EP3449128A1 - Pompe à cavité progressive - Google Patents

Pompe à cavité progressive

Info

Publication number
EP3449128A1
EP3449128A1 EP17717685.6A EP17717685A EP3449128A1 EP 3449128 A1 EP3449128 A1 EP 3449128A1 EP 17717685 A EP17717685 A EP 17717685A EP 3449128 A1 EP3449128 A1 EP 3449128A1
Authority
EP
European Patent Office
Prior art keywords
pump
eccentric screw
drive wheel
screw pump
rotor
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.)
Granted
Application number
EP17717685.6A
Other languages
German (de)
English (en)
Other versions
EP3449128B1 (fr
Inventor
Hans Eglmeier
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete 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 BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Priority to PL17717685T priority Critical patent/PL3449128T3/pl
Publication of EP3449128A1 publication Critical patent/EP3449128A1/fr
Application granted granted Critical
Publication of EP3449128B1 publication Critical patent/EP3449128B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • 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
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the present invention relates to an eccentric screw pump, in particular an eccentric screw pump for a dosing system for a domestic appliance, for example a washing machine.
  • metering pumps for fluids, in particular for liquid detergent, are of interest for being used as part of a metering system in domestic appliances.
  • Dosing systems with dosing pumps in different variants are known, such as, for example, volumetric pumps in the form of gear pumps, peristaltic pumps, or piston pumps.
  • an eccentric screw pump in principle has only a single moving part, this is relatively inexpensive and robust and should therefore be well suited in principle for use in household appliances, especially as a metering pump.
  • the simplicity of an eccentric screw pump requires a relatively complicated drive, since a two-dimensional movement of the rotor of the eccentric screw pump must be realized, which consists of a superposition of a self-rotation of the rotor and an opposite rotation of the rotor axis on a cylinder shell with the same frequency.
  • Drives of known progressing cavity pumps are due to their complexity and the associated costs hardly suitable to be used as part of a metering pump in a domestic appliance, in particular a washing machine.
  • the present invention has for its object to provide an eccentric screw pump with a simple design and inexpensive drive system, wherein the progressive cavity pump, apart from the drive system, has only a single moving part for conveying a fluid, and the drive system is suitable for realizing the two-dimensional movement of a rotor of the progressing cavity pump.
  • an eccentric screw pump which comprises a pump rotor and a pump stator, wherein the pump stator defines a cavity in which at least a part of the pump rotor is rotatably arranged, and the pump rotor is formed, rotated by a drive wheel to promote a fluid, wherein the pump rotor is mounted eccentrically on the drive wheel.
  • an eccentric screw pump is provided with a simple design drive, which is designed to realize the required in an eccentric screw pump complex two-dimensional movement of the pump rotor.
  • the eccentric screw pump is designed as a 2: 1 hypocycloidal progressing cavity pump, wherein the 2: 1 hypocycloid is defined by a first circle with a radius R, which unrolls without slipping on the inside of a second circle with a radius 2R.
  • the pump rotor is mounted eccentrically on the drive wheel such that the longitudinal axis of the pump rotor extends at a distance R from the center of the drive wheel.
  • the drive wheel is a toothed wheel and the eccentric screw pump further comprises a drive worm, which is designed to drive the drive wheel.
  • the drive wheel has a circular circumference. According to a further preferred embodiment, the drive wheel is a crown wheel with teeth or cylindrical pins.
  • the drive wheel is a bevel gear.
  • the drive wheel comprises a groove-like toothing.
  • the drive wheel has a kidney-shaped circumference and the eccentric screw pump further comprises a motor-side drive wheel, which is designed to drive the drive wheel.
  • the pump rotor and the drive wheel are integrally formed.
  • the pump stator comprises a bearing which is designed to receive the drive wheel and / or the pump rotor in stock.
  • the pump stator defines an outlet for discharging the pumped fluid.
  • the pump stator comprises a leakage drain.
  • the pump rotor and the pump stator have a respective shape defining a periodicity along the longitudinal axis of the pump rotor, the length of the pump rotor and the pump stator corresponding to at least one period along the longitudinal axis of the pump stator.
  • a domestic appliance in particular a washing machine, with an eccentric screw pump according to the first aspect of the invention is provided. Show it:
  • FIG. 1 is a schematic representation for illustrating the kinematics of an eccentric screw pump according to an embodiment
