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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/10—Differential gearings with gears having orbital motion with orbital spur 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
  • F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for orbital 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
  • F16H2048/087—Differential gearings with gears having orbital motion comprising bevel gears characterised by the pinion gears, e.g. their type or arrangement
• • 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
  • F16H2048/102—Differential gearings with gears having orbital motion with orbital spur gears with spur gears engaging face 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
  • F16H48/00—Differential gearings
  • F16H48/38—Constructional details
  • F16H48/40—Constructional details characterised by features of the rotating cases

Definitions

• the invention relates to a differential assembly which is part of a differential gear and is used in particular for use in the drive train of a motor vehicle.
• differential arrangements are well known. They usually comprise a differential carrier, which is rotatably driven about a rotational axis, two side tenwellener which are rotatably supported in the differential carrier and serve for torque transmission to two side shafts, and a plurality of differential gears, which rotate together with the differential carrier and with the side gears in meshing engagement are.
• a differential assembly with a two-part differential carrier comprising a cup-shaped basket part with a first bearing lug and a this occlusive cover-shaped basket part with a second bearing attachment.
• the side shaft gears and the differential gears are inserted axially into the pot-shaped basket part, which is then closed with the ceiling-shaped basket part.
• a differential arrangement in the form of a crown wheel differential is known.
• the differential carrier has four openings for mounting the differential gears.
• radially inwardly directed ribs are formed, which are connected to a pin member.
• the pins each protrude into the four mounting holes and have at their ends annular grooves in the axial securing rings for fixing the Ausretesrä- the intervene.
• the crown wheels are inserted axially in the lateral ends of the differential carrier and fixed by means of large axial securing rings relative to this.
• the differential carrier has two opposing mounting holes. In the circumferential direction holes are provided between the mounting holes, in which after insertion of the gear set a pin part is inserted for storing two differential gears.
• the present invention has for its object to propose a differential assembly having a high strength and torsional stiffness, compact builds and thus is inexpensive to produce and can transmit high torques.
• a differential assembly in particular for use in the drive train of a motor vehicle, comprising a differential carrier which is rotatably driven about a rotation axis (A) and in a shell portion at least one mounting hole and in two opposite lid portions each integrally formed bearing neck having; Side shaft gears, which are insertable through the mounting hole in the Differenti-alkorb and - in the assembled state - rotatably supported in the differential carrier on the axis of rotation; four differential gears, which are insertable through the mounting hole in the differential carrier and - in the assembled state - rotate together with the differential carrier about the axis of rotation and wheels are in meshing with the side shafts; a spider assembly which is drivingly connected to the differential carrier in revolution and includes four pins, the four pins, when mounted, supporting one of the differential gears and at least two of the four spigots being adapted to be inserted through the mounting aperture; the differential case comprising the skirt portion and the lid portions is integrally formed.
• one-piece is understood in this context that the differential gears and side gears are mounted exclusively on the at least one mounting hole in the shell section or that the differential carrier has two integral lid parts with molded bearing lugs for storage in a standing housing, only from the Sei -
• the differential assembly is preferably designed as a crown-wheel differential, wherein the side-shaft gears have a crown gear and the differential gears have a spur gear. This has the advantage of a short axial length and thus a relatively low weight.
• the differential assembly may be designed as a bevel gear differential,
• the first and second spigots are drivably connected to the differential carrier in the circumferential direction, the third and fourth spigots being connected at their inner ends to the first and second spigots. At their outer ends, following a first solution, the third and fourth pins are held against the differential carrier in the sense of the circumference.
• the first and the second pin are designed in one piece according to a first embodiment and together form a first pin member and the third and the (fourth pin are formed in one piece and together form a second pin member which is connected to the first pin member such that torque
• the attachment of the first pin part in the differential carrier can be accomplished in various ways become.
• diametrically opposed holes are provided in the shell portion of the differential carrier, in which the first pin part is inserted with its first and second pins; these are arranged offset relative to the at least one mounting opening in the circumferential direction.
