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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
  • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/30—Parts of ball or roller bearings
  • F16C33/58—Raceways; Race rings
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
  • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
  • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
  • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
  • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
  • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
  • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
  • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
  • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
  • F16C2240/30—Angles, e.g. inclinations
  • F16C2240/34—Contact angles
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
  • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
  • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
  • F16C2240/70—Diameters; Radii
  • F16C2240/80—Pitch circle diameters [PCD]
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2326/00—Articles relating to transporting
  • F16C2326/01—Parts of vehicles in general
  • F16C2326/02—Wheel hubs or castors

Definitions

• the present invention is directed to an asymmetric rolling bearing, and more particularly to a multi-row asymmetric rolling bearing.
• the invention will be described with reference to a wheel bearing unit for driven or non-driven wheels of motor vehicles such as pickup trucks, light trucks or SUVs (Sports Utility Vehicles). It is also pointed out that the present invention can also be used in other rolling bearings.
• Rolling bearings are known from the prior art, which have an outer ring, an inner ring and disposed between these rings rolling elements. It is also known from the prior art to arrange these rolling elements in two or more rows. In this way it is possible to distribute the loads acting on the bearing on several rows of rolling elements and thus on several rolling elements. In many applications, however, the bearing center of the respective wheel bearings and the Rad Signsline do not match. For example, it is possible for a wheel suspension of a vehicle to have the wheel contact point of the wheel or tire on the outside relative to the center of the bearing of the vehicle. In this case, uneven forces are applied to the bearing.
• the rolling bearing according to the invention has a first bearing ring and a second bearing ring and a plurality of rolling elements arranged between the first bearing ring and the second bearing ring.
• the rolling elements are arranged in several rows, the rows being arranged asymmetrically in the longitudinal direction of the rolling bearing with respect to any plane perpendicular to the longitudinal direction of the rolling bearing.
• Conventional bearings are usually constructed so that the rows of rolling elements are symmetrical with respect to a median plane.
• such a geometric plane, with respect to which the series are arranged symmetrically can not be formed.
• a series is understood to mean that the rolling elements are arranged substantially annularly between the inner ring and the outer ring.
• the plane with respect to which the rolling elements are arranged asymmetrically is a median plane of the rolling bearing. This means that the plane, also referred to below as the center plane, divides the rolling bearing into two halves of substantially equal length in the longitudinal direction.
• the number of rows is odd. This means that particularly preferably on one side of the median plane, several rows are arranged than on the other side of the median plane, and therefore the number of rows with respect to this median plane is unequal.
• At least three rows are provided.
• the rolling bearing with three rows are located on one side of the plane two rows of rolling elements and on the other side of the plane a row.
• the pitch circle diameters of at least two rows preferably differ.
• the rolling bearing is also formed asymmetrically with respect to the pitch circle diameter of the individual rows with respect to this center plane.
• a pitch circle diameter is understood to be the distance between the center of a rolling element and the center of the rolling element which lies exactly opposite it.
• the row with the larger pitch diameter offers larger areas for power and therefore can absorb a larger force and thus can be taken into account by the different choice of pitch diameter the fact that forces outside of the bearing center act on the bearings.
• the pitch diameter of at least one outer row of the rolling bearing is greater than each of the pitch diameters of one of the other rows. This means that an outer row has a larger pitch circle diameter compared to the other rows. Thus, this outer row can absorb the highest forces.
• the row with the largest pitch circle diameter is arranged with respect to the bearing center on the side on which act also the off-center forces on the wheel bearing.
• the axial distance between a first row and a second row adjacent to this first row is less than the axial distance between the second row and a third row adjacent to this second row.
• two rows are preferably arranged on one side with respect to a bearing center and the third row d. H. the row with the greater distance on the other side of the bearing center. Therefore, preferably, the two arranged on one side of the bearing center rows absorb larger forces and are preferably arranged on those side with respect to the bearing center on which the higher forces are applied to the rolling bearing.
• the pitch circle diameter of a flange-side outer row is greater than the pitch circle diameter of one of the other rows.
• a flange-side outer row is understood to mean that row which is arranged closest to the flange of the wheel carrier to which the rim and the tire are fastened.
