EP1252444B1 - Systeme d'entrainement de pompe a vis - Google Patents

Systeme d'entrainement de pompe a vis Download PDF

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Publication number
EP1252444B1
EP1252444B1 EP01909614A EP01909614A EP1252444B1 EP 1252444 B1 EP1252444 B1 EP 1252444B1 EP 01909614 A EP01909614 A EP 01909614A EP 01909614 A EP01909614 A EP 01909614A EP 1252444 B1 EP1252444 B1 EP 1252444B1
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EP
European Patent Office
Prior art keywords
rotors
gear
screw pump
gearwheels
gears
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.)
Expired - Lifetime
Application number
EP01909614A
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German (de)
English (en)
Other versions
EP1252444A1 (fr
Inventor
Ralf Steffens
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Individual
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Individual
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Filing date
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Publication of EP1252444A1 publication Critical patent/EP1252444A1/fr
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Publication of EP1252444B1 publication Critical patent/EP1252444B1/fr
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Expired - Lifetime 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
    • 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
    • F04C18/12—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 other than internal-axis type
    • F04C18/14—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 other than internal-axis type with toothed rotary pistons
    • F04C18/16—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 other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • 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
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19074—Single drive plural driven
    • Y10T74/19079—Parallel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19074—Single drive plural driven
    • Y10T74/19079—Parallel
    • Y10T74/19088—Bevel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19647—Parallel axes or shafts

