EP2057392A1 - Rotationsscheibe - Google Patents
RotationsscheibeInfo
- Publication number
- EP2057392A1 EP2057392A1 EP07788273A EP07788273A EP2057392A1 EP 2057392 A1 EP2057392 A1 EP 2057392A1 EP 07788273 A EP07788273 A EP 07788273A EP 07788273 A EP07788273 A EP 07788273A EP 2057392 A1 EP2057392 A1 EP 2057392A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotary
- rotation
- disk
- rotary disc
- axis
- 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- Withdrawn
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
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/084—Non-circular rigid toothed member, e.g. elliptic 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/30—Chain-wheels
Definitions
- the present invention relates to a rotary disk, in particular an embodiment of the teeth and the tooth gaps of the rotary disk. Furthermore, the present invention relates to a drive device with at least one rotation disk according to the invention and a belt transmission with at least one rotation disk according to the invention.
- Drive systems based on endless force-transmitting elements, such as belts or chains, and gears are widely used in industrial applications.
- endless force-transmitting elements such as belts or chains, and gears
- gears are widely used in industrial applications.
- such drive systems are used, for example, for transmitting a torque from the crankshaft to the camshafts.
- Trumschwingonne In such drive systems or Umschlingungsgetieri occur so-called Trumschwingonne.
- Trumschwingonne may be transversal, longitudinal or torsional vibrations of the force-transmitting endless element, which are excited by cyclical engine movements.
- the cyclic excitation of the Trumschwingung is usually done by a non-uniform drive element of the engine.
- Particularly important are the torsional vibrations or rotational angle fluctuations of the individual driven components against each other.
- a so-called "timing error” occurs, ie an angle of rotation of the camshaft relative to the crankshaft If this angle error is too great, emissions beyond the permitted pollutant limit values occur during operation of the engine.
- Uncircular gears have been proposed to compensate for these strand vibrations and rotational angle variations.
- Uncircular gears are to be understood as those gears which do not have a circular circumferential cross-section and in which the action curve or the loop of the force-transmitting endless element is not circular.
- the published patent application DE 10 2004 048 629 A1 describes a non-circular rotary disk of a timing drive.
- the rotation disk has a rotation disk radius which functionally depends on the rotation angle and an average radius, the mean radius being selected so that a circumferential arc length of a rotation disk wrap curve equals the product of the predetermined distance of the centers of adjacent teeth and the number of teeth ,
- the utility model DE 202 20 367 U1 describes a synchronous drive device with a plurality of rotors, which are coupled together by means of a force-transmitting endless element, wherein one of the rotors has a non-circular profile with at least two protruding sections which alternate with receding sections, wherein the angular positions of the protruding and the recessed portions of the non-circular profile and the degree of eccentricity of the non-circular profile are such that the non-circular profile is a deformed one. is applied to the force-transmitting endless member, which reduces or substantially nullifies a fluctuating load torque of a load assembly.
- the invention has for its object to provide a rotary disk or a drive device or a wrap-around, are compensated in the rotational angle fluctuations and while a much reduced wear of the power transmitting endless element occurs.
- the rotation disk according to the invention is rotatable about an angle of rotation about an axis of rotation and comprises a number of at a circumference of the rotor tion disc arranged teeth and located between the teeth tooth gaps, the tooth gaps are each symmetrical to a tooth gap axis of symmetry, and a rotation disc radius, which depends functionally on the rotation angle and a certain average radius, and is characterized in that the tooth gap symmetry axes each substantially to the local Center of curvature of the circumference of the rotation disk are aligned.
- each tooth gap symmetry axis runs through the axis of rotation or the center of this circular gear.
- the section of the toothed wheel between two such tooth space symmetry axes is called sector in the context of this description.
- the tooth space contours of the prior art are so distorted that they generate an increased load in the tooth base of the force-transmitting endless element. In addition, occurs on such contours increased wear.
- the tooth gap axes of symmetry are not all aligned with the axis of rotation, but are each directed substantially at the local center of curvature of the circumference of the rotating disc, i. they are perpendicular to the contour of the non-circular wheel.
- the tooth gap symmetry axes then usually no longer run through the axis of rotation.
- the usually a symymetic tooth geometry is determined.
- the flank contour of the tooth results from the shape of adjacent tooth gaps.
- the head contour of the tooth results from the geometry of the contour of the action line.
- the inventive alignment of the tooth gap symmetry axes on the respective local centers of curvature produces symmetrical tooth gap geometries with continuous transitions between the sectors in the tooth spaces. Furthermore, this avoids the problem of increased wear.
- the inlet and outlet of the force-transmitting endless element is friction and wear reduced, since the pressure due to the transmission of force from the teeth on the force-transmitting endless element is now evenly distributed and force peaks are avoided.
- the rotary disk according to the invention provides a significant advantage over the prior art.
