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EP2275684A1 - Agencement doté d'une pompe à roue dentée - Google Patents

Agencement doté d'une pompe à roue dentée Download PDF

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Publication number
EP2275684A1
EP2275684A1 EP09163049A EP09163049A EP2275684A1 EP 2275684 A1 EP2275684 A1 EP 2275684A1 EP 09163049 A EP09163049 A EP 09163049A EP 09163049 A EP09163049 A EP 09163049A EP 2275684 A1 EP2275684 A1 EP 2275684A1
Authority
EP
European Patent Office
Prior art keywords
gear
arrangement according
drive
drive unit
gear pump
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Withdrawn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
EP09163049A
Other languages
German (de)
English (en)
Inventor
Markus Aregger
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.)
Maag Pump Systems AG
Original Assignee
Maag Pump Systems AG
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 Maag Pump Systems AG filed Critical Maag Pump Systems AG
Priority to EP09163049A priority Critical patent/EP2275684A1/fr
Priority to JP2010136816A priority patent/JP2011001955A/ja
Priority to US12/818,615 priority patent/US20100322806A1/en
Publication of EP2275684A1 publication Critical patent/EP2275684A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • 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
    • 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
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • 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
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring

Definitions

  • the present invention relates to an arrangement according to the preamble of claim 1.
  • Gear pumps consist of two intermeshing gears which are mounted on shafts, usually a shaft is connected to a drive unit.
  • the shaft which is not driven by a drive unit, is driven by means of torque transmission from the driven shaft via the tooth flanks.
  • a gear pump is known, in turn, two drive units are provided for individually driving the waves, wherein phase and angular velocity of the intermeshing gears are coordinated such that on the one hand lifting of tooth flanks of intermeshing gears and on the other hand too high excess torque on the tooth flanks Interlocking gears are avoided.
  • the present invention relates to an arrangement with a gear pump comprising a pump housing, two gears contained in the pump housing and intermeshing gears and two shafts, which are operatively connected to the gears and are guided by the pump housing, wherein the two shafts, each with a drive unit (7 , 8) are operatively connected.
  • a gear pump comprising a pump housing, two gears contained in the pump housing and intermeshing gears and two shafts, which are operatively connected to the gears and are guided by the pump housing, wherein the two shafts, each with a drive unit (7 , 8) are operatively connected.
  • a coupling unit for the adjustment of eccentricities between the drive unit and the respective shaft is arranged and that in each case a rotary encoder / sensor unit is arranged between the middle of the gear and the drive center.
  • a variant of the inventive arrangement is characterized in that the encoder / sensor unit is in an axial range, which is defined by the center between the gear center and the drive center plus a two-sided deviation of not more than 10% of the distance between the center of the gear and drive center.
  • rotary encoder / sensor units are each arranged in the middle between the respective gear center and the respective drive center.
  • rotary encoder / sensor unit to the axis of rotation of the respective shaft have a radial distance which is larger, preferably at least twice as large as an outer radius of the gears.
  • rotary encoders / sensor units are either optical or magnetic encoders / sensor units.
  • Rotary encoder / sensor units are arranged such that a standing perpendicular to the shaft and extending through the corresponding encoder / sensor unit connecting line with a centrally extending between the two axes of rotation suction side an angle in the range of 35 ° to 55 °, preferably 40 ° to 50 ° , preferably 45 °, includes.
  • each drive unit comprises a rotor and a stator, wherein the rotor is axially displaceable with respect to the stator.
  • the drive unit has on the side remote from the gear pump side a compensating bearing unit which radially supports the rotor of the drive unit.
  • the coupling unit is a diaphragm coupling.
  • drive units can be connected to the respective shaft of the gear pump from the side applied in relation to the gear pump.
