EP0793038A2 - Transmission à engrenages droits pour l'entraînement d'un rouleau - Google Patents

Transmission à engrenages droits pour l'entraînement d'un rouleau Download PDF

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Publication number
EP0793038A2
EP0793038A2 EP96120229A EP96120229A EP0793038A2 EP 0793038 A2 EP0793038 A2 EP 0793038A2 EP 96120229 A EP96120229 A EP 96120229A EP 96120229 A EP96120229 A EP 96120229A EP 0793038 A2 EP0793038 A2 EP 0793038A2
Authority
EP
European Patent Office
Prior art keywords
pinion
bearing
roller
drive shaft
helical gear
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
EP96120229A
Other languages
German (de)
English (en)
Other versions
EP0793038B1 (fr
EP0793038A3 (fr
Inventor
Joachim Dr. Grabscheid
Christian Schiel
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.)
Voith Patent GmbH
Original Assignee
Voith Sulzer Papiermaschinen 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 Voith Sulzer Papiermaschinen GmbH filed Critical Voith Sulzer Papiermaschinen GmbH
Publication of EP0793038A2 publication Critical patent/EP0793038A2/fr
Publication of EP0793038A3 publication Critical patent/EP0793038A3/fr
Application granted granted Critical
Publication of EP0793038B1 publication Critical patent/EP0793038B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/0006—Driving arrangements
    • D21G1/0013—Driving arrangements for controlled deflection rolls