  • FIG. 2 shows a schematic representation of a kinematic model for illustrating the movement of a pump rotor of an eccentric screw pump according to an embodiment
  • FIG. 3 shows a schematic representation of a drive of a progressing cavity pump according to an embodiment based on the kinematic model of FIG.
  • FIG. 4 shows a schematic representation to illustrate the sequence of movements in the drive of FIG. 3,
  • FIG. 5 shows a cross-sectional view of a pump stator and a pump rotor of an eccentric screw pump according to one embodiment
  • FIG. 6 shows a perspective view of a progressing cavity pump according to an embodiment
  • FIG. 7 shows a plan view of the eccentric screw pump from FIG. 6,
  • FIG. 8 shows a longitudinal section of the eccentric screw pump from FIG. 6,
  • FIG. 9 shows a perspective sectional view of the rotor of the eccentric screw pump of FIG. 6, and FIG. 10 shows a schematic representation of a drive of a progressing cavity pump according to a further embodiment.
  • FIG. 1 illustrates the kinematics of a rotor 107 relative to a stator 109, as implemented in an eccentric screw pump 100 according to an embodiment of the invention described in detail below, in particular in connection with FIGS. 6 to 9, which is a 2: 1 Hypocycloid eccentric screw pump 100 acts.
  • the movement of the rotor 107 can be described by means of a first circle 10 with a radius R which is twice as large as the first circle 10 in a second circle 20 (ie with a radius 2R; Ratio 2: 1), rolls without slip.
  • the eccentricity of the movement of the rotor 107 corresponds to the radius R of the first rolling circle 10.
  • the center of the rolling first circle 10, i. the center of the rotor 107 (or the piercing point of the longitudinal axis of the rotor 107 in the plan view of FIGS. 1 to 3) describes in its movement a further circle which is concentric with the second circle 20 and of which in FIG Arrow a section is indicated.
  • the diameter of the further circle described by the first circle 10 corresponds more or less to the "piston stroke" of the eccentric screw pump 100, as will be explained below in connection with FIG. 5 in particular.
  • the illustrated in Figure 1 kinematics of the eccentric screw pump 100 can be realized by means of a kinematic model, which is shown in Figure 2.
  • This kinematic model consists of a coupling 101, which has a fixed length 2R and at the two ends of which a sliding element 102a, 102b is pivotally connected to the coupling 101.
  • the first sliding element 102a is guided along the y-axis and the second sliding element 102b is guided along the orthogonal x-axis of a Cartesian coordinate system.
  • the coupling 101 corresponds to the diameter of the first circle 10 of FIG. 1, that is to say it has a length of 2R.
  • the center of the coupling 101 performs a circular motion with the radius R around the origin of the coordinate system, which coincides with the center of the second circle 20.
  • the first and second sliding elements 102a, 102b each perform a linear oscillation with the amplitude 2R along the y-axis and the x-axis, respectively, with the oscillation of the first sliding element 102a being 90 ° out of phase the oscillation of the second sliding element 102b takes place.
  • the first slider 102a is located at the origin of the coordinate system when the second slider 102b is at its maximum deflection, and vice versa.
  • the eccentric screw pump 100 is designed such that the center of the coupling 101 of the kinematic model of FIG. 2 coincides with the longitudinal axis of the rotor 107 (more precisely with the penetration point of the longitudinal axis) of the eccentric screw pump 100.
  • FIG. 5 which shows a cross-sectional view of the pump stator 109 and the pump rotor 107 of the eccentric screw pump 100 according to such an embodiment, a circular rotor cross-section in an oblong-shaped stator cross-section is provided in each cross-section perpendicular to the longitudinal axis of the pump rotor 107.
  • FIG. 5 shows a cross-sectional view at a height along the longitudinal axis of the rotor 107, which corresponds to a guide of the rotor 107 through the stator 109 in the x-direction analogous to the guide of the second sliding element 102b of FIG.
  • a guide of the rotor 107 is defined by the stator 109 in a respective direction, for example, orthogonal to the guide of Figure 5, i. a guide in the y-direction is analogous to the guide of the first sliding element 102a of Figure 1, or at a different angle thereto.
  • FIG. 5 shows three excellent points P1, P2 and P3 of the eccentric screw pump 100 according to one embodiment.
  • the point P1 is the center of the pump stator 109.
  • Each cross section of the stator 109 has the point P1 as the center of symmetry.
  • the point P3 is located at a distance 2R from the center of the stator 109, ie from the point P1, in the illustrated phase, ie at the illustrated height, on the x-axis.
  • This point P3 on the rotor 107 performs in the reference system of the stator 109 for the cross section shown here by way of example an oscillation along the x-axis with the amplitude 2R, ie a "piston stroke" of 4R in total.