  • connection between the drive units and the respective shafts of the gear pump are conical polygonal connections.
  • the one drive unit, the gear pump and the other drive unit are each contained in a temperature zone in which the temperatures are adjustable to predetermined values, wherein between adjacent temperature zones preferably isolation areas are present.
  • Further embodiments of the inventive arrangement are characterized in that the determination of the current position of the one gear with respect to the current position of the other gear is adjustable over a reference value, which can be determined before the normal operation of the gear pump or during interruptions of normal operation of the gear pump is.
  • inventions of the inventive arrangement are characterized in that the reference value in the middle between tooth flanks of a tooth gap of a toothed wheel, preferably in the middle between tooth flanks of a tooth gap of a toothed wheel, is located.
  • an arrangement with a gear pump is specified, which is automatically calibrated.
  • the arrangement can perform this calibration both before startup and during service interruptions, without further action by the operator must be made.
  • a possible wear of tooth flanks can be determined, because then changed resp. the difference between the first angular difference and the second angular difference also increases. Excessive closure can then be detected by a simple threshold violation.
  • each encoder / sensor unit are arranged centrally between the teeth of the respective gear and a rotor of the respective drive.
  • a central arrangement of the encoder / sensor units has the advantage that an existing angle of rotation due to a non-ideal rigidity of the entire drive train has a reduced influence on the measurement error of the system.
  • the measurement error is halved by the central arrangement.
  • This operating condition is also referred to as an edge change, because the touching tooth flanks change in the course of a Ausquetschvorganges.
  • inventions of the inventive arrangement are characterized in that one gear drives the other gear with a predetermined torque, wherein the predetermined torque is greater than half of the total torque generated by the two drives.
  • inventive arrangement is characterized in that the delivery medium pressure is measured on the pressure side of the gear pump and that the speed is adjustable in dependence on the measured delivery medium pressure.
  • a known arrangement is shown with a gear pump 1, the conveying medium F from a suction side S on a pressure side D promotes. It is evident in Fig. 1 a pump housing 10, are guided by the waves 2 and 3 to the outside.
  • the guided outward shaft 3 is connected via a first universal joint 4, an adjustable in length axle 6 and a second universal joint 6 with a drive unit 7. Accordingly, the guided outward shaft 2 via a corresponding first and second universal joint and a corresponding axis section with a further drive unit (in Fig. 1 not shown).
  • gears in Fig. 1 not visible
  • the double universal joint consisting of the first and second universal joint 4 and 5 is provided together with the adjustable axle section 6 for receiving lateral and angular deviations of the drive unit with respect to the shaft 2 and 3, respectively.
  • the additional bearing force is due to a relatively short bearing distance of the pump bearings, which are located in the pump housing 10 to support the shafts 2 and 3, in terms of the length of the double-jointed joint considerably.
  • Fig. 2 is a section through an inventive arrangement shown with a gear pump 1, wherein the cutting plane in the axes of rotation 13 and 14 of the shafts 2 and 3 and by a sensor 25 is placed, according to the in Fig. 4 Plotted sectional plane AA.
  • Fig. 2 shows the sake of simplicity, only one half of the gear pump 1. Accordingly, only one drive unit 7 is shown.
  • the drive unit 7 is pressed directly via a flange 15, ie without intermediate gear, to the pump housing 10 or its lid. Via a screw 21, the rotating parts of the drive unit 7, such as a hub 16, a diaphragm coupling 22 and a rotor 18, connected to the shaft 3 of the gear pump 1.
  • the screw 21 can be released if necessary, whereby the drive unit 7 can be solved by the gear pump 1 again. After loosening screws 40, which connects the flange 15 with the pump housing 10 or with its lid, and after loosening the screw 21, the complete drive unit 7 can be released from the gear pump 1.
  • the shafts 2, 3 of the gear pump and their storage units remain within the gear pump and can be disassembled individually.