• two mounting openings are provided, in each of which a bearing disc is seated, wherein the first pin part is inserted with its first and second pin in the bearing discs.
• the torque is transmitted in the circumferential direction of the differential carrier via the bearing disk on the first pin member.
• the arrangement of the bearing discs in the mounting holes results in a high torsional rigidity and strength of the differential carrier, since the bearing discs have a stiffening effect in the circumferential direction.
• a bore is provided diametrically opposite the mounting opening into which the first pin part is inserted with its first pin; the second pin is connected to a bearing disc which is seated in the mounting hole.
• the second pin and the bearing disc can also be designed in one piece, which has a favorable effect on production and assembly.
• the first and the second pin are made separately from each other and connected to the second pin member for transmitting a torque.
• the third and fourth pins are preferably perpendicular to the first pin part. It is convenient to make the first pin part cylindrical. It can simply be inserted into the bores in the casing section of the differential carrier or into bores of the bearing disks inserted in the assembly openings of the differential carrier and fixed axially relative to these. This is done by means of at least one locking ring, which engages in an annular groove of the first pin member. The use of only one locking ring is favorable in terms of manufacturing and assembly costs. It but can also be used per pin a locking ring.
• the one-piece second pin part is designed such that it can be inserted through one of the mounting holes in the differential carrier.
• the pins of the second pin member protrude into the mounting holes without contact.
• the second pin part lies completely within the differential cage and has with its pins in the direction of the webs formed in the circumferential direction between the mounting holes.
• the third and the fourth pin preferably spherical end faces whose curvature is adapted to an inner cylindrical surface of the differential carrier.
• the second pin member preferably has a transverse through bore into which the first pin member is inserted.
• the axes of the first and the second pin part in particular form a right angle with each other.
• the nesting of the pin parts has the advantage that can be dispensed with a further attachment of the second pin member on the differential carrier and that the second pin member is held without additional components coaxial with the axis of rotation of the differential carrier.
• the second pin part has following the through-hole sleeve portions which form contact surfaces for the mounted on the pin of the first pin member differential gears.
• the third and the fourth pin preferably shoulders, against the third and fourth differential gears can start inside.
• the second pin part - in relation to the axis of rotation A of the differential carrier - have axial flats.
• the side shafts inserted into the side shaft gears in a rotatable manner can dip.
• the second pin part may also have a through hole coaxial with the axis of rotation A
• the first pin part may have a central portion with a reduced axial extent with respect to the axis of rotation A. The side waves can thus in immerse the through hole and the recess of the first pin part, so that a short axial length is achieved.
• the third and fourth pins are drivingly connected at their outer ends to the differential cage in a circumferential sense according to a second solution. At their inner ends, the third and fourth pins are connected to the first and second pins.
• the first and second pins are designed in one piece and together form a first pin part and the third and fourth pins are also designed in one piece and jointly form a second pin part.
• the first and second pin members are configured substantially as described above.
• the first pin part is inserted into the through hole of the second pin member and sits with its pin in the holes of the shell portion.
• the third and the fourth pin are preferably drive connected via inserted into the mounting holes of the differential carrier bearing disks in the circumferential sense with the differential carrier drive.
• the first and the second pin part can also be connected with no need for a hole.
• both pin parts can be designed identically and have transverse grooves with which they engage with one another and are axially secured against one another.
• the third and fourth pins are designed separately from each other and connected at their inner ends with the first pin member.
• the third and the fourth pin preferably have at their inner ends in each case a plug-in projection, with which they are inserted into a central through hole of the first pin member.
• the third and the fourth pin preferably have integrally formed bearing disks with which they are received in the assembly openings of the differential carrier and are drive-connected in the sense of the circumference.
• the third and the fourth pins are designed separately from each other and connected at their inner ends with a carrier element connected to the first pin part. It is the first pin part with its first and second pin preferably be inserted into holes in the shell portion, which are offset from the mounting holes in the circumferential direction.
