Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
• • 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
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/008—Prime movers
• • 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
  • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
  • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C18/10—Rotary-piston pumps specially adapted for elastic fluids 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
  • F04C18/107—Rotary-piston pumps specially adapted for elastic fluids 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 with helical teeth
• • 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
  • F04C2/107—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 with helical teeth
• • 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
  • F04C2/107—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 with helical teeth
  • F04C2/1071—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 with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
• • 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
  • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
  • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
• • 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
  • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
  • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
  • F04C29/0085—Prime movers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
• • 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
  • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
  • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
• • 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
  • F04C2220/00—Application
• • 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
  • F04C2240/70—Use of multiplicity of similar components; Modular construction

Definitions

• the invention relates to an eccentric screw pump.
• Eccentric screw pumps are used in various fields, such as agriculture, the chemical industry, the food industry and papermaking. It belongs to the group of rotating positive displacement pumps and consists of a drive device essentially of a rotor and a stator.
• the helical rotor of the eccentric screw pump is characterized by a large pitch, large flight depth and small core diameter.
• the stator has a thread more relative to the rotor and has twice the pitch length of the rotor. Between the stator and the rotor, delivery chambers are thus formed, which move continuously from the inlet to the outlet side and in which the pumped medium can be transported.
• the rotor of an eccentric screw pump usually consists of an abrasion-resistant material such as steel.
• the stator is usually made of an elastic material such as rubber.
• stators are known from the prior art, which consist of a material or a composite material of metal and / or plastic.
• the individual components of the eccentric screw pump are dimensioned and designed accordingly for the respective redesignaufgäbe.
• the delivery rate and the achievable pressure are determined by the size and configuration of the stator and rotor.
• the drive device can thus be used play in two differently used eccentric screw pump designed and constructed the same.
• the eccentric screw pumps can achieve different delivery rates and pressures for the same number of revolutions of the rotors. If the requirements for the eccentric screw pump change because, for example, the delivery capacity has increased and the pump is no longer suitable for this purpose, then the progressing cavity pump can only be exchanged, since a conversion is generally too costly.
• US Pat. No. 2,483,370 discloses an eccentric screw pump with a plurality of cylinders, which are firmly integrated in a housing and in which a rotor gear is also arranged. It is considered advantageous that the pump only requires a single seal due to its design.
• the pump has only one outlet (exhaust port 29), which is why the pressure for all delivery modules can not be varied.
• the conveyor modules are subject to an eccentricity which must be compensated by the internal gear, with the result that the flow rate is limited and the pump is exposed to high wear.
• the pump has only one inlet (inlet port 28) for only one pumped medium and the modules can be exchanged in pairs only with a relatively high effort due to the compact design and the special drive configuration.
• An eccentric screw pump with two pump sections (Pa, Pb), in which at least one inner pump rotor is enclosed by at least one outer pump rotor, wherein the pump sections (Pa, Pb) are driven at different rotational speeds of the rotors, is disclosed in WO 2009/038473 Al ,
• the pump has an inlet (inlet flange 21) and an outlet (outlet flange 28) for conveying a fluid.
• the invention is therefore an object of the invention to provide an eccentric screw pump, with the need to increase the flow, the pressure and / or the simultaneous delivery of more than one fluid is possible, the eccentric screw pump has a relatively low energy consumption during operation of the eccentric screw pump and their production and maintenance costs are kept low.
• an eccentric screw pump which is equipped with a modular conveyor system containing at least two each comprising a rotor and a stator comprising conveyor modules, wherein the conveyor modules are coupled together and the conveyor system is associated with only one drive device and wherein the conveyor system for a pumped medium has more than one input and / or output or at least one modular flow housing.
• the invention is based on the consideration that an adaptation to the respective fraudaufgäbe is particularly easy to implement by a modular conveyor system.
• the inputs and outputs for the pumped medium and the number of conveyor modules should be substantially expandable and combinable as desired.
• the pump can be effectively matched to the requirements of the user.
• the conveyor modules each comprise a stator and a rotor, wherein the rotor is driven by only one drive device.
