EP2873862A1 - Pompe à vis sans fin excentrique et utilisation d'une pompe à vis sans fin excentrique - Google Patents

Pompe à vis sans fin excentrique et utilisation d'une pompe à vis sans fin excentrique Download PDF

Info

Publication number
EP2873862A1
EP2873862A1 EP20140003567 EP14003567A EP2873862A1 EP 2873862 A1 EP2873862 A1 EP 2873862A1 EP 20140003567 EP20140003567 EP 20140003567 EP 14003567 A EP14003567 A EP 14003567A EP 2873862 A1 EP2873862 A1 EP 2873862A1
Authority
EP
European Patent Office
Prior art keywords
eccentric screw
stator
screw pump
pump
region
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.)
Withdrawn
Application number
EP20140003567
Other languages
German (de)
English (en)
Inventor
Elimar Volkmann
Lorenz Lessmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Publication of EP2873862A1 publication Critical patent/EP2873862A1/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • 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
    • F04C2/1073—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 where one member is stationary while the other member rotates and orbits
    • 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
    • F04C2/1073—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 where one member is stationary while the other member rotates and orbits
    • F04C2/1075—Construction of the stationary member

Definitions

  • the present invention relates to an eccentric screw pump for conveying liquid and / or granular media and the use of such an eccentric screw pump according to the features of the preambles of claims 1 and 13.
  • Eccentric screw pumps are pumps for pumping a large number of media, in particular viscous, highly viscous and abrasive media such as sludges, liquid manure, crude oil and fats.
  • Progressing cavity pumps known from the prior art are formed from a rotor and a stator, the rotor being accommodated in the stator and moving eccentrically in the stator.
  • the stator is formed by a housing with a spiral-shaped inside. From the movement of the rotor and mutual conditioning between the stator and rotor moving conveyor chambers are formed, by means of which liquid media can be transported along the stator.
  • the rotor performs an eccentric rotational movement about the stator axis or about the longitudinal axis of the eccentric screw pump.
  • the outer screw i.
  • the stator has the form of a double thread, while the rotor screw is only catchy.
  • progressing cavity pumps are suitable for conveying water, petroleum and a large number of other liquids.
  • the shape of the delivery chambers is constant during the movement of the rotor within the stator, so that the pumped medium is not crushed.
  • not only fluids but also solids can be conveyed with progressing cavity pumps.
  • the eccentric screw pumps require at least one safety device against overpressure.
  • a connecting line between the inlet flange of the suction side of the Pump body and the outlet flange of the pressure side is arranged.
  • the connecting pipe is an external pipe and / or hose line in which an overflow or safety valve is integrated.
  • the object of the invention is therefore to provide an eccentric screw pump with at least one safety device against overpressure, which is characterized by a simple and uncomplicated structure and in particular does not have the disadvantages of the prior art mentioned.
  • the invention relates to an eccentric screw pump for conveying fluid and / or granular media, in particular of viscous, highly viscous and abrasive media.
  • An eccentric screw pump consists of a pump body and a drive unit. The pump body is divided into an inlet region with an inlet nozzle, a pumping unit and an outlet region with an outlet nozzle. The inlet port and the outlet port have normalized flanges for connection to other pipe sections for delivery of the pumped medium.
  • the pump unit is formed of a rotor and a stator.
  • the stator is formed by a housing with a spiral-shaped inside.
  • the rotor is designed as a kind of round-threaded screw and moves eccentrically in the interior of the stator, whereby the delivery chambers formed between the rotor and stator are movable in the conveying direction.
  • the inlet region of the eccentric screw pump forms the suction side and the outlet region of the eccentric screw pump forms the pressure side.
  • a bypass connection with at least one safety valve is arranged between the pressure side and the suction side. This serves for receiving and returning back-flowing medium between the pressure side and the suction side of the eccentric screw pump in order to prevent an uncontrolled overpressure from building up within the eccentric screw pump. Overpressure must be reduced in a controlled manner in order to prevent or avoid damage to the eccentric screw pump.
  • bypass connection and the safety valve are integrated in the pump body of the eccentric screw pump.
  • bypass connection and the safety valve are integrated in the pump unit in the pump body of the eccentric screw pump.
  • the stator has an additional jacket.
  • the stator is arranged in a jacket tube, wherein the stator has an outer circumference which is smaller than the inner circumference of the jacket tube, so that a gap is formed between the stator and the jacket tube. This is in fluid communication with the respective interior spaces of the inlet area and the outlet area and forms the bypass connection. Furthermore, the gap is assigned at least one safety valve.
  • the stator is arranged in a stator sleeve.
  • the inner periphery of the stator sleeve largely corresponds to the outer circumference of the stator, so that the stator sleeve rests with its inner circumference largely flat on the outer circumference of the stator.
  • Between the stator and the Stator sleeve is formed at least one connecting line parallel to the longitudinal axis of the eccentric screw pump.