- the circumference of the rotation disk is substantially non-circular.
- the tooth gap symmetry axes are perpendicular to the contour of the non-circular rotation disk.
- the rotation disk radius can be expressed by a harmonic development of the following form:
- r is the mean radius herein, Sr 1 mmd runout amplitude, H 1 is a number of elevations ⁇ ⁇ a phase position, and t is a running parameter from an interval from 0 to 2 ⁇ .
- the average radius is suitably chosen as a function of the other parameters, so that there is a desired length of the wrap-around curve of the rotary disk.
- the number of surveys is also called order. As can be seen, a plurality of angle-dependent interfering elements of different orders can be superimposed on the middle radius. If no fault element is provided, a circular rotation disk is obtained. Accordingly, it is provided that at least one fault element is always present.
- each parameter Sr 1 is set equal to zero, one also obtains a circular rotation disk. Accordingly, it is provided according to the invention that each parameter Sr 1 is not equal to zero.
- the teeth are designed for an involute toothing.
- the tooth gap symmetry axes are aligned such that a circular surface concentric with the rotation disk is not crossed by the tooth gap symmetry axes which do not run through the axis of rotation.
- the circular area can have a diameter of about 0.1 mm to about 20 mm and in particular have a diameter of about 0.5 mm to about 6 mm.
- a drive device comprises at least two rotary disks and a force-transmitting endless element for transmitting a torque between the rotary disks and is characterized in that at least one of the rotary disks is a rotary disk according to the invention. In this way, increased wear of the force-transmitting endless element is avoided even in the case of the drive device according to the invention.
- the drive device according to the invention can be designed for use in a motor vehicle.
- the drive device according to the invention may be designed for use in an aircraft.
- the drive device according to the invention is a synchronous drive device.
- the belt according to the invention comprises at least two rotary disks and a force-transmitting endless member for transmitting a torque between the rotary disks and is characterized in that at least one of the rotary disks is a rotary disk according to the invention. In this way, increased wear of the force-transmitting endless element is avoided even in the case of the inventive looping gear.
- FIG. 2 is an enlarged view of a portion of a prior art non-circular gear in FIG. 1;
- FIG. 3 shows a cross-sectional view of a rotation disk according to the invention in a preferred embodiment
- FIG. 4 shows an enlarged view of a region around the rotation axis of the rotation disk in FIG. 3,
- FIG. 5 shows a cross-sectional view of an embodiment of a rotation disk according to the invention whose radius is formed by the superimposition of a middle radius with a third order perturbation element and a sixth order perturbation element, and
- FIG. 6 shows an enlarged view of a region A about the rotation axis of the rotation disk in FIG. 5 Detailed description of the drawings
- Figures 1 and 2 show a rotary disk 1 10 of the prior art.
- the prior art rotary disk 110 has a non-circular cross section for compensating for torsional vibrations or rotational angle fluctuations.
- a number of teeth 120 are arranged along the circumference of the rotation disk 110.
- the rotation disk 1 10 rotates about a rotation axis 1 12.
- the tooth gaps located between the teeth 120 are in each case symmetrical to one another with respect to a tooth gap symmetry axis 130.
- the rotation disk 110 is located along an action curve 200 in engagement with a force-transmitting endless element (not shown).
- a tooth gap symmetry axis with associated tangent 220 is shown in Figure 2, passing through the axis of rotation 12, and further illustrating a tooth gap axis of symmetry with associated tangent 240 which, according to the present invention, does not pass through the axis of rotation 112, but perpendicular to the tangent stands and is aligned to the local center of curvature.
- FIGS. 3 and 4 show a rotation disk 10 according to the invention, which rotates about a rotation axis 12.
- a number of teeth 20 is arranged along the circumference of the rotary disk 10.
- Gaps 22 located between the teeth 20 are symmetrical with each other along a tooth gap symmetry axis 30.
- the tooth gap symmetry axes 30 are not limited to the rotation axis. Se 12 aligned.
- the tooth gap axes of symmetry 30 are rather aligned with the local centers of curvature, ie the center of curvature of the curvature at the point at which the tooth gap symmetry axis 30 intersects the circumference of the rotation disk. Therefore, around the rotation axis 12, a circular area 14 is formed, which is not crossed by any of the tooth gap symmetry axes 30.
- FIGS. 5 and 6 show a rotation disk 10 according to the invention in a further embodiment.
- the rotation disk radius is formed from an average radius, which is superposed by a third-order disturbing element and a sixth-order disturbing element in the manner according to the invention.
- FIG. 6 shows the course of the tooth gap symmetry axes 30 in the vicinity of the axis of rotation 12.
- a symmetrical configuration of the tooth gaps 22 along the circumference of the rotary disk 10 is possible without distortion and with continuous transitions of the tooth gaps on the tooth gap symmetry axes 30.