Definitions

  • the invention relates to a dry-compressing screw pump with two externally toothed and counter-rotating Verdrängerspindelrotoren for conveying and compressing gases, wherein a gear for the drive and the synchronization of the rotors is arranged on each of the rotors.
  • Drying pumps are becoming increasingly important, especially in vacuum technology, because increasing obligations in environmental regulations and rising operating and disposal costs and increased demands on the purity of the pumped liquid, the known wet-running vacuum systems such as liquid ring machines and rotary vane pumps are increasingly replaced by dry-compressing pumps.
  • These dry compacting machines include screw pumps, claw pumps, diaphragm pumps, piston pumps, scroll machines and Roots pumps.
  • these machines have in common that they can not meet today's requirements in terms of reliability and robustness and size and weight at a low price level yet satisfactory.
  • the desired spindle rotor speeds are modern Spindle vacuum pumps, so screw pumps, usually well above the rated speed of the asynchronous motors usually used for driving because of their robustness, so that either a frequency converter or an upstream gear transmission speed increase is required.
  • screw pumps usually well above the rated speed of the asynchronous motors usually used for driving because of their robustness, so that either a frequency converter or an upstream gear transmission speed increase is required.
  • a non-contact rolling of the two positive displacement spindles in the pump working space is indispensable.
  • the initially defined screw pump is characterized in that the toothing diameter of the two gears for the two Verdrängerspindelrotoren - also called “rotors" below - smaller than the axial distance of the two rotors that a driving gear in the two gears engages the rotors and meshes with these and that this toothing of the driving gear with the driven gears is executed kronenradä Inc.
  • the peripheral speeds of the gears for the rotors can be significantly reduced and the specific tooth flank load can be increased, so that the noise level and the dynamic factor are reduced. Furthermore, the desired speed increase from the drive gear to the spindle rotors via the diameter and number-of-teeth ratios of this drive gear to the gears of the rotors can be achieved very easily.
  • the solution according to the invention makes it possible that the motor axis can be arranged in the same direction as the two spindle rotor axes or at right angles thereto.
  • both the space of the entire screw pump with motor as well as the cooling is favored by the engine air flow and can be adapted to the respective structural conditions.
  • the driving gear is larger than the two spindle rotor fixed gears.
  • the tooth diameter of the two gears for the rotors is smaller than the axial distance of the two rotors, so that the driving gear engages in these two gears and can obtain a corresponding size.
  • the rotatably mounted on the two Verdrängerspindel pump rotors gears can be acted upon by the driving gear with a larger by a factor of the desired speed increase number of teeth due to their smaller diameter relative to the axial distance, so that the two spindle rotors in opposite directions with increased speed and synchronously driven synchronized become.
  • the screw pump can be operated at a higher speed, whereby the compressibility, the degree of delivery and thus the volumetric efficiency are increased.
  • a more than proportionally higher pumping speed is achieved from the same machine size, so that the specific costs - based on the volume flow - decrease accordingly.
  • the factor for increasing the speed can be the already mentioned value of 1.5 to 4 or possibly even outside of these limits compared to the standard speeds for direct drive.
  • the per se known speed increase can be avoided by means of frequency converters, which are generally relatively expensive.
  • the driving gear may be mounted directly on the shaft of a drive motor. This also contributes to the simplification of the entire drive.
  • a lubricant can be supplied on the inside of the driving gear. Due to the inventive arrangement and assignment of the gears so the lubrication situation can be significantly cheaper, in which on the inner diameter of the toothed side of the driving, in particular crown gear-like gear lubricant is brought, which is distributed by the centrifugal force in a favorable manner on the tooth flank interventions, thereby also another Noise reduction is enabled.
  • the driving gear and / or the spindle rotor fixed gears may be formed kronenradä Republic.
  • the crown wheel-like toothing or design of the gear wheel or gears has already been mentioned. This can therefore relate either to the driving gear or the fixedly connected to the spindle rotor gears or to all gears.
  • the common attack of the driving gear on the two gears of the rotors can be realized as space-saving.
  • An expedient embodiment may be that the driving gear has one or two crown gears arranged similar toothed wheels, which mesh with designed as spur gears rotor-fixed gears.
  • the driving gear has one or two crown gears arranged similar toothed wheels, which mesh with designed as spur gears rotor-fixed gears.
  • crown gear-like driving gear as internally and externally toothed ring gear on its internal teeth designed as a spur gear rotorfestes gear of a rotor shaft and on its outer toothing the other, designed as a spur gear rotor-fixed gear of the second rotor shaft in opposite directions synchronized and drives at increased speed.
  • the crown gear-like drive gear can therefore also be represented or considered as internally and externally toothed ring gear, which in each case synchronizes a classic spur gear in the opposite direction with its two gears and drives it at an increased speed.
  • such a ring gear can be produced as a laminated core.
  • a further embodiment of the invention can provide that the toothings of the crown gear-like gears are each arranged on a cone and the cone angle of the provided on the driving gear two gears relative to a radial plane between these two gears is relatively flat or pointed.
  • the rotor-fixed gears are not spur gears, but bevel gears with a relatively acute cone angle, which may improve the engagement conditions of the teeth.
  • gears connected to the rotors are formed as crown wheels and the drive gear as a spur gear.
  • This spur gear can then attack simultaneously, for example, on the mutually facing areas of the crown gear-like sprockets, wherein the teeth on the driving spur gear but also interrupted by an annular groove and may be limited to the meshing area.
  • the driving gear has two crown gear-like gears - even in a somewhat conical arrangement - it is advantageously possible that the axis of rotation of the driving gear is arranged perpendicular to the axes of rotation of the driven gears and rotors and that in particular two sides facing away from each other each having a sprocket driving gear engages in the space between the two arranged in a common plane driven gears and meshes with these gears.
