WO1994023223A1 - Engrenage planetaire a deux arbres de sortie - Google Patents

Engrenage planetaire a deux arbres de sortie Download PDF

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Publication number
WO1994023223A1
WO1994023223A1 PCT/EP1994/000809 EP9400809W WO9423223A1 WO 1994023223 A1 WO1994023223 A1 WO 1994023223A1 EP 9400809 W EP9400809 W EP 9400809W WO 9423223 A1 WO9423223 A1 WO 9423223A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
stage
output shaft
shaft
speed
Prior art date
Application number
PCT/EP1994/000809
Other languages
German (de)
English (en)
Inventor
Björn FORSBERG
Original Assignee
Cyclo Getriebebau Lorenz Braren 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 Cyclo Getriebebau Lorenz Braren Gmbh filed Critical Cyclo Getriebebau Lorenz Braren Gmbh
Priority to JP6521602A priority Critical patent/JPH07507623A/ja
Priority to KR1019940704250A priority patent/KR950701721A/ko
Priority to EP94911892A priority patent/EP0642637A1/fr
Publication of WO1994023223A1 publication Critical patent/WO1994023223A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
    • B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
    • B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
    • B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
    • B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing
    • B04B2001/2025—Driving control or mechanisms; Arrangement of transmission gearing with drive comprising a planetary gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output

