to and/or a fluid discharge (20) from the rotor holder (10).
- Micropump according to one of the preceding claims, wherein the bearing element (6) and the rotor holder (10), in particular also a kidney plate (11), are axially centred relative to one another, preferably by a housing (12) arranged therearound.
- Micropump according to claim 3 or 4, wherein the kidney plate (11) forms a thrust bearing for the inner rotor and/or the outer rotor and/or the shaft (2).
- Micropump according to one of the preceding claims, wherein the bearing element (6) alone or exclusively contains the two radial bearings (4, 5) for the shaft (2).
- Micropump according to any of the preceding claims, wherein- at least one kidney-shaped cavity (24) is formed on the rotor-side end face (9) of the bearing element (6) for a high-pressure-side emptying of the conveying chambers formed continuously between the inner rotor (3) and the outer rotor (13);
and/or- at least one kidney-shaped cavity (23) is formed on the rotor-side end face of the bearing element (6) for low-pressure-side filling of the conveying chambers formed continuously between the inner rotor (3) and the outer rotor (13). - Micropump according to claim 1, wherein a containment can (15) is provided which surrounds a cavity and with the fluid flowing in the cavity the bearing element (6) with all the functional units contained therein can be tempered, in particular can be cooled.
- Micropump according to claim 8, wherein the functional units are the radial bearing (5) remote from the rotor, an internal magnet (32) and the containment can (15).
- Micropump according to claim 8 or 9, wherein the fluid flowing in the cavity for cooling, flushing and/or lubricating is surrounded by the can (15).
- Micropump according to any one of claims 8 to 10, wherein the fluid flowing in the gap between the bearing element (6) and the containment can (15) tempers, in particular cools, the bearing element (6) with all the functional units contained therein.
- Micropump according to any of the preceding claims, wherein a magnetic system is provided as drive.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011051486.4A DE102011051486B4 (en) | 2011-06-30 | 2011-06-30 | Pump arrangement with micropump and bearing element |
PCT/EP2012/061514 WO2013000745A2 (en) | 2011-06-30 | 2012-06-15 | Micropump, bearing element for a micropump, and working method |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2726740A2 EP2726740A2 (en) | 2014-05-07 |
EP2726740B1 true EP2726740B1 (en) | 2023-10-11 |
Family
ID=46319766
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP12728264.8A Active EP2726740B1 (en) | 2011-06-30 | 2012-06-15 | Micropump, bearing element for a micropump, and working method |
Country Status (5)
Country | Link |
---|---|
US (1) | US9404492B2 (en) |
EP (1) | EP2726740B1 (en) |
CN (1) | CN103732921B (en) |
DE (1) | DE102011051486B4 (en) |
WO (1) | WO2013000745A2 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102016121240A1 (en) * | 2016-11-07 | 2018-05-09 | Nidec Gpm Gmbh | Electric gerotor pump and method of making same |
FR3060669B1 (en) | 2016-12-20 | 2020-11-27 | Coutier Moulage Gen Ind | PLATE GEAR PUMP AND HYDRAULIC CENTERING PINS. |
IT201700067423A1 (en) | 2017-06-16 | 2018-12-16 | Gkn Sinter Metals Ag | Pump arrangement and process for producing a pump arrangement. |
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 (en) | 2019-01-21 | 2020-07-23 | Hnp Mikrosysteme Gmbh | Self-rinsing micropump |
DE102019102073A1 (en) * | 2019-01-28 | 2020-07-30 | Fresenius Medical Care Deutschland Gmbh | Gear pump |
CN117605678B (en) * | 2023-12-26 | 2024-06-14 | 苏州帕夫尔流体科技有限公司 | Gear cavity and pump cover integrated structure |
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US3238883A (en) | 1964-03-09 | 1966-03-08 | Micro Pump Corp | Magnetic drive gear pump |
DE1947798A1 (en) | 1969-09-20 | 1971-04-15 | Danfoss As | Power or work machine |
US3824047A (en) | 1973-03-23 | 1974-07-16 | Dermott H Mc | Floating rotary ring member of fluid displacement device |
US3945779A (en) * | 1973-08-30 | 1976-03-23 | Robert Bosch Gmbh | Bearings for the trunnions of gears in gear pumps or the like |
CA1217089A (en) | 1982-03-23 | 1987-01-27 | Hollis N. White, Jr. | Rotary gerotor hydraulic device with fluid control passageways through the rotor |
CH661323A5 (en) | 1983-09-21 | 1987-07-15 | Walter Weber | GEAR PUMP. |
EP0769621A1 (en) * | 1995-09-26 | 1997-04-23 | Fraunhofer-Gesellschaft Zur Förderung Der Angewandten Forschung E.V. | Micropump and micromotor |
DE19843161C2 (en) | 1998-09-21 | 2000-11-23 | Hnp Mikrosysteme Gmbh | Layer structure housing construction |
ATE348956T1 (en) | 2001-01-22 | 2007-01-15 | Hnp Mikrosysteme Gmbh | PRECISE MINIMAL STORAGE AND ASSEMBLY PROCESS FOR IT |
JP2004360677A (en) | 2003-05-14 | 2004-12-24 | Matsushita Electric Ind Co Ltd | Coolant pump |
JP2007009787A (en) * | 2005-06-30 | 2007-01-18 | Hitachi Ltd | Motor-integrated internal gear pump and electronic equipment |
DE102008054755A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | Conveying device, particularly gear wheel pump, has housing, where surfaces of housing units have mounting surfaces for mounting conveyor elements |
DE102011001041B9 (en) | 2010-11-15 | 2014-06-26 | Hnp Mikrosysteme Gmbh | Magnetically driven pump arrangement with a micropump with forced flushing and working method |
-
2011
- 2011-06-30 DE DE102011051486.4A patent/DE102011051486B4/en active Active
-
2012
- 2012-06-15 EP EP12728264.8A patent/EP2726740B1/en active Active
- 2012-06-15 US US14/129,475 patent/US9404492B2/en active Active
- 2012-06-15 WO PCT/EP2012/061514 patent/WO2013000745A2/en active Application Filing
- 2012-06-15 CN CN201280038326.2A patent/CN103732921B/en active Active
Also Published As
Publication number | Publication date |
---|---|
DE102011051486A1 (en) | 2013-01-03 |
US20150132172A1 (en) | 2015-05-14 |
WO2013000745A4 (en) | 2013-12-19 |
EP2726740A2 (en) | 2014-05-07 |
US9404492B2 (en) | 2016-08-02 |
WO2013000745A2 (en) | 2013-01-03 |
WO2013000745A3 (en) | 2013-10-24 |
DE102011051486B4 (en) | 2023-06-01 |
CN103732921A (en) | 2014-04-16 |
CN103732921B (en) | 2017-08-11 |
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