  • the toothing diameters of these two gears 3 and 4 for the two Verdrängerspindelrotoren 1 and 2 are smaller in all embodiments than the axial distance A of the two rotors 1 and 2.
  • a driving gear 5 is provided in all embodiments, which with the two gears 3 and 4 the rotors 1 and 2 meshes or engages with its teeth in the toothing.
  • a crown wheel-like toothing or design of the gear wheel or gears to be explained in more detail below is provided.
  • the driving gear 5 is independent of its respective shape larger than the two spindle rotor fixed gears 3 and 4, so that on the one hand by the matching number of teeth and size of the driven gears 3 and 4 a synchronization the two rotors 1 and 2 and on the other hand by the larger dimension of the driving gear 5 with a correspondingly higher number of teeth an increase in the rotational speed of the driven gears 3 and 4 compared to the rotational speed of the driving gear 5 results.
  • the driving gear 5 is expediently mounted directly on the shaft 6 of a drive motor, not shown.
  • a lubricant may be supplied to the inside of the driving gear 5 for lubrication of the teeth interventions, so that it passes through the centrifugal force practically by itself to the teeth and engagement points of these teeth.
  • driving gear 5 and the driven gears 3 and 4 have a crown gear similar teeth together. This can be designed differently according to the various embodiments or defined within this description.
  • the driving gear 5 and the spindle rotor fixed, ie driven gears 3 and 4 are each kronenradä Republic or formed as crown wheels.
  • the shaft 6 of the drive motor can be arranged parallel to the rotor axes.
  • the driving gear 5 may also have a or according to Figure 9 to 11 two parallel, but directed to opposite sides crown gear arranged sprockets 7, which mesh with trained as spur gears rotor-fixed gears 3 and 4, as clearly seen in Figure 9 and 10 ,
  • FIGS. 9 and 10 show similar embodiments, each with two crown-wheel-like sprockets 7, which mesh with rotor-toothed gears 3 and 4 designed as spur gears.
  • Figure 10 with respect to Figure 9, the advantageous particularity that the two sprockets 7 of the driving gear 5 relative to each other in the axial and / or rotational direction are adjustable and fixable.
  • the one ring gear is arranged on a ring 10 which fits on a shoulder 11 of the driving gear 5 and this paragraph 11 adds to a gear 5 of Figure 9, and that between the paragraph 11 and the ring 10 a Ring disc 12 can be inserted in the axial direction, so that the distance between the two sprockets 7 in the axial direction, depending on the thickness or number of annular discs 12 can be adjusted.
  • the attachment of the ring 10 and thus also the washer ring 12 can be done by means of screws not shown.
  • each toothing has a torsional backlash around which one toothed wheel can be rotated relative to the other until it comes from the abutment on the tooth flank side to the abutment on the trailing edge side.
  • This backlash of a gearing is technically unavoidable.
  • this rotational backlash can be set and optimized targeted.
  • each of the teeth on the two driven gears 3 and 4 receives a set preselected rotational backlash, this possibility also exists in the embodiment of Figure 11 and optionally Figure 8.
  • the transmission ratio between the driving gear 5 and the rotor fixed gears 3 and 4 are particularly easy to change by the same sprockets 7, the gears 3 and 4 are replaced or replaced without the axis positions of the drive and rotor pair must be adjusted. Only the distance between the two sprockets 7 on the drive wheel 5 is about the embodiment according to Figure 10 still adapt. Thus, the rotor speed for different applications can be changed with little effort by changing the simple spur gears 3 and 4 while adjusting the distance of the sprockets 7.
  • the annular disc 12 can also be made elastic.
  • the crown gear-like drive gear 5 can be represented or defined as internally and externally toothed ring gear according to Figure 7, which is formed on its internal teeth formed as a spur gear rotor fixed gear 3 of a rotor shaft or a rotor 1 and its outer teeth the other, also designed as a spur gear rotor-fixed gear 4 of the second rotor shaft or the second rotor 2 synchronized in opposite directions and drives due to the different diameter with increased speed.
  • the driving crown gear-like gear forming sprocket can be produced as a laminated core.
  • Figure 8 shows an embodiment in which connected to the rotors 1 and 2 gears 3 and 4 as in the embodiments of Figure 1 to 6 as crown wheels, the drive gear 5 but is designed as a spur gear, the teeth not over the entire axial extent this drive gear 5 rich, but are divided into two spaced sprockets 7.
  • the drive shaft 6 extends at right angles to the axes of the rotors 1 and 2.
  • FIG. 11 shows an embodiment in which the toothings of the gearwheels 3, 4 and 5, which in this case are likewise considered as crown gear wheels, are each arranged on a cone, analogously to the exemplary embodiment according to FIG. 9, two toothed rings or toothings facing away from one another on the driving gearwheel 5 are whose cone angle relative to a arranged between these sprockets or gears radial diameter plane 8 is relatively flat or pointed.
  • the crown wheel similarity of the two sprockets of this driving gear 5 would be even more clearly seen if the frontal, in the radial direction opposite the sprockets farther inferior depressions 9 would be slightly lower than in the illustration of Figure 10.
  • inventions according to Figure 9 to 11 have in common that the two sides facing away from each other on a sprocket 7 having driving gear 5 in the space between the two arranged in a common plane driven gears 3 and 4 meshes and with these, which is either a Enlargement of the diameter of the driving gear 5 with the same space requirement or a reduction of the construction allowed.
  • the screw pump 10 is designed as a two-shaft displacement machine and has two externally toothed, oppositely rotating Verdrängerspindelrotoren 1 and 2.
  • these rotors 1 and 2 with simultaneous synchronization and speed increase kronenradähnliche gears 3 and 4 are arranged in a matching plane to the two oppositely rotating rotors 1 and 2 or rotor spindles, in which a larger kronenradähnliches Drive gear 5 engages in such a way that the two spindle rotors 1 and 2 are driven in opposite directions with increased speed, wherein Kronenrad similarity also includes an internally and externally toothed ring gear in conjunction with spur gears or bevel gears and the possibility that only the drive gear 5 or only the driven gears. 3 and 4 are crown-like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)