Definitions

  • the invention relates to a planetary gear according to the preamble of claim 1.
  • a screw centrifuge has a drivable drum and a screw conveyor rotating in it.
  • the drum speed must be adjustable, but also the screw speed or the speed difference between the drum and the screw.
  • the drive of this screw centrifuge disclosed in DE-OS 28 11 887 has a drive motor which drives the peripheral wheels of two epicyclic gears via the gear housing, these being coupled to the drum , so that the drum rotates at a speed proportional to the speed of the drive motor.
  • the output shaft of the first epicyclic gear is coupled to the worm and is driven by the output shaft of the second epicyclic gear. If the drive shaft of the second epicyclic gear is held in place, the output shaft of the second epicyclic gear rotates, driven via the peripheral gear of the transmission, according to the translation of the second epicyclic gear between the peripheral gear and the output shaft.
  • the input shaft of the second epicyclic gear from driven by an adjustable control motor, the speed of the output shaft of the second epicyclic gearbox is reduced or increased, depending on the direction of rotation of the input shaft, regardless of the drum speed.
  • the drum speed is changed by changing the speed of the drive motor, the speed difference between the drum and the screw also changes. If the drum is to be operated with a constant speed difference from the screw, the difference in speed must be adjusted accordingly when the drum speed changes with the control motor.
  • the object of the invention is to provide a transmission in which the adjustable speed difference between two output shafts can be kept independent of the speed of the drive.
  • the transmission according to this patent claim follows the basic solution principle of reducing or increasing the speed of that output shaft of the first gear stage, which drives the screw, for example in a screw centrifuge, by means of the second gear stage, the speed of which of an input shaft can be regulated as a control shaft, whereby the amount of the speed change only depends on the speed of this control shaft.
  • the speed difference between the output shafts of the first stage is therefore only dependent on the speed of the control shaft of the second stage. Influencing the speed difference by changing the speed of the Drive means, for example of a drive motor, no longer occurs.
  • the one output shaft of the first gear stage which is designed according to claim 14 as a gear housing with a circumferential wheel, can be driven by a drive means, the input shaft of this first gear stage being driven by an output shaft of the second upstream gear stage.
  • This one output shaft of the first gear stage is therefore directly coupled to the drive means, for example a drive motor, and is thus driven with the speed of the drive motor without further gear ratio.
  • the other output shaft of the first stage is driven by the drive means via the housing and the planetary gear of the first stage, the speed of which in turn depends on the speed of the input shaft and the driven housing with the peripheral wheel of the first stage.
  • this input shaft is driven by one of the two output shafts of the second gear stage.
  • This output shaft in question can be driven by an output element of the second gear stage, which interacts with a sun gear of the control shaft via first planet gears.
  • the differential speed between the first and second output shafts of the first stage could already be regulated via the control shaft of the second stage.
  • the differential speed would not, however, depend solely on the speed of the control shaft, since with a constant speed of the control shaft or the input shaft of the first gear stage but a reduced speed of the drive means and thus the peripheral wheel of the first gear stage, the speed difference between the output shafts naturally changes. This is explained more clearly below using a numerical example in the figure description.
  • This undesirable change in the differential speed is eliminated by a gear device in the form of a further engagement means in the one output shaft of the second gear stage.
  • the aim of this device is to change the speed of the input shaft of the first stage at a constant speed of the control shaft so that the influence of the change in the speed of the drive means is compensated.
  • the one output shaft which according to claim 2 or 4 is designed as a transmission housing of the second stage and is fixedly connected to the output shaft designed as a transmission housing of the first stage, has an engagement means which has a second , Planet gears which are operatively connected to the first planet gears act on the output element of the second stage, the second planet gears being operatively connected to a further input shaft of the second stage via a second sun gear.
  • this solution is realized constructively by the output element being designed as a first peripheral gear, which is non-rotatably connected to the output shaft of the second stage and the engagement means is present in the form of a second peripheral gear in the housing of the second gear stage, which, like that Housing or the peripheral wheel of the first gear stage is driven by the drive means.
  • This interacts with the second sun gear via the second planet gears, the second planet gears having the same web carrier as the first planet gears of the second gear stage. If the second sun gear is now held in place, the rotation of the second peripheral gear causes a rotation of the web carrier, which also carries the first planet gears, which interact with the first peripheral gear, which in turn with the output shaft of the second gear stage and thus connected to the input shaft of the first gear stage.
  • a change in the drive speed at a constant speed of the control shaft leads to a change in the speed of the input shaft of the first gear stage, which exactly compensates for the otherwise undesirable change in the differential speed.
  • the procedure is similar, but in this the output shaft of the second gear stage is connected in a rotationally fixed manner to a first web carrier of the first gear stage, which forms the output element of this stage and which carries the first planet gears, which have a freely rotating peripheral gear and cooperate with the sun gear of the control shaft, a second web carrier, which is connected to the driven gear housing in a rotationally fixed manner, as the engagement means carries the second planet gears, which interact with the peripheral gear and the second sun gear.