• the carrier element preferably has a first through hole extending perpendicular to the axis of rotation, into which the first pin part is inserted, as well as two further holes transverse to the through hole into which the third and fourth pins are inserted. It is advantageous if the carrier element per pin has a shoulder against which the corresponding differential gears can at least indirectly start inside. It can be interposed between the shoulder and the pinion a thrust washer.
• the third and the fourth pin are secured at their inner ends in each case by means of a securing ring on the carrier element. At their outer ends of the third and fourth pin preferably integrally formed bearing discs, with which they are received in the mounting holes.
• the mounting openings are preferably designed symmetrically with respect to the longitudinal center plane.
• the pins of the journal cross assembly are axially fixed to the holes of the opposite bearing discs or the shell portion; This is preferably done by means of retaining rings which engage in annular grooves of the pins.
• these are kept free of play relative to this at least in the circumferential direction of the differential carrier.
• the differential carrier at each of the mounting holes has two mutually circumferentially opposite support surfaces with which the associated bearing plate in the assembled state in abutment.
• the support surfaces are on a cross-sectional plane through the journal axis or directly adjacent to this.
• Figure 2 shows the differential arrangement according to section line H-II of Figure 1;
• Figure 3 shows the differential arrangement according to section line MI-III of Figure 2;
• Figure 4 shows the differential arrangement according to section line IV-IV of Figure 2;
• Figure 5 shows the spider assembly of Figure 1 in plan view
• Figure 6 shows the spider assembly of Figure 1 in side view
• FIG. 5 shows a differential arrangement according to the invention according to a second exemplary embodiment in a radial view
• Figure 8 shows the differential assembly of Figure 7 according to section line VIII-VIII;
• FIG. 9 shows the differential arrangement from FIG. 8 according to section line IX-IX;
• FIG. 10 shows the differential arrangement from FIG. 8 according to section line X-X;
• Figure 11 is a differential arrangement according to the invention according to a third exemplary embodiment 5 in cross section;
• Figure 12 is a differential arrangement according to the invention according to a fourth embodiment in cross section;
• Figure 13 is a differential arrangement according to the invention according to a fifth embodiment in cross section.
• Figure 14 shows a differential arrangement according to the invention according to a sixth embodiment in cross section;
• FIG. 15 shows a differential arrangement according to the invention in a radial view according to a seventh exemplary embodiment
• FIG. 16 shows the differential arrangement from FIG. 15 according to section line XVI-XVI;
• FIG. 18 a radial view of a differential arrangement according to the invention in accordance with an eighth exemplary embodiment
• FIG. 19 shows the differential arrangement from FIG. 18 according to section line XIX-XIX;
• FIG. 20 shows the differential arrangement from FIG. 18 according to section line XX-XX;
• Figure 21 shows a differential arrangement according to the invention according to a ninth embodiment in cross section; 0
• FIG. 22 a cross-sectional view of a differential arrangement according to the invention in accordance with a tenth exemplary embodiment
• FIG. 23 shows the pin cross arrangement from FIG. 22 in a perspective view
• FIGS. 1 to 6 will be described together below.
• a differential assembly 2 with a one-piece differential carrier 3 which is to be stored in a standing housing, not shown.
• two mutually pointing in the opposite direction bearing lugs 4, 5 are formed on the differential carrier 3, on the $ 0 each a rolling bearing not shown here is pushed.
• the differential carrier 3 is made in one piece as a casting, so that it has a high rigidity.
• the differential assembly 2 is part of a differential gear in the drive train of a motor vehicle and is used for torque transmission from a longitudinal drive shaft on two side shafts.
• a flange 6 is integrally formed on the differential carrier 3, on which a ring gear for introducing the torque in the differential assembly 2 can be attached.
• the introduced torque is transmitted via four on a spider assembly 7 rotatably mounted and rotating together with the differential carrier 3 differential gears 8 on this meshing side shaft gears 9, 10.
• the side shaft gears 9, 10 are compared to the differential carrier 3 usually supported by means of reibmindernder thrust washers 12, 13 axially.