• the rotors are connected to one another in order to transmit the forces occurring during operation of the eccentric screw pump, in particular the torque forces generated by the drive device.
• the conveyor modules in such a way with each other coupled, that between the respective rotors of the conveyor modules and a rotation angle-dependent pressure pulsation caused vibrations, a phase difference of 180 ° is achieved. Since the frequency of the vibrations is the same, due to the fact that only one drive system is used, so the vibrations are reduced to a minimum.
• the conveyor modules via suction pressure or flow housing are coupled together.
• the suction and pressure housings are provided with a connecting piece for connection to the delivery lines.
• a suction line can be connected to the suction housing and a pressure line to the pressure housing.
• the conveyor modules can optionally be coupled together with a pressure, suction or flow-through housing, or finally provided with a pressure or suction housing.
• the conveyor modules can be designed differently, so that at the same rotational frequency of the rotors, the delivery rates of the conveyor modules are different. If different products are promoted, a certain mixing ratio can be set.
• the rotors associated with the conveyor modules are preferably coupled to each other via a rigid connection within the housing, so that transmission of the forces acting on the rotor by the drive device is possible without play and loss.
• the rotors may be formed by any rigid or rigid connection known in the art be coupled, which is suitable depending on the application to transmit torques or torques and axial forces. As an example, let us look at material connections such as
• the rotors are releasably connected to each other.
• the assembly and disassembly of the conveyor modules is thereby simplified and improved.
• the rotor in one piece for at least two conveyor modules. Since there are no connection points, this design is particularly well suited for the promotion of, for example, abrasive and aggressive media.
• the housings and stators are pushed over the one-piece rotor.
• the stator is considered in this particular embodiment, even if the delivery module fulfills its function only after assembly, together with the respective rotor section.
• the eccentric screw pump is preferably configured such that the axial force F acting in the direction of the drive device approaches zero or at least is reduced. This is achieved by the fact that each two conveyor modules, in the same speed and the same sense of rotation of the rotors, promote in opposite directions. For this purpose, the conveyor modules on opposite slopes. In an eccentric screw pump with, for example, two conveyor modules, one conveyor module has a left and the other conveyor module Right turn on. The axial forces which occur during operation of the eccentric screw pump in each case per delivery module act in opposite directions and cancel out almost completely when identical delivery modules are used. Under similar is, apart from the different pitch, to understand a particular embodiment and dimensioning of the conveying elements.
• the conveyor modules are arranged in series.
• the torque transmission from the drive device to the rotors or to the rotor can be kept particularly simple.
• two adjacent conveyor modules are coupled to one another via a flow-through housing and configured for the same conveying directions.
• the slopes are identical for both conveyor modules, preferably, the conveyor modules have a left slope.
• the product is thus conveyed via the inlet connection of the pump housing into a first delivery module, through a flow-through housing and a second delivery module in one direction. Since each delivery module represents a pressure stage, the resulting pressure can be increased by connecting several delivery modules in series.
• the gradients are different for both conveyor modules.
• the eccentric screw pump may include a first conveyor module with a left slope and a second conveyor module with a right slope, both of which are coupled together via a pressure housing, so that the fluid is conveyed through the conveyor modules towards the pressure housing.
• the eccentric screw pump may comprise a first delivery module with a right pitch and a second delivery module with a left slope, both being connected via a suction housing, so that the delivery medium is sucked in by the delivery modules and conveyed in opposite directions.
• the eccentric screw pump comprises only two conveyor modules. Even if only two conveyor modules are used, the eccentric screw pump can be configured according to the respective requirements of the randomlyaufgäbe and yet has a compact design.
• the eccentric screw pump can be configured to achieve twice the delivery capacity with the same simple speed and pressure, compared to a conventional progressive cavity pump, with the same speed and direction of rotation.
• a first conveyor module coupled to the drive device has a left-hand pitch and a second conveyor module connected in series has a right-hand pitch. Both conveyor modules are coupled together via a pressure housing.
• the second delivery module has a suction housing at its end opposite the pressure housing.