Claims (12)

  1. Pompe à vis à compression sèche (10) avec deux rotors hélicoïdaux à déplacement (1, 2) pourvus d'une denture externe et tournant dans des sens opposés et destinés à refouler et à comprimer des gaz, une roue dentée (3, 4) destinée à entraîner et à synchroniser les rotors (1, 2) étant disposée sur chacun des rotors (1, 2), caractérisée en ce que le diamètre de la denture des deux roues dentées (3, 4) pour les deux rotors hélicoïdaux à déplacement (1, 2) est inférieur à l'entraxe (A) des deux rotors (1, 2), qu'une roue dentée (5) menante s'engage dans les deux roues dentées (3, 4) des rotors (1, 2) et que l'engrènement de cette roue dentée (5) menante dans les roues dentées (3, 4) menées est réalisé à la manière de roues de champ.
  2. Pompe à vis selon la revendication 1, caractérisée en ce que la roue dentée (5) menante est plus grande que les deux roues dentées (3, 4) solidaires du rotor hélicoïdal.
  3. Pompe à vis selon la revendication 1 ou 2, caractérisée en ce que la roue dentée (5) menante est fixée directement sur l'arbre (6) d'un moteur d'entraînement.
  4. Pompe à vis selon l'une quelconque des revendications 1 à 3, caractérisée en ce que, pour lubrifier l'engrenage, un lubrifiant est apte à être acheminé sur la face interne de la roue dentée (5) menante.
  5. Pompe à vis selon l'une quelconque des revendications 1 à 4, caractérisée en ce que la roue dentée (5) menante et/ou les roues dentées (3, 4) solidaires du rotor hélicoïdal sont conformées en forme de roue de champ.
  6. Pompe à vis selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la roue dentée (5) menante comporte une ou deux couronnes dentées (7) disposées à la manière de roues de champ, ces couronnes dentées engrenant dans des roues dentées (3, 4) solidaires du rotor et conformées sous forme de roues droites.
  7. Pompe à vis à compression sèche selon l'une quelconque des revendications 1 à 5, caractérisée en ce que, en sa qualité de couronne dentée à denture interne et externe, la roue dentée (5) menante ressemblant à une roue de champ synchronise dans des sens opposés et entraîne à vitesse augmentée par sa denture interne une roue dentée (3) solidaire du rotor conformée en forme de roue droite de l'arbre d'un des rotors et par sa denture externe l'autre roue dentée (4) solidaire du rotor conformée en forme de roue droite de l'arbre du deuxième rotor.
  8. Pompe à vis selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les dentures des roues dentées (3, 4, 5) ressemblant à des roues de champ sont disposées chacune sur un cône et que l'angle au sommet des deux dentures prévues sur la roue dentée (5) menante est relativement plat ou aigu par rapport à un plan radial (8) entre ces deux dentures.
  9. Pompe à vis selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les roues dentées (3, 4) reliées aux rotors (1, 2) sont conformées en forme de roues de champ et que la roue dentée menante (5) est conformée en forme de roue droite.
  10. Pompe à vis selon l'une quelconque des revendications précédentes, caractérisée en ce que l'axe de rotation (6) de la roue dentée (5) menante est disposée perpendiculaire aux axes de rotation des roues dentées (3, 4) menées et des rotors (1, 2) et que la roue dentée (5) menante comportant notamment sur chacune de deux faces détournées l'une de l'autre une couronne dentée respective s'engage dans l'espace ménagé entre les deux roues dentées (3, 4) menées disposées dans un même plan et engrène dans ces roues dentées.
  11. Pompe à vis selon l'une quelconque des revendications 6 à 10, caractérisée en ce que les deux couronnes dentées (7) de la roue dentée (5) menante sont aptes à être réglées et arrêtées l'une par rapport à l'autre suivant la direction axiale et/ou dans le sens de rotation.
  12. Pompe à vis selon l'une quelconque des revendications 6 à 11, caractérisée en ce que l'une des couronnes dentées (7) est disposée sur un anneau (10) épousant la forme d'un épaulement (11) de la roue dentée (5) menante et qu'au moins une rondelle (12) est apte à être placée entre l'épaulement (11) et l'anneau (10).
EP01909614A 2000-02-02 2001-01-12 Systeme d'entrainement de pompe a vis Expired - Lifetime EP1252444B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10004373 2000-02-02
DE10004373A DE10004373B4 (de) 2000-02-02 2000-02-02 Trockenverdichtende Schraubenpumpe
PCT/EP2001/000320 WO2001057401A1 (fr) 2000-02-02 2001-01-12 Systeme d'entrainement de pompe a vis