• the side shafts, which are connected via a longitudinal toothing 14, 15 with the side shaft gears 9, 10, are coaxially within the sleeve-shaped bearing lugs 4, 5 and penetrate the differential carrier 3 in the axial direction.
• the differential assembly 2 is designed in the form of a Kronenraddifferentials, wherein the side shaft gears 9, 10 are designed as crown wheels and the differential gears 8 as spur gears. This results in a compact design and low weight.
• mounting holes 16 are provided. These are diametrically opposite each other, have a same contour and are each designed symmetrically with respect to the longitudinal center plane to avoid unwanted imbalances.
• Each of the mounting holes 16 is just large enough to insert the side shaft gears 9, 10 and the differential gears 8 in the differential carrier 3.
• first and the second pin 17, 18 are integrally formed and together form a first cylindrical pin member 22.
• the third and fourth pins 19, 20 are also designed in one piece and together form a second pin member 23.
• Das first pin member 22 is inserted into bores 24, 25 in the shell portion 26 of the differential carrier 3 and secured axially by means of a securing ring 27 with respect to this.
• the second pin member 23 is fixed in the circumferential direction with the first pin member 22, so that a torque is transmitted from the first to the second pin member.
• the second pin member 23 has a transverse through hole 21 into which the first pin member 22 is inserted.
• the Axes B, C of the two pin parts 22, 23 in this case form a right angle with each other.
• the second pin member 23 is free of support against the differential carrier 3, so that the manufacturing tolerances of the mounting holes 16 can be roughly maintained.
• the second pin member 23 has, subsequent to the through-bore 21, two sleeve sections 28, 29, via which the torque is transmitted in the circumferential sense of the differential carrier 3.
• the sleeve portions 28, 29 are designed so long that their end faces contact surfaces 31, 32 form for the mounted on the pins 17, 18 of the first pin member 22 differential gears 8.
• the third and fourth pins 19, 20 have shoulders 33, 34 against which the third and fourth differential gears 8 can start inside. This ensures that the differential gears 8 are held with their serrations in the region of the crown gears of the side shaft gears 9, 10.
• FIGS. 7 to 10 which show a second exemplary embodiment of a differential arrangement according to the invention, will be described jointly below.
• the differential arrangement shown largely corresponds to that of FIGS. 1 to 6, for which reason reference is made to the above description with regard to the similarities.
• corresponding components are provided with increased by 50 reference numerals.
• the present embodiment differs by the shape of the mounting holes 66, in each of which a washer-shaped bearing disc 87, 88 seated free of play.
• the first pin member 72 is inserted into bores 74, 75 of the bearing discs 87, 88 and axially secured against these.
• the dimensions and tolerances are chosen so that a torque in the circumferential direction of the differential carrier 53 via the bearing plates 87, 88 is transmitted to the first pin member 72.
• the circumferentially between the shell openings 66 formed shell portion is designed breakthrough, so that a high rigidity of the differential carrier 53 results.
• the pins 69, 70 of the second pin member 73 are therefore shorter than the pins 67, 68 of the first pin member and have spherical end faces. With these spherical end faces, the pins 69, 70, as shown in FIG. 10, bear against the inner cylindrical surface of the differential carrier 53 without support. In this case, no direct force transmission from the basket 53 to the second pin member 73.
• annular grooves are provided, in each of which a locking ring 86 for securing the first pin member 72 relative to the bearing discs 87, 88 engages.
• the sleeve portions 78 are shortened compared to the first embodiment, so that the second pin member 73 can be threaded into the modified mounting hole 66.
• spacers 30 are placed on the sleeve sections 78 against which the differential gears 58 start.
• the mounting holes 66 are formed by covering two surfaces, of which a first surface 89 inscribes approximately a circle and of which a second surface 90 is greater than a radial projection of the side shaft gears 59, 60th Der Deutschen
• the second face 90 is designed essentially in the form of a slot extending in the circumferential direction, the shape of which in radial view corresponds approximately to the radial projection of the side-shaft gears 59, 60 ,
• the slot is located away from the flange 56 with respect to a plane spanned by the journal axes B, C.