  • the second web carrier is driven by the drive means via the housing of the second stage. If the second sun gear is fixed, the peripheral gear is rotated and the speed of the first web carrier, which is connected to the input shaft of the first gear stage, is influenced.
  • the invention also has some advantages over the prior art, particularly when used on screw centrifuges, with regard to the necessary drives of the machine.
  • the main drive of the machine for example an electric motor
  • the main drive of the machine has to exert considerable acceleration forces which result from the inertia of the drum to be overcome, the screw conveyor and the batch in the drum.
  • shear forces can arise within the batch for the case where the drum and screw rotate at different speeds.
  • the control shaft In the epicyclic gear according to the invention, it results that the control shaft must simply be held in order to achieve a zero speed difference in the starting stage.
  • control motor for driving the control shaft is at a standstill in this phase and is only accelerated from standstill to a relatively low number of revolutions in a predetermined direction of rotation only to set the desired differential speed.
  • the control motor can thus be designed to be relatively poor in performance, the individual bearings of the control shaft and the subsequent epicyclic gear also being loaded with only a low number of revolutions.
  • the input shaft of the second stage is fixedly connected to a third circumferential gear which acts on the second, in this case freely rotating sun gear via third planet gears mounted on the web carrier.
  • the speed difference between the output shafts of the first stage can be adjusted independently of the main drive speed by the rotatable further input shaft of the second stage, in this case in the speed ratio 1: 1 between the another input shaft and the output shaft of the second stage. If, on the other hand, the additional input shaft is held and the control shaft of the second stage is used to set the speed difference, the same conditions as in the embodiment according to the invention according to claim 2 are established.
  • the input shaft of the second stage is advantageously designed to be stationary, whereby the manufacturing cost of the transmission is reduced and the desired controllability is nevertheless given. If, however, the second sun gear is designed to be drivable via the input shaft, the differential speed can additionally be varied via this input shaft.
  • the gear housing is used to drive the second peripheral wheel or the second web carrier. This simplifies the construction of the transmission, since the transmission housing, which is present anyway, is simultaneously used to drive the transmission. However, for safety reasons, for example, a stationary gear housing may also be desired, in which case the gear elements to be driven can be driven via conventional drive means, such as gears and shafts, chains or belt drives.
  • the circumferential wheel which is common to the first and second planet gears of the second gear stage has separate raceways for the planet gears. This makes it possible to provide the raceways with different toothings which are optimally adapted to the respective requirements.
  • separate circumferential wheels can also be provided in the second gear stage, which are coupled to one another or at least can be coupled.
  • Both planetary gearboxes and cycloidal gearboxes can be used for the epicyclic gearbox described.
  • a planetary gear stage can also be easily combined with a cycloid gear stage in order to an ideal epicyclic gearbox in terms of gear ratio, load capacity and running properties.
  • FIG. 1 shows the entire epicyclic gear in a first embodiment
  • FIG. 2 shows a sketch of the second gear stage of an epicyclic gear according to FIG. 1,
  • FIG. 3 shows a sketch of the second gear stage of an epicyclic gear according to a second embodiment
  • Figure 4 shows a sketch of the second gear stage of a planetary gear according to a third embodiment
  • FIG. 5 shows a sketch of the second gear stage of an epicyclic gear as a further development of the gear according to FIG. 2.
  • the planetary gear according to FIG. 1 consists of a first cycloid gear stage and a second planetary gear stage.
  • a gear housing 3 of the first gear stage has a toothing 2, via which the gear housing 3 is set in rotation by a drive motor, not shown.
  • the gear housing 3 also serves as the first output shaft of the first gear stage, to which, for example, the drum of a screw centrifuge can be connected.
  • a second output shaft 4 of the first gear stage is formed by the actual output shaft of the epicyclic gear, which is operatively connected to the housing 1 of the first stage via the cycloidal gear.
  • the second gear stage also has a housing 1 which is fixedly connected to the housing 3 of the first stage and together with this forms a common housing body of the epicyclic gear.
  • a control shaft 5 of the second stage which is connected to a control motor, not shown, is located on a side of the common housing body facing away from the second output shaft 4 of the first stage.
  • Another input shaft 6 of the second stage is located on this side, arranged coaxially to the control shaft 5.
  • the gear housing 1, 3 is set in rotation via the toothing 2.
  • An internal ring gear 7 of the cycloid gear stage which rotates with the gear housing 1, 3, is firmly connected to the gear housing 1, 3.
  • the internal ring gear 7 interacts via two cams 8 with two eccentrics 10 which are seated on an output shaft 9 of the second gear stage and in this exemplary embodiment serve as input shafts of the first gear stage.
  • the cams 8 are mounted on bolts 11, which in turn are connected to the second output shaft 4 of the first stage.
  • the input shaft of the first stage is formed by the eccentrics 10 of the cycloid gear.
  • the input shaft of the first gear stage is thus held on the output shaft 9 of the second gear stage, it rotates the drive motor the internal ring gear 7, whereby the cam discs 8 are rotated according to the gear ratio.
  • the rotary movement of the cams 8 in turn is transmitted to the second output shaft 4 of the second stage via the bolts 11. If the output shaft 9 of the second stage is additionally rotated, the speed of the second output shaft 4 of the first stage is reduced or increased, depending on the direction of rotation of the output shaft 9 of the second stage.