• the flange-side outer row is the row on the vehicle outside. This embodiment is selected when the wheel contact point is located on the vehicle outer side relative to the bearing center. It would also be possible in this case to provide more rows on the flange side with respect to the center plane than on the wearer side. However, it is also possible that the wheel contact point relative to the center of the vehicle interior side - hereinafter also referred to as the carrier side - is.
• the pitch circle diameter of the carrier-side outer row would preferably be greater than each of the pitch circle diameter of one of the other rows. In this case, more rows could also be arranged on the carrier side with respect to the center plane than on the flange side.
• the outer ring on a predetermined flange-side outer diameter and a deviating carrier-side outer diameter. This means that the diameter of the outer ring also varies along the length of the rolling bearing. By means of this embodiment it can be achieved that a certain wall thickness of the outer ring can be maintained even with differently sized pitch circle diameters.
• the rolling elements are selected from a group of rolling elements, which contains balls, cylindrical rollers, cones and the like. It is possible that the same WälzShavatung is arranged in all rows of a bearing, such as balls. However, it is also possible that different rows of the rolling bearing are equipped with different types of rolling elements, for example, one row is equipped with balls and another row with cylindrical rollers. In this way, the balance of forces acting on the rolling bearing can be ideally taken into account.
• the diameters of the rolling elements of at least two rows are different.
• those rolling elements with the larger diameter are provided on the respective flange or carrier side arranged outside rows.
• all rows have the same contact angle.
• the pressure angle is determined relative to the longitudinal direction or axis of rotation of the bearing. This means that the raceways are arranged on the outer and inner rings so that the power transmission of all rows takes place at substantially the same angle with respect to the axis of rotation of the bearing.
• the pressure angle of at least two rows are chosen differently. Also by the choice of these pressure means, the wheel bearing to the respective requirements, d. H. the respectively absorbed forces or their directions are adjusted. Preferably, the pressure angles of the outer rows are greater than the pressure angles of the inner rows.
• At least one bearing ring is constructed in two parts.
• this is the bearing inner ring, one part of which carries the raceways for two rows of rolling elements and the second part of a raceway for the remaining row.
• the median plane is preferably between the bearing ring halves.
• the division of the bearing inner ring in two bearing ring halves facilitates its assembly. It is also possible to provide only one inner ring half with raceways for part of the rows and provide the raceways for the remaining rows directly on a preferably rotatable relative to the outer ring flange body.
• the rolling bearing has a device for detecting the wheel speed.
• This may be, for example, a magnetic disk that outputs a changing signal to a sensor as a result of the rotation.
• the present invention is further directed to a wheel carrier with a rolling bearing of the type described above.
• Fig. 1 is a schematic representation for illustrating the problem underlying the invention
• FIG. 6 shows a rolling bearing according to the invention in a fifth embodiment
• FIG. 9 shows a partial view of a bearing according to the invention for illustrating the geometries.
• Fig. 1 shows a schematic representation for illustrating the problem underlying the invention.
• the reference numeral 1 refers to a wheel bearing, which is not shown in detail.
• This wheel bearing has a bearing center M on.
• a tire 7, which is arranged on a rim 8 is displaced laterally to the right with respect to this bearing center M, which is indicated by the line R.
• the tire is displaced in the upper part of the image I relative to the bearing center M in the direction of a wheel carrier 6. Therefore, the Radauf- standpoint is relative to the bearing center M on the vehicle inside.
• the reference numeral 10 refers to a brake disc.
• Fig. 2 shows an inventive rolling bearing in a first embodiment.
• This rolling bearing has a bearing outer ring 2 and a bearing inner ring 3.
• the bearing inner ring 3 is designed in two parts in the embodiment shown in Fig. 1 and has two inner ring halves 3a and 3b.
• the rolling bearing shown in Fig. 2 has three rows 11, 12 and 13, in each of which rolling elements 5 are arranged.
• the rolling elements 5 are each arranged in rings and extend in planes perpendicular to the plane of the figure.
• the individual rolling elements 5 can run in (not shown in detail) bearing cages.
• the reference numeral 15 refers to sealing means for sealing the rolling bearing. 1
• the reference ME refers to a median plane which is perpendicular to the plane of the figure.