  • the point P3 corresponds to the circle center of the rotor cross section.
  • the circle center of the drive wheel 103, ie the Drive wheel axis runs through this point.
  • the drive wheel 103 in the reference system of the stator 109 performs an oscillating movement in the x-direction.
  • the rotor axis passes through the point P2, which is located at a distance R from the stator center point P1.
  • this point P2 moves in the reference frame of the stator 109 on a circle of radius R about the stator center point P1.
  • the point P2 moves on a circle of radius R around the center of the circle of the rotor cross-section, ie around the point P3.
  • a pin described below in connection with FIG. 7 may be attached to the drive wheel 103, which serves to generate an axial force on the rotor 107.
  • the pin in the reference frame of the stator 109 performs a circular movement (in Figure 7, the movement circle of the pin center is drawn).
  • the points P1, P2 and P3 marked in Fig. 5 correspond in Fig. 2 but which corresponds to a different orientation of the rotor 107 (namely an orientation with an angle ⁇ of approximately 60 °), the center of the large circle 20 (P1), i. the stator center, the center of the coupling 101 (P2), i. the rotor axis rotating in the reference frame of the stator 109 on a circle of radius R around the stator center point, and the fulcrum point of the second slider 102b (P3), i. the center of the rotor cross-section oscillating along the x-axis.
  • FIG. 3 illustrates an implementation of the kinematic model of FIG. 2 in the context of a drive mechanism of the eccentric screw pump 100 according to one embodiment.
  • the drive mechanism comprises a round drive gear in the form of a gear 103 and a cylindrical drive worm 105 which is designed to interact in a known manner with the teeth of the gear 103 (inter alia the exemplary tooth 103a), such as by a drive motor caused rotational movement of the drive screw 105 in a rotation of the gear 103 results.
  • the drive wheel 103 is thus fixed centrally at the point corresponding to the position of the first sliding element 102a in the kinematic model of FIG. 2, and the pump rotor 107 is connected to the drive gear 103 such that the coupling 101 is connected to the diameter the pump rotor 107 or the center point of the coupling 101 coincides with the longitudinal axis of the pump rotor 107.
  • the pump rotor is eccentrically attached thereto at a distance R from the center of the drive wheel 103.
  • Figure 4 shows the relative positions of the drive wheel 103 to the drive screw 105 of the eccentric screw pump 100 according to an embodiment in a full revolution of the drive wheel 103.
  • the coupling and the sliding elements in the views of Figure 4 are not actually present in the eccentric screw pump 100, but merely serve to illustrate that the kinematic model of Figure 2 is realized.
  • the movement of the pump rotor 107 of the eccentric screw pump 100 may be thought of as the movement of the circle whose diameter is defined by the coupling, as already described above.
  • Figure 4 illustrate again that at a full revolution of the drive wheel 103 whose center is oscillating only in the y-direction, ie in the vertical direction back and forth, but no movement in the x-direction, ie horizontal direction
  • the distance between the center of the drive wheel 103 and the longitudinal axis of the drive worm 105 does not change.
  • FIGS. 6 to 9 show different views of an embodiment of the eccentric pump screw 100, namely a perspective view, a plan view, a longitudinal section and a perspective sectional view.
  • the drive wheel 103 is designed as helical geared spur gear 103, for example the tooth 103a, which can be driven by the drive worm 105 designed as a cylindrical worm.
  • the eccentric attachment of the pump rotor 107 to the drive wheel 103 can be seen for example in the plan view of Figure 7. It should be noted that the center of the upwardly projecting pin on the gear 103 is not the pivot point about which the gear 103 rotates (eccentrically) because, as already described above in connection with Figure 5, the pin is a circular motion performs while the gear 103 rotates about its geometric center. In one embodiment, the pin may serve to press the pump rotor 107 axially into the pump stator 109 by means of a pressure plate. The pin slides with the above-mentioned movement on the printing plate.
  • the longitudinal section through the eccentric screw pump 100 shown in FIG. 8 shows the pump rotor 107 in one Orientation in which the maximum eccentricity of the drive wheel 103 is just in the plane of the drawing.
  • the pump rotor 107 can be formed in one piece with the drive wheel 103.
  • a portion of the pump stator 109 (in Figure 8, the upper portion of the pump stator 109), for example, as part of a housing may be designed to serve as a bearing for the drive wheel 103 and / or the pump rotor 107, the above-described oscillating movement of the drive wheel 103 allows.
  • the pump stator 109 may further include an outlet 1 13 for discharging a conveyed fluid and a leakage drain 1 1 1.