  • the connection line is fluidly connected to the respective inner spaces of the inlet area and the outlet area via first and second connections and forms the bypass connection.
  • the first and second connections are, in particular, bores in the housing of the pump body, in particular in the areas in which the outlet and inlet areas respectively adjoin the pump unit.
  • At least one safety valve is assigned to the at least one connecting line.
  • the at least one connecting line between the stator and stator sleeve is formed for example by a continuous recess in the outer circumferential surface of the stator parallel to the longitudinal axis of the eccentric screw pump.
  • a continuous groove is formed on the outer circumferential surface. The recess extends along a length of the stator, in particular along the entire length of the stator.
  • the rotor comprises a cavity along its rotor longitudinal axis.
  • the cavity may for example be a through-hole through the rotor along the rotor longitudinal axis.
  • the cavity can already be integrated into the rotor during manufacture by already hollow-casting it or hollow molding it by means of another suitable method.
  • the cavity of the rotor is in fluid communication with the respective interior spaces of the inlet region and the outlet region and forms the bypass connection.
  • the cavity is associated with at least one safety valve.
  • the eccentric screw pump has a stator with at least one return flow channel.
  • the return flow channel is formed parallel to the longitudinal axis of the eccentric screw pump along the stator length.
  • the at least one return flow channel is in fluid communication with the respective interior spaces of the inlet region and the outlet region and forms the bypass connection.
  • the return flow channel is formed in particular in a region between an internal thread of the stator and the outer circumferential surface of the stator.
  • the return flow channel has no open connection to the internal thread of the stator and / or the outer circumferential surface of the stator. That is, the return flow channel is formed in the stator material.
  • the return flow channel is assigned at least one safety valve.
  • a portion of the pumped medium is passed as a return flow via the at least one return flow channel of the stator back into the inlet region of the pump body.
  • the at least one return flow channel is cast during manufacture in the stator.
  • the at least one return flow channel can be subsequently formed even after the stator has been manufactured.
  • the safety valve is arranged within the return flow channel, preferably in a region between the inlet region and the pumping unit.
  • the safety valve is integrated in the outlet region of the pump body. It is provided that an outlet opening of the safety valve opens via a first connection in a return flow channel. Also in this embodiment, multiple return ducts and a plurality of appropriately arranged safety valves can be used. When an overpressure builds up on the pressure side of the eccentric screw pump, a portion of the pumped medium is passed as a return flow via the at least one return flow channel of the stator back into the inlet region of the pump body.
  • the safety valve for preventing an impermissible increase in pressure within the eccentric screw pump can be a spring-loaded safety valve, a weight-loaded safety valve or a medium-loaded safety valve.
  • the safety valve is an overflow valve for relieving the interior of the eccentric screw pump in the event of inadmissible overpressure within the closed system.
  • a previously described eccentric screw pump according to the invention can be used in particular for conveying fluid and / or granular media in a borehole.
  • Such an eccentric screw pump can generally be used whenever, for example, due to the medium to be pumped, the development of overpressure is to be expected.
  • the integrated return circuit By integrating the return circuit with safety or overflow valve in the pump body of the eccentric screw pump whose structure remains compact.
  • the integrated return circuit generally does not increase the pump body of the eccentric screw pump.
  • a return circuit is not only possible for progressing cavity pumps with a stator formed of an elastomer.
  • a return circuit into a so-called stepwise vortex pump in a comparable manner.
  • a stepwise vortex pump for example, in the US 2008/0050249 A1 described.
  • this pump has no stator made of a rubber, which is attacked, for example, when pumping petroleum or the like from the pumped medium.
  • the pump is built in stages, contains only corrosion-resistant metal components and works centralized. This can eliminate vibrations in the system, and the pump can operate at elevated temperatures and be made smaller.
  • FIG. 1 shows an eccentric screw pump 1 with conventionally known external bypass line 2 according to the prior art.
  • the eccentric screw pump 1 comprises a pump body 3 with an inlet region 4, a pumping unit 5 and an outlet region 6.
  • the inlet region 4 forms the suction side S of the eccentric screw pump 1 and the outlet region 6 forms the pressure side D of the eccentric screw pump 1.
  • the pumping unit 5 consists of an eccentric screw conveyor , the so-called rotor 8, which rotates in a stator 7 with a spiral-shaped inner side, forming traveling conveying chambers 14.
  • the rotor 8 is connected to the drive unit 12, which connects the rotor 8 with a drive shaft 13 by means of a coupling rod 9 arranged in the inlet region of the pump body 3. In between are joints 10, 11 for the connection of and power transmission between the drive unit 12 and the rotor. 8
  • the medium M to be delivered passes into the eccentric screw pump 1, is transported through the traveling delivery chambers 14 in the conveying direction Fr by the pumping unit and pumped out of the eccentric screw pump 1 via the outlet flange 16 of the outlet region 6.