• the rows in the longitudinal direction LR of the bearing are asymmetrical, ie on the left side of this center plane E are the two rows 11 and 12 and on the right the row 13.
• this asymmetrical arrangement of the rows would also be an even number of rows possible so that, for example, three rows are arranged on one side of the median plane and only one on the other side.
• you realize that the distance the rows 11 and 12 in the longitudinal direction LR is less than the distance between the row 12 and the row 13 in the longitudinal direction LR.
• the rows 11 and 12 are thus arranged in tandem.
• the individual rows 11, 12 and 13 have different pitch circle diameters (Tk1, Tk2, Tk3), which, as mentioned above, from the distance between a rolling element center of a rolling element to an opposite rolling element and there turn the rolling element center result.
• the row 11 has the largest pitch circle diameter Tk1 and the row 13 the smallest pitch circle diameter Tk3, wherein the pitch circle diameter Tk2 of the row 12 is only slightly larger than the pitch circle diameter Tk3.
• the vehicle outer side or the flange side row 11 and 12 have a larger pitch circle diameter than the carrier side row 13.
• the rolling bearing shown in FIG. 2 is particularly suitable for those situations in which the wheel contact point lies with respect to the bearing center on the vehicle outside or on the flange side.
• a pitch circle diameter decreasing on average from outside to inside is achieved.
• the distance between the row 13 and the row 12 is considerably greater than the distance between the row 11 and the row 12. In this way, at the same time the row 13 relative to the rolling bearing can be arranged relatively far outside.
• FIG. 3 shows a bearing arrangement according to the invention in a second embodiment.
• a flange 17 is arranged in this embodiment, the bearing ring 2.
• This flange can be connected to the carrier or a wheel.
• the Rolling elements 5 of the individual rows 11, 12 and 13 each have different diameters, wherein in this embodiment, the diameters of the respective outer rows 11 and 13 are selected to be greater than the diameter of the rolling elements in the inner row 12.
• the individual rolling elements 5 of all rows have a substantially identical rolling element diameter.
• Fig. 4 shows a further embodiment of the bearing according to the invention.
• a flange 17 is not arranged on the outer ring but on a flange body 18 rotatable relative to the outer ring.
• the two inner ring halves 3a and 3b are held together by a flanged edge 21 or flange 21 on the one hand and a shoulder 22 on the other hand on the flange 18 and axially braced.
• the inner ring 3 and the inner ring halves 3a and 3b are rotatably connected to the flange 18.
• the inner ring half 3a has two raceways 9 for the rolling elements of the rows 11 and 12.
• the inner ring half 3b has a raceway 9 for the rolling elements of the row 13.
• Fig. 5 shows another embodiment of a rolling bearing according to the invention.
• the two inner ring halves 3a and 3b are provided here, but only the inner ring half 3b.
• the raceways 9 for the rolling elements of the rows 11 and 12 are arranged directly on the flange 18 in this case. It can be seen that in the embodiment shown in Figures 4 and 5, although the diameter of the rolling elements of the rows 11 and 13 is substantially equal but the pitch circle diameter of the row 13 is slightly smaller than the pitch circle diameter of the row 11.
• Fig. 6 shows another embodiment of a rolling bearing according to the invention.
• a flange 21 is provided which presses the two inner ring halves 3a and 3b against the shoulder 22 of the flange 18.
• two flanges 17 and 24 are provided here, wherein the flange 24 is arranged on the bearing outer ring 2. It can also be seen that the diameter of the bearing outer ring 2 in the direction of the flange 17 is greater than the diameter in the direction of the wheel carrier (not shown), that is, in FIG. 6 to the right.
• Fig. 7 shows a further embodiment of a rolling bearing according to the invention. This embodiment is similar to that of FIG. 5, but also here a second flange 24 is arranged on the bearing outer ring 2.
• Fig. 8 shows a further embodiment of a bearing according to the invention for illustrating the geometries.
• reference character B denotes the total bearing width
• reference character D denotes the bearing height, ie, the distance between a radially inner surface of the bearing inner race 3 and a radially outer surface of the bearing outer race 2, disregarding the flange 24.
• the reference character F denotes the flange-side outer diameter of the outer ring and the reference symbol E the vehicle inner side or carrier-side outer diameter of the rolling bearing.