• the pumped medium sucked in via a suction nozzle on the pump housing, but here additionally via a suction nozzle on the suction housing.
• the pumped liquid is thus promoted in the operating state of the pump coming from two sides to the pressure housing and exits via a pressure port on the pressure housing. In this way, different fluids can be supplied.
• the fluid or the media are merged, with a mixing ratio can be adjusted by a suitable choice of the conveyor modules.
• the eccentric screw pump which achieves twice the pressure with a simple delivery rate, as in the case of a conventional eccentric screw pump.
• the eccentric screw pump is equipped with two conveyor modules of the same pitch, preferably left-hand pitch. Both conveyor modules are coupled together via a flow housing.
• the second delivery module has a pressure housing at its end opposite the throughflow housing.
• the fluid is sucked in via the suction port of the pump housing and conveyed via the first delivery module, the flow-through housing and the second delivery module to the pressure housing, which is provided with a discharge nozzle.
• the eccentric screw pump comprises a total of four conveyor modules. This makes it possible, depending on the configuration, in comparison to a conventional eccentric screw pump, either four times the flow rate at the same pressure or twice the flow rate at double pressure can be achieved.
• two conveyor modules with different pitch are coupled to each other via a pressure housing, the two pairs of conveyor modules thus formed in turn are connected to each other via a suction housing coupled.
• a further suction housing is arranged at the opposite end of the drive device of the eccentric screw pump.
• the pumped liquid can thus be conveyed via a total of three suction nozzles and two discharge nozzles.
• the conveyor modules preferably have the gradients left-right-left-right from the first to the fourth conveyor module.
• the conveyor modules via a suction, two fürströmungs- and a pressure housing are coupled together.
• two conveyor modules with the same pitch are coupled via a flow-through housing, the two conveyor module pairs thus formed in turn via a pressure housing with each other.
• a suction housing is arranged at the opposite end of the drive device of the eccentric screw pump.
• the conveyor modules preferably have the slopes left-left-right-right.
• the eccentric screw pump preferably has mixing means coupled to the rotor in the coupling region of the conveyor modules. This makes it possible that the fluid or the media to be mixed during transport. This is particularly advantageous when two different products, for example when the one product via a first suction housing and the other product via a second suction housing, are introduced into the eccentric screw pump.
• the means for mixing is located within the pressure housing and directly coupled to the rotor. A separate drive is therefore not required.
• the housing are formed substantially identical.
• suction and pressure housing identical and are defined only by the nature of their use.
• the flow-through housing is preferably formed from a suction or pressure housing by the suction or discharge nozzle is provided with a closure means.
• the closure means may be formed as a blind flange, which is fastened via a flange on the housing neck.
• the advantages achieved by the invention are, in particular, that a delivery of different pumped media, in a certain predefined mixing ratio, can be realized with only one pumping system.
• the pumping system can be particularly easily adapted to the conveying tasks by the number and selection of the conveying modules and the coupling means. Due to the fact that the delivery rate and delivery speed of a progressive cavity pump are determined and influenced by various factors such as the geometry and pitch of the rotor and stator, the delivery rate can be set particularly easily with the aid of the modular pump structure. Through the use of delivery modules with different delivery rates, the mixing ratio of the pumped media can be influenced. In addition, a cost saving is possible.
• the conveyor modules can be arranged so that the axial forces cancel out almost completely. By reversing the direction of rotation of the rotor or the rotors, the conveying direction can be changed.
• Another advantage is that only one sealing system on the suction side of the drive system is required and serviceable.
• the eccentric screw pump according to the invention as a so-called submersible pump, with the same pipe diameter or drilling or bunghole, the flow rate can be doubled.