  • control shaft 5 is connected in a rotationally fixed manner to a first sun gear 12 which drives first planet gears 13, which are mounted on webs 14 of a freely rotating web carrier 15.
  • the first planet gears 13 cooperate with a peripheral gear 16, which is rotationally connected to the output shaft 9 of the second gear stage or the input shaft of the first gear stage.
  • the further input shaft 6 of the second stage is provided in one piece with a second sun gear 17 which, via second planet gears 18, which cooperate on the same webs 14 as the first planet gears 13, cooperates with a second circumferential gear 19 which rotates with the one driven by the drive motor Gear housing 1 of the second stage is connected.
  • the input shaft 6 of the second stage is fixed so that the differential speed between the two output shafts 3, 4 of the first stage only depends on the speed of the control shaft 5. If there is a gear ratio of 56:55 between the internal ring gear 7 and the output shaft 4 of the first stage, then with the input shaft of the first stage fixed, the output shaft 4 rotates at a speed of the internal ring gear 7 of 4000 rpm with a speed of 4072.7 rpm / min. If there is a gear ratio of 55: 1 between the input shaft and the output shaft 4 of the first stage, then the output shaft 4 rotates at a speed of the input shaft of the first stage of 1600 rpm with a speed of -29.1, with the internal ring gear 7 held tight RPM
  • the result is a speed on the output shaft 4 of 4044 rpm.
  • the speed difference between the output shaft 4, as the actual output shaft of the epicyclic gearbox, and the housing of the first stage as the second output shaft 3 of the epicyclic gearbox, which rotates at the drive speed of 4000 rpm, is therefore 44 rpm.
  • the speed of the input shaft of the first stage must also be changed when the drive speed changes.
  • the speed of the input shaft of the first stage must be reduced to 1200 rpm.
  • This change in speed is realized in the second gear stage.
  • Figure 3 shows the second gear stage according to a second embodiment.
  • the first gear stage is identical to that of the first embodiment.
  • the first gear stage is therefore not described again.
  • the illustrated second embodiment differs from the first embodiment in principle in that the first and second sets of planet gears 113, 118, which act on the first and second sun gear 112, 117 of the second stage, have a common, freely rotating planet gear 120, but in in this case are mounted on separate webs 114, 121.
  • the first planet gears 113 are mounted on first webs 114, which are connected to the output shaft 109 of the second stage via a first web carrier 115.
  • Second lands 121 are connected to the second stage gear housing 101 which is driven by the drive motor.
  • the rotation of the gear housing 101 does not influence the speed of the web carrier, but rather the speed of the common freely rotating planetary wheel 120;
  • the speed of the first webs 114 and thus of the output shaft 109 of the second stage is in turn influenced by influencing the speed of the planet wheel 120.
  • FIG. 4 shows the second gear stage of a third embodiment, which corresponds to the second embodiment according to FIG. 3 in terms of the gear structure.
  • the difference to the second embodiment is that instead a planetary gear, a cycloid gear is used for the second gear stage.
  • first double eccentric 212 instead of the first sun gear, there is a first double eccentric 212 and instead of the second sun gear a second double eccentric 217.
  • the double eccentrics 212, 217 interact with cams 213, 218 which replace the planet gears.
  • the cam disks 213 interacting with the first double eccentric 213 are mounted on first bolts 214 which replace the first webs and are in turn firmly connected to the output shaft 209 of the second stage.
  • the second cams 218 are mounted on second bolts 221 which, like the second webs of the second embodiment, are fixedly connected to the gear housing 201 which is driven by the drive motor.
  • the mode of operation of this gear stage is therefore identical to that of the second embodiment.
  • FIG. 5 shows a further exemplary embodiment of the second gear stage of the epicyclic gear according to the invention.
  • the output shaft 9 of the second stage is formed in one piece with a first circumferential wheel 16, which acts on planet wheels 13 mounted on freely movable web carriers 14, 15 on a sun gear 12, which is integrally connected to the control shaft 5 of the second stage.
  • Second planet gears 18 are mounted on the web carriers, which roll on a circumferential gear 19 fastened to the gear housing 1 of the second stage and mesh with a second, freely rotating sun gear 17.
  • This second sun gear 17 is mounted on the control shaft 5 of the second stage according to FIG. 5 and has a further toothed raceway in which the teeth of third planet gears 20 engage.
  • the third planet gears are also mounted on the web carriers 14, 15 and are dimensioned in accordance with the first and second planet gears.
  • the third planet gears 20 in turn roll on a third peripheral gear 21 which is fixedly connected to a further input shaft 6 of the second stage and has the same rolling diameter as the first peripheral gear 16 of the second stage.
  • the control shaft 5 and the further input shaft 6 are arranged coaxially as in the previous exemplary embodiments, the input shaft 6 being designed as a hollow shaft in which the control shaft 5 is rotatably mounted relative to the input shaft 6.
  • the speed difference between the first and second output shafts 3, 4 of the first gear stage can be set exclusively on the basis of the speed of the control shaft 5, a change in the control shaft speed a change in the speed difference in question corresponds to the transmission ratio of the second gear stage.
  • the control shaft 5 of the second stage is now held in the exemplary embodiment according to FIG. 5 and the speed difference change is carried out on the basis of the further input shaft 6, there are different transmission ratios between the input shaft 6 and the output shaft 9 of the second stage, which are fixed to the input shaft of the first stage connected is.
  • the third peripheral gear 21, which is connected to the input shaft 6, is designed like the first peripheral gear 16, which is connected to the output shaft 9 of the second gear stage.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)