Definitions

  • the present invention relates to a spur gear for driving a roller, one end of which is mounted on a support bracket via a self-aligning bearing, with an external toothed ring rigidly connected to one end of the roller, a drivable pinion which meshes with the external toothed ring and which is designed as a hollow body and is mounted on a pendulum bearing on the support bracket, a drive shaft arranged laterally to the pinion, which is rotatably coupled at one end to the pinion, and an additional support bearing for the pinion, which is also located on the support bracket and is located next to the pinion bracket and which supports a radial to enable pinion tilting Game.
  • Such a spur gear is known from DE 38 04 225 A1.
  • Rolls of this type are, for example, deflection adjustment rolls or suction rolls such as those used in the paper industry, for example in dewatering presses, smoothing units and the like. be applied.
  • Such rollers have a roller shell which is rotatable about a fixed support.
  • the roller shell bends under load, the external toothed ring, which is firmly connected to the roller shell, inclines somewhat together with the end region of the roller shell relative to the non-inclinable gear housing, which also serves as a support stand for the entire roller.
  • the pinion is therefore spherical.
  • the tooth flanks consequently lie against one another along a common flank line according to the normal force to be transmitted and the position of the pinion with respect to the direction of deflection of the roll shell can be chosen arbitrarily.
  • a degree of freedom of the pinion must also be restricted, namely the tilting of the pinion about the central axis of the pinion parallel to the line of engagement due to the offset of the pinion axes and the shaft driving the pinion, which generates a frictional moment.
  • the crowning of the tooth flanks has the advantage of having an oblique load distribution that limits the transmissible torque mitigate high edge pressure. However, it may only be small, otherwise the transferable power will decrease again. The radial play is therefore chosen to be small.
  • the pinion tilting that occurs during operation of the roller causes a comparatively large additional deflection of the coupling between the drive shaft and pinion.
  • the drive shaft is designed as a clutch shaft between a drive sleeve driven by the roller drive and the pinion, this also results in a relatively large difference in the flexion angle of the clutch between the clutch shaft and pinion on the one hand and the clutch shaft and drive sleeve on the other.
  • the invention has for its object to develop a spur gear of the type mentioned so that the problems mentioned are overcome.
  • the load distribution on the tooth flanks of the pinion should be improved and the flexion angle between the drive shaft and clutch should be reduced in order to make the force distribution more uniform over the tooth width and to increase the transferable power.
  • the arrangement of the additional support bearing inside the drive shaft eliminates the corresponding space requirement in the pinion, so that the drive shaft can be arranged closer to the pinion pendulum bearing and the coupling between the drive shaft and pinion has a smaller distance from the center plane of the pinion pendulum bearing. The reaction moments and forces are therefore lower and there is a more even load distribution on the tooth flanks of the pinion.
  • the coupling between the drive shaft and the pinion is preferably arranged directly adjacent to the pinion pendulum bearing.
  • Another advantage of the spur gear according to the invention is that the reaction forces occurring at the coupling between the drive shaft and pinion are at least partially absorbed and compensated for by the additional support bearing arranged in the drive shaft. This also makes the load distribution on the tooth flanks of the pinion even. Due to the small distance of the coupling between the drive shaft and the pinion from the pinion pendulum bearing, the deflection of the coupling and thus also the difference between the deflection of the coupling between a drive shaft designed as a coupling shaft and the pinion on the one hand and the coupling shaft and the drive sleeve driven by the roller drive are reduced on the other hand.
  • the two couplings can be designed for higher loads with the same size.
  • the pinion drive shaft can be coupled directly to the pinion, so that the flange existing in the known spur gear is eliminated. This reduces the moment of inertia of the pinion and increases its critical speed.
  • the power limit of the transmission according to the invention is thereby increased compared to the known transmission.
  • the radial play can be provided between the outer ring of the self-aligning bearing and the inner diameter of the drive shaft or between the inner ring of the self-aligning bearing and the outer diameter of the bearing journal.
  • a sleeve shrunk into the inner ring of the self-aligning bearing can also be provided, with the play then being present between this and the outer diameter of the bearing journal.
  • the spur gear according to the invention is used in particular for a roller which is designed as a hollow roller and in which the roller pendulum bearing is arranged essentially centrally within the external ring gear. This configuration causes the outer ring gear to only tip about its center when the roller shell is loaded and the distance between the axes of the outer ring gear and the pinion does not change.
  • the spur gear according to the invention is used for a deflection adjustment roller.
  • FIG. 1 An embodiment of the invention is shown in the drawing and is described below.
  • the single figure shows a schematic sectional view of a spur gear according to the invention and the associated end of one Roller.
  • roller 1 shows a roller 1, one end 2 of which is mounted on a support bracket 4 via a self-aligning bearing 3 and has an external ring gear 5.
  • the external ring gear 5 meshes with a pinion 6 designed as a hollow body, which is also mounted on the support bracket 4 via a self-aligning bearing 7 and is driven by a coupling shaft 8, the pinion end 9 of which is coupled to the pinion 6.
  • the roller 1 is designed as a hollow roller, the roller shell 10 of which can be rotated about a fixed support 11, which is also mounted in the support frame 4.
  • the coupling shaft 8 is arranged in a drive sleeve 12 with internal teeth 13, which is supported by two roller bearings 14 and 15 in a bearing plate 16 of the support frame 4 and is driven by a drive pin 17.
  • the internal toothing 13 of the drive sleeve 12 meshes with an external toothing 18 at the end 19 of the coupling shaft 8 remote from the pinion. In this way, rotation of the drive pin 17 is transmitted to the coupling shaft 8.
  • the coupling shaft 8 has further external toothing 20, which meshes with an internal toothing 21 of the pinion 6 so that the rotation of the drive pin 17 is finally transmitted to the pinion 6 via the coupling shaft 8.
  • the internal toothing 21 of the pinion 6 is located directly next to the centrally arranged self-aligning bearing 7 of the pinion 6, so that the coupling shaft 8 directly adjoins the self-aligning bearing 7 at the side.
  • the coupling shaft 8 is designed as a hollow shaft, which has a recess 22 on its pinion-side end 9, which receives a self-aligning bearing 23.
  • the self-aligning bearing 23 is mounted on a journal 24 which is fastened to the support frame 4 and also the self-aligning bearing 7 of the pinion 6 wears.
  • the self-aligning bearing 23 thus acts as a support bearing for the pinion 6, which counteracts tilting of the pinion 6.
  • a radial play can be provided between the outer ring 25 of the self-aligning bearing 23 and the inner circumference of the coupling shaft 8 or between the inner ring 26 of the self-aligning bearing 23 and the outer circumference of the journal 24, which allows the pinion 6 to be tilted by a predetermined amount.
  • a sleeve 27 can also be shrunk into the inner ring of the self-aligning bearing 23, the inside diameter of which is larger than the outside diameter of the journal 24 by the desired amount.
  • the pinion 6 can therefore vary according to the normal force to be transmitted by one to the line of engagement of the Twist the toothing with the external ring gear 5 vertical axis.
  • the pinion 6 Due to the axial offset between the coupling shaft 8 and the pinion 6 and the friction torque generated thereby, the pinion 6 also tilts about an axis parallel to the line of engagement as far as the clearance permits, so that there is a defined position of the pinion 6, in which a crowning of the pinion teeth is modeled kinematically.
  • the pinion 6 Due to the coupling between pinion 6 and coupling shaft 8 by means of two ring gears 20 and 21, the pinion 6 can also incline with respect to the coupling shaft 8, the inclination that occurs due to the small distance k between the center plane I of the pinion pendulum bearing 7 and the coupling 20, 21 between Coupling shaft 8 and pinion 6 is relatively small.
  • the coupling 20, 21 between the coupling shaft 8 and the pinion 6 is preferably between the self-aligning bearing 7 of the pinion 6 and the self-aligning bearing 23 arranged in the coupling shaft 8 and acting as a support bearing arranged.
  • the distance k between the clutch 20, 21 and the central plane I of the pinion pendulum bearing 7 is therefore minimal.
  • the coupling shaft 8 is directly coupled to the pinion 6.
  • the pinion 6 has few parts and has a low moment of inertia. In addition to a good load distribution on the tooth flanks of the pinion 6, this results in a high critical speed of the pinion 6.
  • the good load distribution is further favored in that the coupling forces between pinion 6 and coupling shaft 8 are at least partially compensated for by the self-aligning bearing 23 in the coupling shaft 8. Due to the proximity of the coupling 20, 21 to the center plane I of the pinion pendulum bearing 7, the bending angle between the pinion 6 and the coupling shaft 8 and between the coupling shaft 8 and the drive sleeve 12 is small, so that overall a spur gear with a very good power transmission to the roller jacket 10 is obtained. In addition to high efficiency, this also results in reduced wear.