• FIG. 1 shows an eccentric screw pump with two delivery modules, which are coupled to one another via a throughflow housing and a pressure housing is arranged, an eccentric screw pump with two m conveying modules in opposite directions, which are coupled together by means of a pressure housing and at the end of a suction housing, an eccentric screw pump with two conveying in opposite directions conveyor modules which are coupled together by means of a pressure housing and at the end of a suction housing is arranged with a compensating coupling to a drive device, an eccentric screw pump with a total of four conveyor modules, which via a suction and two pressure housing together are coupled and at the end of a suction housing is arranged, FIG. 5 shows an eccentric screw pump with a total of four delivery modules which are coupled to one another via a pressure and two flow-through housing and at the end of which a suction housing is arranged,
• Figure 6 is a known from the prior art conveyor system, in which a total of four eccentric screw pumps are connected in parallel.
• the device according to FIG. 1 shows an eccentric screw pump 2 with a first and a second delivery module 4, 6, each comprising a stator 8 and a rotor 10, which are coupled to one another via a flow-through housing 12.
• a pressure housing 16 with a pressure connection 18 is arranged on the second delivery module 6.
• Both conveyor modules 4,6 are of identical design and have a left-hander L on.
• the flow-through housing 12 is a
• Pressure housing or a suction housing which is provided with a closure means 20.
• the closure means 20 should be arranged close to the pressure housing in order to avoid dead space, which adversely affect the flow path and by the medium can settle.
• the eccentric screw 2 is equipped with feet not shown here.
• the unused for the promotion nozzle of the flow housing 12 can be used advantageously as a stand or as a basis for the mounting of a stand.
• the conveyor system composed essentially of the conveyor modules 4, 6 and the housings 12, 16 is coupled to the drive device 14, which encloses a pump housing 22 with a suction nozzle 24 and a drive component 26. summarizes.
• the power transmission to the rotor 10 of the first conveyor module 4 takes place by means of drive shafts 30 coupled via joints 28.
• the drive device 14 is provided with a seal 32 in order to prevent the conveying medium from escaping to the outside.
• the rotors 10 of the conveyor modules 4, 6 are connected to one another via a rigid coupling 34.
• the fluid passes from a suction line, not shown here via the suction port 24 into the pump housing 22 and is conveyed by means of the conveyor modules 4,6 through the flow housing 12 through to the pressure housing 16, where it then via the discharge port 18 in a pressure line, not shown here is transported.
• the axial forces occurring counteract the conveying direction and are absorbed by a bearing provided for this purpose. Since the conveyor modules 4, 6 are connected in series in this embodiment, a double pressure is achieved compared with a conventional eccentric screw pump equipped with only one rotor-stator arrangement.
• FIG. 1 An eccentric screw pump 2 with two conveying modules 4, 6 coupled via a pressure housing 16 is shown in FIG.
• the first conveying module 4 has a left-hand pitch L and the second conveying module 6 has a right-hand pitch R.
• the rotors 10 are connected to each other via a rigid coupling 34.
• a provided with a suction port 24 suction housing 36 is arranged at the drive device 14 opposite end of the eccentric screw pump 2.
• the pump housing 22 has a further suction port 24.
• the housing arranged at the end of the eccentric screw pump 2 acts as a suction housing 36.
• the pumped medium is thus transported via the two suction nozzle 24 into the pressure housing 16 and conveyed through the discharge port 18.
• the pumped media are transported in opposite directions.
• the axial forces occurring during operation of the eccentric screw pump 2 and acting on the rotors 10 counteract, whereby the resultant force acting on the bearings of the drive device 14 approaches zero or is at least reduced.
• the coupling 34 for the rotors 10 should be designed so that they can absorb the tensile forces occurring.
• the drive shafts 30, joints 28 and bearing 32 are less stressed, resulting in less wear.
• the components of the eccentric screw 2 can be dimensioned correspondingly cheaper.
• a means for mixing is arranged in the region of the coupling 34, which is coupled to the rotors and is designed as a stirring element 37. Since the conveyor modules 4, 6 are connected in parallel in this embodiment, a double delivery capacity is achieved compared with a conventional eccentric screw pump.
• the rotor 10 may also be formed in one piece.
• a coupling 34 can be dispensed with.
• the rotor 10 has for this purpose two sections for the conveyor modules 4,6. A first section with a left slope L and a second section with a right slope R.