- the contour of the teeth 20 is then obtained from the positions of the tooth gaps 22 and the contour of the effective angle of the rotary disk 10.
- the rotary disk according to the invention is preferably used in a synchronous drive device or in a belt wrap.
- the Syn- chronantriebsvoriques or the belt transmission is preferably designed for use in a motor vehicle or in an aircraft.
- the rotation disk according to the invention can also be used independently of these applications, for example in textile or office machines.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pulleys (AREA)
- Gears, Cams (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202006012973U DE202006012973U1 (de) | 2006-08-23 | 2006-08-23 | Rotationsscheibe |
PCT/EP2007/058170 WO2008022912A1 (de) | 2006-08-23 | 2007-08-07 | Rotationsscheibe |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2057392A1 true EP2057392A1 (de) | 2009-05-13 |
Family
ID=37311694
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07788273A Withdrawn EP2057392A1 (de) | 2006-08-23 | 2007-08-07 | Rotationsscheibe |
Country Status (4)
Country | Link |
---|---|
US (1) | US20090253542A1 (de) |
EP (1) | EP2057392A1 (de) |
DE (1) | DE202006012973U1 (de) |
WO (1) | WO2008022912A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006049987A1 (de) * | 2006-10-24 | 2008-04-30 | Schaeffler Kg | Kraftschlüssiges Umschlingungsgetriebe mit unrunder Rotationsscheibe |
JP6955157B2 (ja) * | 2017-11-06 | 2021-10-27 | 株式会社椿本チエイン | スプロケット及び伝動機構 |
US11255700B2 (en) * | 2018-08-06 | 2022-02-22 | Allegro Microsystems, Llc | Magnetic field sensor |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE947584C (de) * | 1949-07-07 | 1956-08-16 | Goodman Mfg Co | Geschwindigkeitswechselgetriebe |
US3752035A (en) * | 1971-04-05 | 1973-08-14 | Gen Electric | Auto-synchronizing gear system |
DE2203233A1 (de) * | 1972-01-24 | 1973-08-02 | Aero Commerce Gmbh | Verzahnung fuer unrunde getrieberaeder, insbesondere ovalzahnraeder |
DE2303453A1 (de) * | 1973-01-25 | 1974-11-21 | Hallden Machine Co | Zahnradgetriebe |
US3899932A (en) * | 1973-12-19 | 1975-08-19 | Roger Owen Durham | Chain retention device for elliptical sprockets |
US5545871A (en) * | 1994-01-11 | 1996-08-13 | Micropump, Inc. | Method of making a modified elliptical gear |
US7074147B2 (en) * | 1998-08-25 | 2006-07-11 | Cloyes Gear And Products, Inc. | Roller chain sprocket with symmetric cushion rings |
DE69711607T2 (de) * | 1997-06-18 | 2003-11-27 | Morse Tec Europe Srl | Kettenrad mit zur Geräuschlosigkeit verbessertem Zahnprofil |
DE10022080C2 (de) * | 2000-05-03 | 2002-07-18 | Demag Mobile Cranes Gmbh & Co | Turas |
CA2463715C (en) * | 2001-11-27 | 2010-09-14 | Litens Automotive | Synchronous drive apparatus with non-circular drive elements |
SG126693A1 (en) * | 2002-03-27 | 2006-11-29 | Inst Of High Performance Computing | Sprocket tooth profile |
DE20319172U1 (de) * | 2003-09-18 | 2004-04-22 | Litens Automotive Partnership, Woodbridge | Nicht kreisförmige Rotationskomponente |
ES2528666T3 (es) * | 2006-10-09 | 2015-02-11 | The Gates Corporation | Sistema de transmisión de correa sincrónica |
DE102007003399A1 (de) * | 2007-01-23 | 2008-07-24 | Schaeffler Kg | Rotationsscheibe mit einer sich periodisch ändernden Zahnlückengeometrie |
-
2006
- 2006-08-23 DE DE202006012973U patent/DE202006012973U1/de not_active Expired - Lifetime
-
2007
- 2007-08-07 US US12/373,900 patent/US20090253542A1/en not_active Abandoned
- 2007-08-07 WO PCT/EP2007/058170 patent/WO2008022912A1/de active Application Filing
- 2007-08-07 EP EP07788273A patent/EP2057392A1/de not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO2008022912A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2008022912A1 (de) | 2008-02-28 |
DE202006012973U1 (de) | 2006-10-19 |
US20090253542A1 (en) | 2009-10-08 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
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17P | Request for examination filed |
Effective date: 20090323 |
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AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK RS |
|
17Q | First examination report despatched |
Effective date: 20090728 |
|
DAX | Request for extension of the european patent (deleted) | ||
RBV | Designated contracting states (corrected) |
Designated state(s): DE FR GB IT |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20110510 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230522 |