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  • Gear Transmission (AREA)
EP96120229A 1996-02-29 1996-12-17 Transmission à engrenages droits pour l'entraínement d'un rouleau Expired - Lifetime EP0793038B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19607678 1996-02-29
DE19607678A DE19607678C1 (de) 1996-02-29 1996-02-29 Stirnradgetriebe für den Antrieb einer Walze

Publications (3)

Publication Number Publication Date
EP0793038A2 true EP0793038A2 (fr) 1997-09-03
EP0793038A3 EP0793038A3 (fr) 1998-04-29
EP0793038B1 EP0793038B1 (fr) 2001-05-30

Family

ID=7786785

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96120229A Expired - Lifetime EP0793038B1 (fr) 1996-02-29 1996-12-17 Transmission à engrenages droits pour l'entraínement d'un rouleau

Country Status (2)

Country Link
EP (1) EP0793038B1 (fr)
DE (2) DE19607678C1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10158034B4 (de) * 2001-11-27 2010-02-25 Voith Patent Gmbh Dichtungsanordnung für eine Walze
AT508004B1 (de) 2009-03-23 2010-10-15 Andritz Ag Maschf Lagergetriebeeinheit für eine papier- oder kartonmaschine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3804225A1 (de) 1987-02-12 1988-08-25 Voith Gmbh J M Stirnradgetriebe fuer den antrieb eines walzenmantels

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3290897A (en) * 1965-05-26 1966-12-13 Farrel Corp Drive for shell type rolls
FR2225660B1 (fr) * 1973-07-20 1975-04-11 Poclain Sa

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3804225A1 (de) 1987-02-12 1988-08-25 Voith Gmbh J M Stirnradgetriebe fuer den antrieb eines walzenmantels

Also Published As

Publication number Publication date
EP0793038B1 (fr) 2001-05-30
DE19607678C1 (de) 1997-02-13
EP0793038A3 (fr) 1998-04-29
DE59607004D1 (de) 2001-07-05

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