  • the bypass line 2 is arranged with a safety valve 20, for example with an overflow valve 21, via suitable connecting means 17, 18.
  • the overflow valve 21 is arranged directly on a connecting means 17 which is assigned to the outlet flange 16.
  • the bypass line 2 extends between the spill valve 21 and the connecting means 18, which is associated with the inlet flange 15, parallel to the pump body third
  • FIG. 2 shows an eccentric screw pump 30-1 according to the invention.
  • the stator 7 is surrounded by a jacket tube 45.
  • the housing of the pump body 3 has a first connection 46 to the jacket tube 45, so that the interior of the outlet region 5 is fluidically connected to a cavity 43 formed between jacket tube 45 and stator 7.
  • the housing of the pump body 3 in the inlet region 4 has a second connection 47 to the jacket tube 45, so that the interior of the inlet region 4 is fluidly connected to the cavity 43 formed between the jacket tube 45 and the stator 7.
  • a return flow channel 44 is formed between the jacket tube 45 and the outer jacket surface of the stator 7, through which a portion of the medium M R can flow from the pressure side D back to the suction side S of the eccentric screw pump 30-1 when an overpressure arises within the eccentric screw pump 30-1.
  • the backflowing medium M R opens into the inlet region 4 of the pump body 3 and is then conveyed again in the conveying direction FR by the eccentric screw pump 30-1.
  • one or more overflow valves 40 for limiting the delivery pressure of the eccentric screw pump 30-1 are arranged, whose outlet opens into the interior of the pump body 3 in the inlet region 4 ,
  • the arrangement of an overflow valve 40 in the cavity 43 is in FIG. 3 shown in detail.
  • FIG. 4 shows an eccentric screw pump 30-2 according to the invention.
  • the stator 7-2 is surrounded by a stator sleeve 50.
  • a connecting line 52 is at least partially formed parallel to the longitudinal axis L of the eccentric screw pump 30-2.
  • the connecting line 52 has at the pressure-side end of the eccentric screw pump 30-2 a first connection 55 to the interior of the eccentric screw pump 30-2 in the outlet region 6.
  • the connecting line 52 at the suction end of Eccentric screw pump 30-2 a second connection 56 to the interior of the eccentric screw pump 30-2 in the inlet region 4.
  • the first connection 55, the connection line 52 and the second connection 56 form a return flow passage, through which a portion of the medium M R can flow from the pressure side D back to the suction side S of the eccentric screw pump 30-2 when an overpressure arises within the eccentric screw pump 30-2 ,
  • the backflowing medium M R opens into the inlet region 4 of the pump body 3 and is then conveyed again in the conveying direction FR by the eccentric screw pump 30-2.
  • one or more overflow valves 40 for limiting the delivery pressure are arranged.
  • FIG. 5 shows a third embodiment of an eccentric screw pump 30-3 according to the invention.
  • an at least partially hollow rotor 8-3 is used.
  • the rotor 8-3 comprises a cavity 60 which extends along the rotor longitudinal axis L R.
  • the rotor 8-3 has at its drive end connecting bores 62 between the outer circumferential surface of the rotor 8-3 and the cavity bore 60, for establishing a fluid connection between the cavity 60 and the interior of the pump body 3 in the inlet region 5 of the eccentric screw pump 30-3.
  • an overflow valve 40 is additionally integrated.
  • the cavity 60 of the rotor 8-3 and the connecting bores 62 form a return flow passage, through which a portion of the medium M R can flow from the pressure side D back to the suction side S of the eccentric screw pump 30-3 when an overpressure within the eccentric screw pump 30-3 arises.
  • the backflowing medium M R opens into the inlet region 4 of the pump body 3 and is then conveyed again in the conveying direction FR by the eccentric screw pump 30-3.
  • FIG. 6 shows a fourth embodiment of an eccentric screw pump 30-4 according to the invention.
  • the used stator 7-4 cast-in return flow channels 65 parallel to the rotor longitudinal axis LR, which form a fluid connection with the interior of the pump body 3 in the outlet region 6 and with the interior of the pump body 3 in the inlet region 4.
  • the return flow channels 65 in which in each case at least one overflow valve 40 can be arranged, a portion of the medium M R flows when an overpressure arises within the Eccentric screw pump 30-4 from the pressure side D back to the suction side S of the eccentric screw pump 30-4.
  • the backflowing medium M R opens into the inlet region 4 of the pump body 3 and is then again conveyed in the conveying direction FR by the eccentric screw pump 30-4.
  • the overflow valve 40 can also be integrated and arranged in the pump body such that the medium M R flowing back through the return flow passages 65 of the stator 7 4 flows through the overflow valve 40 before it opens into the inlet region 4 of the pump body 3.
  • FIG. 7 shows a fifth embodiment of an eccentric screw pump 30-5 according to the invention.
  • the stator 7-5 also cast-in return flow channels 65. These are in fluid communication with the interior of the pump body 3 in the outlet region 6 and with the interior of the pump body 3 in the inlet region 4 via first and second connections 66, 67.
  • the overflow valve 40 * is integrated around the discharge nozzle into the outlet region 6 of the pump body 3. The outlet opening of the overflow valve 40 * opens into one or more first connections 66 and thus into one or more of the cast-in return flow passages 65.
EP20140003567 2013-10-24 2014-10-18 Pompe à vis sans fin excentrique et utilisation d'une pompe à vis sans fin excentrique Withdrawn EP2873862A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201310111716 DE102013111716B3 (de) 2013-10-24 2013-10-24 Exzenterschneckenpumpe und Verwendung einer Exzenterschneckenpumpe