  • the drive unit 7 is next to the flange 15 and the hub 16 further comprises a rotor 18, a stator 17 and a drive cover 19 with an opening 20.
  • the drive cover 19 closes the drive unit 7 on the the gear pump 1 side facing away from and is connected to the stator 17, wherein the opening 20 is arranged centrally on the extended axis of rotation 13 of the shaft 3.
  • Gear pump side, the stator 17 is connected to the flange 15.
  • the gear pump 1 is direct, i. without intermediate gear, connected to the drive unit 7.
  • the screw 21 is provided by means of which the rotor 18 is fixed axially via the hub 16 and the flange 15. The screw 21 is guided during the assembly of the drive unit 7 to the gear pump 1 through the opening 20 in the drive cover 19 along the axis of rotation 13 of the shaft 3 and fixed in a corresponding bore in the shaft 3.
  • the hub 16 is connected to the shaft 3 via a so-called conical polygon connection, on the one hand allows a precise axial alignment of the rotor 18 to the shaft 3, on the other hand, a very torsionally rigid connection between the rotor 18 of the drive unit 7 and the driven shaft 3 of the gear pump 1 allows.
  • the membrane coupling 22 and the hub 16 are conceivable, for example, as a single part, as well as from Fig. 2 shows that in the left, drive side half of the individual part of the classic function of a hub which can be coupled to the shaft 3, in the right part of this single part is thin-walled and thus fulfills the functions of a membrane coupling.
  • a compensating bearing 23 is provided on the side facing away from the gear pump 1, which holds the rotor 18 radially in position with respect to the stator 17.
  • a so-called torque motor is used, which is a high-pole permanent-magnet three-phase synchronous motor with hollow shaft rotor for the direct, above-mentioned coupling to the gear pump.
  • Torque motors are characterized in particular by a short compact design and a low torsional backlash (high torsional rigidity).
  • a rotary encoder 24 is arranged, which cooperates with a connected to the stator 17 sensor unit 25.
  • a grid is applied to the hub 16, which is read by the sensor unit 25.
  • corresponding magnetic measuring devices or other methods for position determination can also be used.
  • the rotary encoder 24 In order to minimize any measurement errors due to eccentricity of the rotary encoder 24 to the toothing, the rotary encoder 24 is made as large as possible in diameter. The eccentricity of the encoder 24 itself is minimized by the integration of the inclusion of the encoder 24 in the hub 16. Since the hub 16 is in one piece, very close manufacturing tolerances can be adhered to the inclusion of the encoder 24.
  • the sensor unit 25 is preferably selected between the center of the rotor 18 or stator 17 and the center of the driven gear 11 of the gear pump 1. With a uniform stiffness distribution over the drive train (ie between the center of the rotor 18 and stator 17 and the center of the driven gear 11 of the gear pump 1), the encoder 24 is resp. the sensor unit 25 is preferably arranged in the middle between the center of the rotor 18 and stator 17 and the center of the driven gear 11 of the gear pump 1.
  • a possible field of application of the arrangement with a gear pump is the pressure build-up downstream of an extruder in the conveyance of plastic melts in an extrusion line.
  • the polymer melts are conveyed at temperatures of up to 300 ° C. against high discharge pressures (eg 300 bar).
  • high discharge pressures eg 300 bar
  • high drive power and thus high torques are necessary.
  • the gear pump or the pump housing is heated to a temperature of, for example, 300 ° C, caused by the conveying medium, while the temperature of the drive units 7 and 8, especially for the necessary electronic circuits in these, should not exceed 60 ° C.
  • insulating dividing wall 30 and 31 are required, respectively between the temperature zones 32 and 33 resp. between the temperature zones 33 and 34 are present.
  • additional measures are required as needed, so that the temperature in the cold temperature zones 32 and 34 does not reach unacceptable levels.
  • An additional measure for example, is that an active cooling (for example, an active water cooling) is provided.
  • the rotor 18 ( Fig. 2 ) to protect from over temperature by a cooling of the flange 15 is connected between the hub 16 and the gear pump 1.
  • the cooling is realized for example by star-shaped holes in the flange 15. This achieves very good cooling properties, since the deflections produce high turbulences.
  • the hub 16 is cooled on the entire surface flange side by radiation and forced convection.