Abstract

Un engrenage planétaire comprend deux arbres de sortie (3, 4) qui tournent à des vitesses de rotation diverses. La vitesse de rotation du deuxième arbre de sortie (4) peut être réduite ou accrue au moyen d'un deuxième étage de l'engrenage dont l'arbre moteur (5) est un arbre de réglage dont la vitesse de rotation est réglable. La différence entre les vitesses de rotation des deux arbres de sortie (3, 4) dépend uniquement de la vitesse de rotation de l'arbre de réglage (5) et non de la vitesse de rotation d'entraînement, de sorte que la différence entre les vitesses de rotation des deux arbres de sortie (3, 4) reste automatiquement constante même lorsque la vitesse de rotation d'entraînement varie, sans aucun changement de la vitesse de rotation de l'arbre de réglage (5).
PCT/EP1994/000809 1993-03-29 1994-03-15 Engrenage planetaire a deux arbres de sortie WO1994023223A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP6521602A JPH07507623A (ja) 1993-03-29 1994-03-15 二本の被駆動軸を備えた遊星伝動装置
KR1019940704250A KR950701721A (ko) 1993-03-29 1994-03-15 두개의 피동축을 가진 유성 기어 장치
EP94911892A EP0642637A1 (fr) 1993-03-29 1994-03-15 Engrenage planetaire a deux arbres de sortie

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4310158.5 1993-03-29
DE4310158A DE4310158C1 (de) 1993-03-29 1993-03-29 Umlaufrädergetriebe mit zwei Abtriebswellen

Publications (1)

Publication Number Publication Date
WO1994023223A1 true WO1994023223A1 (fr) 1994-10-13

Family

ID=6484135

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1994/000809 WO1994023223A1 (fr) 1993-03-29 1994-03-15 Engrenage planetaire a deux arbres de sortie

Country Status (7)

Country Link
EP (1) EP0642637A1 (fr)
JP (1) JPH07507623A (fr)
KR (1) KR950701721A (fr)
CN (1) CN1108458A (fr)
CA (1) CA2136327A1 (fr)
DE (1) DE4310158C1 (fr)
WO (1) WO1994023223A1 (fr)

Cited By (8)

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Publication number Priority date Publication date Assignee Title
EP0798046A1 (fr) * 1996-03-29 1997-10-01 GUINARD CENTRIFUGATION Société dite : Décanteuse centrifuge à module redex
WO1998013626A1 (fr) * 1996-09-23 1998-04-02 Scandrive I Hallstahammar Ab Dispositif de reglage permettant des changements d'angle de rotation entre deux elements rotatifs
WO2002081094A1 (fr) * 2001-04-04 2002-10-17 Centriquip Limited Boite de vitesses pour centrifugeuse telle qu'une centrifugeuse de decantation
US6548454B1 (en) 1997-08-29 2003-04-15 Nsk Ltd. Rolling apparatus containing a liquid fluorinated polymer oil and thickening agent
DE102006028804A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge mit Antriebsvorrichtung
DE102006028803A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge
EP3301323A1 (fr) * 2016-09-29 2018-04-04 Schunk GmbH & Co. KG Spann- und Greiftechnik Train d'engrenage de type roue cycloïdale
EP3301324A1 (fr) * 2016-09-29 2018-04-04 Schunk GmbH & Co. KG Spann- und Greiftechnik Train d'engrenage de type roue cycloïdale

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DE19511749A1 (de) * 1995-03-30 1995-10-05 Horst Wandelt Mechanischer Antrieb
EP2200862B1 (fr) * 2007-10-23 2015-02-25 Johnson Controls Components GmbH & Co. KG Étage d'engrenage
CN101956816A (zh) * 2009-07-14 2011-01-26 金昱诚 无段变速器控制装置
CN104074930B (zh) * 2014-07-17 2016-08-31 天津职业技术师范大学 一种同轴单输入同侧双输出摆线减速器
CN104455234B (zh) * 2014-12-02 2016-08-24 孙建宁 一种多动力混合输入双/单输出的无级变速箱