Publications (1)

Publication Number Publication Date
EP2873862A1 true EP2873862A1 (fr) 2015-05-20

Family

ID=51752975

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20140003567 Withdrawn EP2873862A1 (fr) 2013-10-24 2014-10-18 Pompe à vis sans fin excentrique et utilisation d'une pompe à vis sans fin excentrique

Country Status (7)

Country Link
US (1) US20150118085A1 (fr)
EP (1) EP2873862A1 (fr)
CN (1) CN104564655A (fr)
AU (1) AU2014240308B2 (fr)
BR (1) BR102014025717A2 (fr)
DE (1) DE102013111716B3 (fr)
RU (1) RU2014142779A (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3020097B1 (fr) * 2014-04-22 2019-07-19 Pcm Technologies Pompe a cavites progressantes
ES2890807T3 (es) * 2014-05-12 2022-01-24 Hugo Vogelsang Maschb Gmbh Bomba de tornillo excéntrico con montaje a través del rotor hueco
DE102015101352A1 (de) * 2015-01-29 2016-08-04 Netzsch Pumpen & Systeme Gmbh Stator-Rotor-System und Verfahren zum Einstellen eines Stators in einem Stator-Rotor-System
CN106678036B (zh) * 2015-11-10 2019-01-11 耐驰（兰州）泵业有限公司 用于偏心螺杆泵的可调整定子
DE102016207247A1 (de) * 2016-04-28 2017-11-02 BSH Hausgeräte GmbH Exzenterschneckenpumpe
DE102018117374A1 (de) * 2018-07-18 2020-01-23 Seepex Gmbh Pumpengehäuse
CN108825511A (zh) * 2018-07-23 2018-11-16 无锡唯勒科技有限公司 单螺杆转子泵