  • Fig. 4 shows a possible positioning of the sensor unit 25, which is used to determine the current position of the one gear with respect to the current position of the other gear, wherein Fig. 4 a section transverse to the axes of rotation 11 and 13 of the shafts 2 and 3 shows.
  • the fluid is transported in the direction of arrow from the suction side S with the gear pump on the pressure side D.
  • a force component is generated in the direction of the arrows P, P ', which act on the shaft bearing of the gear pump and to a slight shift of waves 2 and 3 ( Fig. 2 ) to lead.
  • the sensor unit 25 will now move in the direction of displacement, i. in the direction of deflection of the shaft, attached.
  • the attachment takes place, for example, below 45 ° and is thus on average of the possible displacement angle, which is differential pressure dependent and viscosity-dependent.
  • z. B. a schwradbreiten- and game size-dependent arrangement of the sensor unit 25 are made.
  • Fig. 5 shows a section transverse to the axes of rotation 13 and 14 in the region of the gears 11 and 12. conveying medium F is received on the suction side S of the tooth gaps and then transported along the pump housing to the pressure side D, where the medium F through the meshing gears 11, 12 is squeezed out.
  • a "trapped volume” is created in the toothed area between the tooth base and the tooth tip of the toothed wheels, which is due to the almost touching tooth flanks in front of and behind it Volume is sealed.
  • a flow gap can be generated in a targeted manner at the locations where a large flow gap is desired for tribological reasons (optimum gap thickness relative to the tooth flanks). Due to the existing position control of the shafts, the ratio of these two sealing gaps can be actively controlled. Once, the gap leading to the "trapped volume” can be minimized, once the gap following the trapped volume. This makes it possible for the squeezing process to be actively influenced from this "trapped volume", thus optimizing the uniformity of the flow.
  • the first shaft 2 drives the second shaft 3 with a defined torque.
  • a first absolute rotation angle difference with the aid of the illustrated rotary encoder 24 in combination with the sensor unit 25 (FIG. Fig. 2 ) in both waves 2 and 3 determined by determining a difference between a measured value of the one sensor unit 25 and a measured value of the other sensor units 25 '.
  • the second shaft 3 drives the first shaft 3 with the same defined torque as in the first step.
  • a second absolute rotation angle difference is in turn determined by means of the described rotary encoder 24 in combination with the sensor unit 25 in both shafts 2 and 3, again determining the difference between a measured value of the one sensor unit 25 and a measured value of the other sensor units 25 ' ,
  • a difference between the first absolute rotation difference and the second absolute rotation difference is formed.
  • This difference is the actual range in which the gears can move to each other, provided that the defined torque that was used in the first and second step in the measurement is not exceeded.
  • a reference value can now be determined, in relation to which the current positions of the gears are specified.
  • the reference value is then a zero point of a defined coordinate system. For example, the reference value lies in the middle between tooth flanks of a tooth gap, so that the absolute values of the maximum deflections are identical.
  • the operating conditions can now be selected in a first setting, for example, such that one gear transmits half plus a defined percentage of the total torque. Accordingly, then transmits the other gear half minus the defined percentage of total torque.
  • the backlash between the flanks of two intermeshing teeth is selectable, for example, in 10% increments from the contact of the flanks (no backlash) over a central orientation (ie, the teeth entering a tooth space) Tooth lies exactly in the middle of the gap) until the tooth flanks touch again, this time being the trailing tooth flanks.
  • Fig. 6 illustrates the operating conditions just explained in turn in a section transverse to the axes of rotation 13 and 14 in the region of the gears 11 and 12. Again, in the meshing region of the gears 11 and 12, a detail X shown enlarged as detail, in which also an adjusted backlash 26th is shown highlighted.
  • the edge change operation is based on Fig. 7 explained, in turn, sections transverse to the axes of rotation 13, 14 in a region of the meshing gears 11, 12 show.