• FIG. 3 shows an eccentric screw pump 2 as shown in FIG. 2, but with a different drive device 14.
• the drive device has a compensation coupling 33 for transmitting the torque to the rotors. Due to the compact Design of the drive device 14, the extended design of the eccentric screw pump 2, by the series-connected conveyor modules 4,6, are almost completely compensated.
• FIG. 4 shows an eccentric screw pump 2 with a total of four conveyor modules 4,6,38,40 shown, wherein two analogous to the embodiment in Figure 2 by means of pressure housing 16 coupled conveyor modules are coupled together via a suction housing 36, such that the conveyor modules 4, 6,38,40 of the conveyor system of the drive device 14, starting the slopes left-right-left-right.
• a suction housing 36 is arranged with a suction nozzle 24.
• the rotors 10 are connected by rigid couplings 34.
• the fluid is conveyed over a total of three suction port 24 and two discharge ports 18. Since the four conveyor modules 4,6,38,40 are connected in parallel in this embodiment, a four times the capacity compared to a conventional eccentric screw pump is achieved. Due to the same number of conveyor modules
• FIG. 1 A further alternative embodiment with a total of four conveyor modules 4, 6, 38, 40 is shown in FIG.
• the conveyor module pairs 4, 6 and 38, 40 connected in series have different pitches, so that the conveyor system comprises a total of conveyor modules 4, 6, 38, 40 with the slopes left-left-right-right.
• the eccentric screw 2 the pumped liquid is sucked by means of the suction nozzle 24 on the suction housing 36 and the pump housing 22 and transported away via only a discharge port 18.
• FIG. 6 shows, for comparison, an arrangement known from the prior art with a plurality of identical eccentric screw pumps 42 of the same design.
• the total of four progressing cavity pumps 42 are connected in parallel to achieve four times the capacity compared to a simple eccentric screw pump.
• the arrangement known from the prior art has, inter alia, a disadvantageously high energy requirement for operating the pump, high production and maintenance costs and a high space requirement.
• Each of the four eccentric screw pumps 42 each comprise a drive device 14, a rotor-stator arrangement 44 and an end opposite to the drive device 14 arranged pressure housing 16, which is provided with a pressure port 18.
• the fluid is sucked through the suction port 24 on the pump housing 22 and conveyed in the direction of the pressure housing 16, from where it is transported via the discharge port 18 in pressure lines, not shown here.
• the device according to the invention is specifically geared to an eccentric screw pump 2, which can be used flexibly and can be saved with the costs and effort. Due to the particularly simple modular design, the eccentric screw 2, by the number and selection of suitable conveyor modules 4,6,38,40 and housing 16,36, the respective redesignaufgäbe be adjusted. All that is required is only one drive device 14, which above all keeps the energy and maintenance requirements comparatively low. Due to the mutual arrangement of conveyor modules with different gradients L, R, the axial forces acting on the bearings of the eccentric screw pump can also be reduced.

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• 2012
  • 2012-12-19 DE DE102012112618.6A patent/DE102012112618B3/de active Active
• 2013
  • 2013-12-17 RU RU2015129345A patent/RU2015129345A/ru unknown
  • 2013-12-17 EP EP13836227.2A patent/EP2935890A2/de not_active Withdrawn
  • 2013-12-17 JP JP2015548198A patent/JP6101363B2/ja not_active Expired - Fee Related
  • 2013-12-17 WO PCT/DE2013/000802 patent/WO2014094715A2/de active Application Filing
  • 2013-12-17 KR KR1020157019332A patent/KR101728260B1/ko active IP Right Grant
  • 2013-12-17 BR BR112015012372-4A patent/BR112015012372B1/pt active IP Right Grant
  • 2013-12-17 CN CN201380062388.1A patent/CN104822942A/zh active Pending
  • 2013-12-17 AU AU2013362364A patent/AU2013362364B2/en not_active Ceased
  • 2013-12-18 AR ARP130104824A patent/AR094087A1/es unknown
• 2015
  • 2015-06-17 US US14/742,230 patent/US20150285245A1/en not_active Abandoned

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