  • the leakage drain 1 1 1 serves to be able to discharge fluid conveyed by the eccentric screw pump 100, which exits from the sealing shoulder below the drive wheel 103.
  • Both the shape of the pump rotor 107 and the corresponding shape of the pump stator 109 have a periodicity along the longitudinal axis of the pump rotor 107, the rotor period is usually half as large as the stator period.
  • the length of pump rotor 107 and pump stator 109 corresponds to approximately 3.8 rotor periods along the longitudinal axis of pump rotor 107, which corresponds to one-to-one stator periods.
  • the length of the pump rotor 107 and the pump stator 109 should correspond to at least one period along the longitudinal axis of the pump stator 109, ie, a stator period.
  • these values result in an overall movement in which the fluctuations caused by the oscillation of the gearwheel 103, for example in the torque or in the rotor speed, are comparatively low are and without any practical limitations in terms of eg smoothness in purchasing can be accepted.
  • the drive gear 103 can also be formed as a crown gear with teeth or cylindrical pins, as bevel gear, especially in Globoidversion, or as Globoidrad.
  • the toothing of the drive wheel 103 embodied, for example, as a spur wheel can be formed like a hollow-chevron.
  • the globoid variant can also be applied to the other gear shapes.
  • FIG. 10 shows a schematic plan view of a circular motor-side drive wheel 205 and a drive wheel 203 of the pump rotor 107 of the eccentric screw pump 100.
  • FIG. 10 shows a schematic plan view of a circular motor-side drive wheel 205 and a drive wheel 203 of the pump rotor 107 of the eccentric screw pump 100.
  • the above-described movement of the drive wheel 203 of the pump rotor 107 i. an internal rotation with opposite oscillation
  • the circumference of the drive wheel 203 of the pump rotor 107 is formed substantially kidney-shaped.
  • the eccentric screw pump 100 has, inter alia, the following advantages.
  • the eccentric screw pump 100 according to the invention has (apart from the drive worm 105 or the drive wheel 205) only a single moving part, namely the pump rotor 107 together with the drive wheel 103, which, as described above, can also be integrally formed. To compensate for the eccentric motion 100 no additional component is required in the eccentric screw pump 100 according to the invention. It is therefore a technically simple to be realized solution, especially since the only moving part, ie the pump rotor 107 in conjunction with the drive wheel 103 of the eccentric screw pump 100, rigid (non-elastic) can be formed.
  • the eccentric screw pump 100 according to the invention can be designed to be very compact, since a required in conventional pumps eccentric compensation, for example in the form of a propeller shaft, can be omitted, which usually takes a large overall length. Given the space available, the length saved in the eccentric screw pump 100 according to the invention can be converted into additional length of a pumping cell. Since the length of the pumping cell is generally proportional to the length of the contact line between the rotor 107 and the stator 109 of the eccentric screw pump 100, which is also referred to as a sealing contour, the eccentric screw pump 100 according to the invention can be made correspondingly more fluid-tight and thus dose more accurately, i.
  • the actual volumetric flow corresponds better to the nominal volumetric flow rate (in practice, minimal slippage is usually unavoidable).
  • a larger gap between the rotor 107 and the stator 109 of the eccentric screw pump 100 according to the invention use, resulting in a reduction of the required accuracy of the components and thus ultimately to a reduction in the cost of the eccentric screw pump 100 given dosing.
  • eccentric screw pump 100 in contrast to eccentric screw pumps with elastic couplings, e.g. a spring-bar coupling or a cardan shaft with elastic joints, only a small additional bearing load, since no lateral forces are generated. Therefore, the components of the eccentric screw pump 100 according to the invention are not subject to component fatigue due to strong bending cycle stress.
  • elastic couplings e.g. a spring-bar coupling or a cardan shaft with elastic joints
  • the combination of rotor 107 and stator 109 of the eccentric screw pump 100 according to the invention enables exactly the movement described above with reference to the kinematic model of FIG. Since in this case the drive wheel 103 performs this movement, no additional bearing is required in the eccentric screw pump 100 according to the invention. at Embodiments of the eccentric screw pump 100, this area can serve only as a seal with a correspondingly selected fluid guide.
  • the drive wheel 103 in the form of the gear in any phase i. in any angular orientation, connect with the drive worm 105.
  • the gear 103 it is not necessary to note a particular angular orientation of the gear 103 relative to the drive worm 105, which greatly simplifies assembly and reduces assembly costs over pump designs where the drive gear must be mounted in phase.