  • a state is shown in which the tooth Z 1 'of the toothed wheel 11, which engages in a tooth gap of the toothed wheel 12, contacts the tooth Z 1 .
  • a state shown later in time in which the engaging in a tooth gap of the gear 11 tooth Z 2 of the gear 12, the tooth Z 1 'touches.
  • the operating conditions according to the mentioned edge change operation are used, for example, in highly viscous media in which the squeezing pressure is so great that a very large torque is required to produce the squeeze pressure energy, as these represent a pure energy loss.
  • the monitoring of signs of wear can also be exploited to the extent that upon detection of a predetermined level of wear an audible and / or visual warning is given to the supervisor, so that precautions can be taken to prevent failure of the pump system.
  • an audible and / or visual warning is given to the supervisor, so that precautions can be taken to prevent failure of the pump system.
  • pressure fluctuations are eliminated or at least greatly reduced by actively influencing the rotational speeds of the two gear shafts.
  • the inventive arrangement or the inventive method is able to vary the speed curve per Ausquetschvorgang, in such a way that the pressure on the pressure side is within narrow limits, resp. that the pressure on the pressure side is constant.
  • the Ausquetschvorgang of the pumped medium from the tooth base is controlled specifically on the current position of the one gear with respect to the current position of the other gear.
  • a speed curve 90 of the gear pump shaft, a pressure curve 91 of the pressure on the pressure side of the gear pump and a torque curve 92 of the torque of the gear pump shaft is shown.
  • the speed curve 90, the pressure curve 91 and the torque curve 92 are plotted as a function of time t.
  • the speed of the gear pump shaft is in Setting the time function so that the pressure on the pressure side of the gear pump is constant or at least within a predetermined tolerance range.
  • the in Fig. 9 shown speed curve 90 has a periodicity with a period T on. It is the period of time during which a tooth engagement takes place in a corresponding tooth gap. If, therefore, the speed for both shafts is controlled synchronously in accordance with the speed curve 90, the pulsation can be completely compensated.
  • the speed curve 90 Due to the periodicity, it is possible to store the speed curve 90 in a memory unit (Look-up Table). The values for the speed to be set are then read out in a predetermined cycle, the predetermined clock resulting from the pressure to be set on the pressure side.
  • the selective influencing of the position control can also be used for shear-sensitive materials to reduce a total shear stress.
  • care is taken to ensure that a maximum permissible shear load is not exceeded.
  • the present invention makes it possible for the first time to specifically influence the effects of pulsation, crushing pressures and tribological behavior.
  • the settings may take into account all effects that are relevant to the specific case, or individual operating conditions may be considered as a priority. By this is meant that these operating conditions should have a more significant influence on the behavior of the overall system.
  • involute toothings typically used for gear pumps is that the transmission ratio of the two rotational speeds remains constant during one revolution, which is a basic prerequisite for a constant volume flow.
  • circular arc gears have the disadvantage that the transmission ratio of the rotational speeds of the waves periodically fluctuates and thus the delivery medium flow pulsates.
  • the use of the described invention with two controlled drive units makes it possible for the first time to use circular-arc toothing without an undesired pulsation of the delivery medium flow.
  • the drive speeds of the waves can be corrected accordingly and compensated with opposite speed profile, so that circular bevel gears with constant transmission ratio and thus constant flow are possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP09163049A 2009-06-18 2009-06-18 Agencement doté d'une pompe à roue dentée Withdrawn EP2275684A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP09163049A EP2275684A1 (fr) 2009-06-18 2009-06-18 Agencement doté d'une pompe à roue dentée
JP2010136816A JP2011001955A (ja) 2009-06-18 2010-06-16 歯車ポンプを有する装置
US12/818,615 US20100322806A1 (en) 2009-06-18 2010-06-18 Arrangement including a gear pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09163049A EP2275684A1 (fr) 2009-06-18 2009-06-18 Agencement doté d'une pompe à roue dentée