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GB1131579A (en) * 1967-02-28 1968-10-23 Hitachi Shipbuilding Eng Co Improvements relating to centrifugal separating machines with differential drives
FR2070485A5 (en) * 1969-12-05 1971-09-10 Defontenay Paul Control system for centrifuge - to produce differential rotation
DE2811887A1 (de) * 1978-03-18 1979-09-27 Westfalia Separator Ag Antrieb fuer eine kontinuierlich arbeitende schneckenzentrifuge
FR2610058A1 (fr) * 1987-01-26 1988-07-29 Maag France Dispositif de transmission de puissance avec reduction de vitesse entre un ensemble tournant et un arbre monte coaxial a l'interieur de celui-ci
WO1991010846A1 (fr) * 1990-01-08 1991-07-25 Alfa-Laval Separation, Inc. Transmissions pour centrifugeuses

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FR2177242A5 (fr) * 1972-03-21 1973-11-02 Holweg Const Mec
FR2247641A1 (en) * 1973-10-16 1975-05-09 Weingarten Ag Maschf Gear drive with output to input phase control - for machine tools can operate when machine is running
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Publication number Priority date Publication date Assignee Title
GB1131579A (en) * 1967-02-28 1968-10-23 Hitachi Shipbuilding Eng Co Improvements relating to centrifugal separating machines with differential drives
FR2070485A5 (en) * 1969-12-05 1971-09-10 Defontenay Paul Control system for centrifuge - to produce differential rotation
DE2811887A1 (de) * 1978-03-18 1979-09-27 Westfalia Separator Ag Antrieb fuer eine kontinuierlich arbeitende schneckenzentrifuge
FR2610058A1 (fr) * 1987-01-26 1988-07-29 Maag France Dispositif de transmission de puissance avec reduction de vitesse entre un ensemble tournant et un arbre monte coaxial a l'interieur de celui-ci
WO1991010846A1 (fr) * 1990-01-08 1991-07-25 Alfa-Laval Separation, Inc. Transmissions pour centrifugeuses

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5941810A (en) * 1996-03-29 1999-08-24 Guinard Centrifugation Centrifugal separator having a planetary hub
FR2746675A1 (fr) * 1996-03-29 1997-10-03 Guinard Centrifugation Decanteuse centrifuge a module redex
EP0798046A1 (fr) * 1996-03-29 1997-10-01 GUINARD CENTRIFUGATION Société dite : Décanteuse centrifuge à module redex
GB2333343B (en) * 1996-09-23 2000-10-11 Scandrive Hallstahammar Ab Adjusting device for providing changes of the angle of rotation between two rotary elements
GB2333343A (en) * 1996-09-23 1999-07-21 Scandrive Hallstahammar Ab Ajusting device for providing changes of the angle of rotation between two rotary elements
US6014907A (en) * 1996-09-23 2000-01-18 Scandrive Control Ab Adjusting device for providing changes of the angle of rotation between two rotary elements
WO1998013626A1 (fr) * 1996-09-23 1998-04-02 Scandrive I Hallstahammar Ab Dispositif de reglage permettant des changements d'angle de rotation entre deux elements rotatifs
US6548454B1 (en) 1997-08-29 2003-04-15 Nsk Ltd. Rolling apparatus containing a liquid fluorinated polymer oil and thickening agent
WO2002081094A1 (fr) * 2001-04-04 2002-10-17 Centriquip Limited Boite de vitesses pour centrifugeuse telle qu'une centrifugeuse de decantation
DE102006028804A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge mit Antriebsvorrichtung
DE102006028803A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge
US7883457B2 (en) 2006-06-23 2011-02-08 Westfalia Separator Gmbh Helical conveyor centrifuge having a planetary gear drive device
EP3301323A1 (fr) * 2016-09-29 2018-04-04 Schunk GmbH & Co. KG Spann- und Greiftechnik Train d'engrenage de type roue cycloïdale
EP3301324A1 (fr) * 2016-09-29 2018-04-04 Schunk GmbH & Co. KG Spann- und Greiftechnik Train d'engrenage de type roue cycloïdale

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EP0642637A1 (fr) 1995-03-15
KR950701721A (ko) 1995-04-28
CN1108458A (zh) 1995-09-13
CA2136327A1 (fr) 1994-10-13
JPH07507623A (ja) 1995-08-24
DE4310158C1 (de) 1994-12-22

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