• the reference A denotes the bore diameter of the rolling bearing.
• the reference symbols Dw denote the individual diameters of the respective rolling bodies, for example the reference character Dw1 denotes the diameter of a rolling body 5 in the row 11.
• the reference symbols Tk1 denotes the reference symbols
• the reference numeral n denotes the width of the middle board between the rows 12 and 13.
• the reference numeral m designates the flange width of the inner ring or the inner ring half 3b on the side facing the carrier device (not shown).
• the reference numerals ⁇ 1- ⁇ 3 respectively designate the on-board angles of the inner raceways 9.
• the pitch circle diameter Tk1 of the row 11 is larger than the pitch circle diameter Tk2 of the row 12.
• the pitch circle diameter Tk1 is preferably greater than or equal to the pitch circle diameter Tk3 of the row 13.
• the pitch diameter Tk3 is greater than or equal to the pitch circle diameter Tk2 of the row 12.
• the flange-side outer diameter F is greater than the carrier-side diameter E (defined relative to the longitudinal direction LR) and the contact angle ⁇ 3 of the row 13 is greater than or equal to the pressure angles ⁇ 1 and ⁇ 2 of the rows 11 and 12.
• the pitch circle diameter Tk3 would be greater than the pitch circle diameter Tk2 and the pitch circle diameter Tk3 would be greater than or equal to the pitch circle diameter Tk1.
• the carrier-side outer diameter E of the outer ring would be greater than the flange-side outer diameter F. It should be noted, however, that in the embodiment described here, all pitch circle diameter could be selected to be equal, since the asymmetrical arrangement of the rows d. H. the arrangement of two rows on one side of the median plane ME and only one row on the other side in each case on the side with the two rows higher forces can be absorbed.
• the overall bearing width B is greater than the sum of all the rolling body diameters added to the rim width of the inner ring m and the centerboard width n.
• the total bearing width in the embodiment shown in FIG. 9 is greater than 28 mm.
• the vehicle inner side or carrier-side outer diameter of the outer ring E in the embodiment shown in FIG. 8 is greater than the sum of the pitch circle diameter Tk3 and the diameter Dw3 of the rolling elements of the row 13.
• the carrier-side outer diameter E is at least 6 mm larger than the above-mentioned Sum of the pitch circle diameter Tk3 and the diameter Dw3.
• the pitch circle diameter Tk3 is preferably at least 3.5 mm larger than the bore diameter A.
• the flange-side outside diameter F is greater than the pitch circle diameter Tk1 of the row 11 plus the rolling body diameter Dw1.
• the carrier-side outer diameter E is greater than the sum of the pitch circle diameter Tk1 and the rolling body diameter Dw 1 by at least 6 mm.
• the respective on-board angles ⁇ 1 and ⁇ 3 of the raceways 11 and 13 are greater than the on-board angle ⁇ 2 of the middle track of row 12 or the same.
• the angles to the longitudinal axis of the bearing are considered. This means that the pressure angles of the outer rows d. H. however, the angles at which the forces are transmitted from the outer ring to the inner ring are greater in the outer rows than the pressure angle of the inner row 12. However, it would also be possible for the pressure angles of all rows to be the same.

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• 2006
  • 2006-01-31 DE DE102006004297.2A patent/DE102006004297B4/de active Active
• 2007
  • 2007-01-16 CA CA2641532A patent/CA2641532C/en active Active
  • 2007-01-16 KR KR1020087020552A patent/KR20080091246A/ko not_active Application Discontinuation
  • 2007-01-16 US US12/162,746 patent/US8007182B2/en active Active
  • 2007-01-16 WO PCT/DE2007/000056 patent/WO2007087775A1/de active Application Filing
  • 2007-01-16 JP JP2008555604A patent/JP2009525446A/ja active Pending
  • 2007-01-16 RU RU2008135302/11A patent/RU2429392C2/ru active
  • 2007-01-16 BR BRPI0706796A patent/BRPI0706796A8/pt not_active IP Right Cessation
  • 2007-01-16 EP EP07711146A patent/EP1979639A1/de not_active Ceased
  • 2007-01-16 CN CN2007800087234A patent/CN101400905B/zh active Active

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