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2505136A (en) * 1946-06-18 1950-04-25 Robbins & Myers Internal helical gear pump
US4076466A (en) * 1973-05-18 1978-02-28 Swanson Engineering, Inc. Fluid pump for use in explosive bore holes
DE3818508A1 (de) * 1988-05-31 1989-12-07 Netzsch Mohnopumpen Gmbh Exzenterschneckenpumpe in sterilisierbarer ausfuehrung
EP0482912A1 (fr) * 1990-10-23 1992-04-29 Halliburton Company Pompe de fond de puits pour essai de formation
US20080050249A1 (en) 2006-08-23 2008-02-28 Higra Industrial Ltda Progressive vortex pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2527673A (en) * 1947-02-28 1950-10-31 Robbins & Myers Internal helical gear pump
US3011445A (en) * 1957-11-13 1961-12-05 Robbin & Myers Inc Helical gear pump with by-pass
US4011917A (en) * 1974-08-19 1977-03-15 Wladimir Tiraspolsky Process and universal downhole motor for driving a tool
DE4330226C1 (de) * 1993-09-07 1994-09-08 Bornemann J H Gmbh & Co Exzenterschneckenpumpe
US7757781B2 (en) * 2007-10-12 2010-07-20 Halliburton Energy Services, Inc. Downhole motor assembly and method for torque regulation
AR064436A1 (es) * 2007-12-19 2009-04-01 Knoop Eberardo Acoplamiento entre motor y rotor helicoidal para bombas de cavidad progresiva
CN201318291Y (zh) * 2008-12-17 2009-09-30 杭州兴龙泵业有限公司 磺酸盐专用螺杆泵撬装系统

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2505136A (en) * 1946-06-18 1950-04-25 Robbins & Myers Internal helical gear pump
US4076466A (en) * 1973-05-18 1978-02-28 Swanson Engineering, Inc. Fluid pump for use in explosive bore holes
DE3818508A1 (de) * 1988-05-31 1989-12-07 Netzsch Mohnopumpen Gmbh Exzenterschneckenpumpe in sterilisierbarer ausfuehrung
EP0482912A1 (fr) * 1990-10-23 1992-04-29 Halliburton Company Pompe de fond de puits pour essai de formation
US20080050249A1 (en) 2006-08-23 2008-02-28 Higra Industrial Ltda Progressive vortex pump

Also Published As

Publication number Publication date
DE102013111716B3 (de) 2015-03-19
BR102014025717A2 (pt) 2015-09-22
AU2014240308B2 (en) 2016-03-31
RU2014142779A (ru) 2016-05-20
US20150118085A1 (en) 2015-04-30
AU2014240308A1 (en) 2015-05-14
CN104564655A (zh) 2015-04-29

Similar Documents

Publication Publication Date Title
DE102013111716B3 (de) Exzenterschneckenpumpe und Verwendung einer Exzenterschneckenpumpe
DE102013102030B3 (de) Schraubenspindelpumpe
DE2720130A1 (de) Meisseldirektantrieb fuer tiefbohrwerkzeuge
EP3236074B1 (fr) Pompe rotative comprenant une rainure de graissage dans une nervure d'étanchéité
DE102014222322B3 (de) Flügelzellenpumpe mit verbessertem Startverhalten
DE102013102031B4 (de) Aus wenigstens zwei Teilen gebildete Schraubenspindelpumpe
DE102010035597A1 (de) Lageranordnung für eine Pumpe
EP2935890A2 (fr) Pompe polyvalente
DE102009017452B4 (de) Ölförderpumpe
DE102013100451B4 (de) Rotor für Schnecken- und / oder Exzenterschneckenpumpen und Schnecken- oder Exzenterschneckenpumpe
DE102021214256A1 (de) Gerotoreinrichtung und Pumpeneinrichtung mit Gerotoreinrichtung
WO2020020902A1 (fr) Dispositif de refoulement de fluide
DE102008059636A1 (de) Pumpenanordnung
WO2015104012A1 (fr) Pompe à vis excentrique, accouplement à pivot et procédé de production d'un accouplement à pivot
DE102018112492B3 (de) Schraubenspindelpumpe
DE102015215982B4 (de) Pumpe sowie System zur Versorgung eines Verbrauchers
DE102008042233A1 (de) Exzenterschneckenpumpe sowie mechanisches Koppelelement für die Exzenterschnecke einer Exzenterschneckenpumpe
EP0628725A2 (fr) Pompe à engrenages
DE202020107544U1 (de) Pumpe mit 3D-gedruckten Rotoren
EP4198309A1 (fr) Pompe à vis
DE3545698C1 (en) Clutch fitted to an internal combustion engine
DE102004030123B3 (de) Schraubenspindelpumpe
EP3572666A1 (fr) Élément de raccordement d'une pompe de transport de fluide
WO2024052400A1 (fr) Système de pompe pour un entraînement d'essieu électrique
DE102022125309A1 (de) Totraumarme radiale Dichtung

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20141018

AK Designated contracting states

Kind code of ref document: A1

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

AX Request for extension of the european patent

Extension state: BA ME

R17P Request for examination filed (corrected)

Effective date: 20151120

RBV Designated contracting states (corrected)

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

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

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20171211