Publications (1)

Publication Number Publication Date
EP2275684A1 true EP2275684A1 (fr) 2011-01-19

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EP09163049A Withdrawn EP2275684A1 (fr) 2009-06-18 2009-06-18 Agencement doté d'une pompe à roue dentée

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EP (1) EP2275684A1 (fr)
JP (1) JP2011001955A (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2505335A2 (fr) 2011-03-31 2012-10-03 Frank Reineke Dispositif d'extrusion pour la production d'un profil en forme de bande ou tube en matière plastique ou de caoutchouc
DE102012216817A1 (de) * 2012-09-19 2014-03-20 Nordson Corporation Dosiereinrichtung für ein Fluid
WO2018206050A1 (fr) * 2017-05-12 2018-11-15 Schaeffler Technologies AG & Co. KG Actionneur électrique de pompe, transmission à variation continue avec actionneur électrique de pompe et procédé de commande pour actionneur électrique de pompe
CN109854498A (zh) * 2019-03-06 2019-06-07 郑州沃华机械有限公司 一种双驱动轴熔体泵及其控制方法
CN114033671A (zh) * 2021-11-09 2022-02-11 中国人民解放军火箭军工程大学 一种圆弧螺旋齿轮泵半接触式端面间隙补偿装置及方法
DE102021206654A1 (de) 2021-06-28 2022-12-29 Zf Friedrichshafen Ag Betätigungsvorrichtung für die Betätigung eines Stellelements einer Stelleinrichtung eines Kraftfahrzeugs
CN119177927A (zh) * 2024-11-22 2024-12-24 江苏芬奇工业设备制造有限公司 一种具有进液防堵的自吸齿轮泵
EP4448971A4 (fr) * 2021-12-16 2025-11-26 Project Phoenix Llc Vérifications de diagnostic d'une pompe à engrenages dans un système fluidique

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH659290A5 (de) 1982-07-08 1987-01-15 Maag Zahnraeder & Maschinen Ag Zahnradpumpe.
EP0886068B1 (fr) 1998-08-25 2003-10-08 Maag Pump Systems Textron AG Pompe à engrenages à arbres d'entraínements multiples

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH659290A5 (de) 1982-07-08 1987-01-15 Maag Zahnraeder & Maschinen Ag Zahnradpumpe.
EP0886068B1 (fr) 1998-08-25 2003-10-08 Maag Pump Systems Textron AG Pompe à engrenages à arbres d'entraínements multiples

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2505335A2 (fr) 2011-03-31 2012-10-03 Frank Reineke Dispositif d'extrusion pour la production d'un profil en forme de bande ou tube en matière plastique ou de caoutchouc
DE102012216817A1 (de) * 2012-09-19 2014-03-20 Nordson Corporation Dosiereinrichtung für ein Fluid
WO2018206050A1 (fr) * 2017-05-12 2018-11-15 Schaeffler Technologies AG & Co. KG Actionneur électrique de pompe, transmission à variation continue avec actionneur électrique de pompe et procédé de commande pour actionneur électrique de pompe
US11767842B2 (en) 2017-05-12 2023-09-26 Schaeffler Technologies AG & Co. KG Electric pump actuator, stepless transmission with electric pump actuator and control method for an electric pump actuator
CN109854498A (zh) * 2019-03-06 2019-06-07 郑州沃华机械有限公司 一种双驱动轴熔体泵及其控制方法
DE102021206654A1 (de) 2021-06-28 2022-12-29 Zf Friedrichshafen Ag Betätigungsvorrichtung für die Betätigung eines Stellelements einer Stelleinrichtung eines Kraftfahrzeugs
CN114033671A (zh) * 2021-11-09 2022-02-11 中国人民解放军火箭军工程大学 一种圆弧螺旋齿轮泵半接触式端面间隙补偿装置及方法
CN114033671B (zh) * 2021-11-09 2023-08-08 中国人民解放军火箭军工程大学 一种圆弧螺旋齿轮泵半接触式端面间隙补偿装置及方法
EP4448971A4 (fr) * 2021-12-16 2025-11-26 Project Phoenix Llc Vérifications de diagnostic d'une pompe à engrenages dans un système fluidique
CN119177927A (zh) * 2024-11-22 2024-12-24 江苏芬奇工业设备制造有限公司 一种具有进液防堵的自吸齿轮泵

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