Publications (2)

Publication Number Publication Date
EP1252444A1 EP1252444A1 (fr) 2002-10-30
EP1252444B1 true EP1252444B1 (fr) 2007-08-15

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ID=7629466

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01909614A Expired - Lifetime EP1252444B1 (fr) 2000-02-02 2001-01-12 Systeme d'entrainement de pompe a vis

Country Status (10)

Country Link
US (1) US6666672B1 (fr)
EP (1) EP1252444B1 (fr)
JP (1) JP2003521637A (fr)
KR (1) KR100749729B1 (fr)
AT (1) ATE370333T1 (fr)
AU (1) AU3729301A (fr)
CA (1) CA2398263A1 (fr)
DE (2) DE10004373B4 (fr)
ES (1) ES2296732T3 (fr)
WO (1) WO2001057401A1 (fr)

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WO2008003657A1 (fr) * 2006-07-03 2008-01-10 Ralf Steffens Entraînement pour une pompe à broche hélicoïdale
US20080063554A1 (en) * 2006-09-08 2008-03-13 Gifford Thomas K Precision flow gear pump
DE102008019449A1 (de) 2007-04-18 2008-10-23 Alfavac Gmbh Lagerung für eine Schraubenspindelpumpe
WO2010006663A1 (fr) 2008-07-18 2010-01-21 Ralf Steffens Refroidissement d'une pompe à vis
WO2011101064A2 (fr) 2010-02-18 2011-08-25 Ralf Steffens Entraînement pour un compresseur à broches
WO2012112565A2 (fr) 2011-02-15 2012-08-23 Rotation Medical, Inc. Procédés et appareil pour la distribution et le positionnement de matériaux en feuille
DE102013211185A1 (de) 2012-06-15 2013-12-19 Ralf Steffens Spindelverdichter-Gehäuse
DE102013021902B4 (de) * 2013-12-26 2017-06-14 HENKE Property UG (haftungsbeschränkt) Schmelzepumpe zum Aufbau von Druck zwecks Durchdrücken von Kunststoffschmelze durch ein Werkzeug
CA2945821C (fr) 2014-05-09 2018-09-04 Rotation Medical, Inc. Systeme de pose d'implant medical pour un implant de type feuille
JP2018515196A (ja) 2015-05-06 2018-06-14 ローテーション メディカル インコーポレイテッドＲｏｔａｔｉｏｎ Ｍｅｄｉｃａｌ，Ｉｎｃ． 医療用インプラント搬送システムおよび関連する方法
FR3038954B1 (fr) * 2015-07-16 2017-07-21 Airbus Helicopters Boite de transmission de puissance et aeronef
US10314689B2 (en) 2015-12-31 2019-06-11 Rotation Medical, Inc. Medical implant delivery system and related methods
CN110225726A (zh) 2017-12-07 2019-09-10 罗特迅医疗有限公司 医疗植入物输送系统和相关方法
DE102018210922A1 (de) * 2018-07-03 2020-01-09 Leybold Gmbh Zwei- oder Mehrwellen-Vakuumpumpe
WO2021022352A1 (fr) * 2019-08-02 2021-02-11 Rt Hamilton And Associates Limited Pompe à vis à vide sèche refroidie

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Also Published As

Publication number Publication date
AU3729301A (en) 2001-08-14
ATE370333T1 (de) 2007-09-15
DE10004373A1 (de) 2001-08-09
EP1252444A1 (fr) 2002-10-30
DE10004373B4 (de) 2007-12-20
WO2001057401A1 (fr) 2001-08-09
ES2296732T3 (es) 2008-05-01
DE50112863D1 (de) 2007-09-27
KR20020071961A (ko) 2002-09-13
CA2398263A1 (fr) 2001-08-09
US6666672B1 (en) 2003-12-23
JP2003521637A (ja) 2003-07-15
KR100749729B1 (ko) 2007-08-17

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