Landscapes

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

Abstract

Pompe à cavité progressive (100) comprenant un rotor (107) et un stator (109), ce dernier (109) définissant une cavité dans laquelle au moins une partie du rotor (107) est montée rotative, ledit rotor (107) étant conçu pour être entraîné en rotation par un pignon d'entrainement (103, 203) afin de refouler un fluide, ledit rotor (107) étant monté de manière excentrée sur le pignon d'entraînement (103, 203).
EP17717685.6A 2016-04-28 2017-04-12 Pompe à cavité progressive Active EP3449128B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL17717685T PL3449128T3 (pl) 2016-04-28 2017-04-12 Pompa śrubowa jednowirnikowa

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016207247.1A DE102016207247A1 (de) 2016-04-28 2016-04-28 Exzenterschneckenpumpe
PCT/EP2017/058807 WO2017186497A1 (fr) 2016-04-28 2017-04-12 Pompe à cavité progressive

Publications (2)

Publication Number Publication Date
EP3449128A1 true EP3449128A1 (fr) 2019-03-06
EP3449128B1 EP3449128B1 (fr) 2021-11-17

Family

ID=58548694

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17717685.6A Active EP3449128B1 (fr) 2016-04-28 2017-04-12 Pompe à cavité progressive

Country Status (5)

Country Link
EP (1) EP3449128B1 (fr)
CN (1) CN109072904B (fr)
DE (1) DE102016207247A1 (fr)
PL (1) PL3449128T3 (fr)
WO (1) WO2017186497A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111120298B (zh) * 2019-12-16 2020-09-25 大庆市华禹石油机械制造有限公司 一种基于偏心传动的泵

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2483370A (en) * 1946-06-18 1949-09-27 Robbins & Myers Helical multiple pump
ZA79440B (en) * 1978-02-10 1980-09-24 Oakes Ltd E T Drive arrangement
GB2120729B (en) * 1982-05-21 1985-07-24 Mono Pumps Ltd Helical gear pump
JPS6196193A (ja) * 1984-10-17 1986-05-14 Heishin Sobi Kk 一軸偏心ねじポンプの駆動装置
CN2345736Y (zh) * 1998-06-11 1999-10-27 中国科学院大连化学物理研究所 一种螺杆泵
DE10212184A1 (de) 2002-03-20 2003-10-09 Ecolab Gmbh & Co Ohg Verfahren zum Dosieren eines pastösen Waschmittelkonzentrats
DE10243674B3 (de) * 2002-09-20 2004-04-01 Netzsch-Mohnopumpen Gmbh Exzenterschneckenpumpe mit Reservestator
JP5070515B2 (ja) * 2007-03-08 2012-11-14 兵神装備株式会社 ロータ駆動機構及びポンプ装置
GB2454700B (en) * 2007-11-15 2013-05-15 Schlumberger Holdings Work extraction from downhole progressive cavity devices
CN202560176U (zh) * 2012-05-14 2012-11-28 大庆永磁电机制造有限公司 一种带渗漏液溢流系统的螺杆泵直驱装置
JP6188015B2 (ja) * 2013-05-21 2017-08-30 兵神装備株式会社 一軸偏心ねじポンプ
DE102013111716B3 (de) * 2013-10-24 2015-03-19 Netzsch Pumpen & Systeme Gmbh Exzenterschneckenpumpe und Verwendung einer Exzenterschneckenpumpe
CN103711691A (zh) * 2014-01-06 2014-04-09 中国石油大学(华东) 可平衡轴向力和径向力的单螺杆泵
CN205135988U (zh) * 2015-11-23 2016-04-06 重庆高研泵业有限公司 安全螺杆泵

Also Published As

Publication number Publication date
WO2017186497A1 (fr) 2017-11-02
DE102016207247A1 (de) 2017-11-02
CN109072904B (zh) 2020-01-10
PL3449128T3 (pl) 2022-03-28
EP3449128B1 (fr) 2021-11-17
CN109072904A (zh) 2018-12-21

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