• the contact points are formed by two circumferentially opposing support surfaces 92, 93, against which the associated bearing plate 87, 88 is supported in the circumferential direction.
• the bearing discs 87, 88 are axially supported in the region of the slot against the differential carrier, wherein a support portion 94 located axially away from the flange 56 is formed by a radius.
• the embodiment shown in Figure 11 largely corresponds to that of Figures 7 to 10.
• the present embodiment is characterized in that the differential carrier 103 has a mounting opening 116 and a diametrically opposite bore 124.
• the sowel- lenzier 119, 120 and the differential gears 108 are inserted through the one mounting hole 116 in the differential carrier 103.
• the first pin part 122 is designed in one piece and is inserted with its first pin 117 into the bore 124 and connected integrally with its second pin 118 to the bearing disk 137.
• the bearing plate 137 is held without play in the mounting hole 116.
• the differential arrangement shown in Figure 12 also largely corresponds in structure to that of Figures 7 to 10.
• the difference is only in the design of the spider assembly 157.
• the second pin member 173 includes a ring member having a coaxial with the axis of rotation A through hole 196 whose diameter is selected so that the side shafts can dive into it.
• the ring member has a solid wall and supported with its sleeve portions 179, the first cylindrical pin member 172 relatively far from the outside, so that a high torsional rigidity results.
• the first pin member 172 has a central portion 197 of reduced diameter so that there is a reduced axial extent with respect to the axis of rotation A.
• the side shafts can thus immerse in the through hole 196 of the second pin member 173 and the recess 197 of the first pin member 172, so that a short axial length is achieved.
• the differential arrangement shown in Fig. 13 is similar to the embodiment of Figs. 7 to 10, and therefore, in view of the similarities, the above description is referred to.
• components corresponding to one another are provided with reference numerals increased by 150 relative to the embodiment shown in FIGS. 7 to 10.
• the only difference is that the first and second pins 217, 218 are made separately. At their inner ends they are inserted into the through hole 221 of the second pin member 223 and axially fixed by means of retaining rings 236 with respect to this.
• the first and second pins 217, 218 are integrally formed with the respective bearing disk 237, 238.
• the bearing discs 237, 238 sit in the two mutually in the shell portion 226 diametrically opposite mounting holes 216 a backlash.
• the differential arrangement shown in Figure 14 largely corresponds to the embodiment of Figure 12, to the description of which reference is made. Corresponding components are increased by 100 compared to this. The only difference is in the design of the first and second pins 267, 268, which are carried out here separately from each other. These are inserted with their inner ends in the holes 271 of the second pin member 273 and axially held by means of retaining rings. In this case, the retaining rings engage in the central opening 296 and prevent the pins 267, 268 migrate to the outside. At their outer ends of the first and the second pin 267, 268 are integrally formed with the bearing discs 287, 288, which sit in the assembly openings 266 in the circumferential direction without play.
• FIGS. 15 to 17 will be described together below.
• the differential arrangement shown corresponds largely to a combination of nation of the first two embodiments.
• the present embodiment is characterized in that both the first pin member 322 and the second pin member 323, which together form the spider assembly 307, are directly connected to the differential carrier 303, wherein a circumferential torque from the differential carrier 303 in the pins 317, 318, 319, 320 is initiated.
• the first pin member 322 is held in bores 324, 325 in the shell portion.
• the second pin member 323 is received with its pins 319, 320 in bearing discs 337, 338, which in turn are seated in the mounting holes 316.
• the bearing discs 337, 338 are axially secured to the pins 319, 320 by means of retaining rings 336.
• the mounting holes 316 in the differential carrier 303 are modified in that the first surface 339 is formed by a semicircle whose radius corresponds to the radius of the bearing disks 337, 338.
• the bearing discs 337, 338 are supported flat in this area against the differential carrier 303, resulting in a higher rigidity.
• the slot-like second surface 340 of the mounting holes 316 is formed on its side remote from the flange 306 by three radii and has a central support portion 347.
• the radius of this support portion 347 corresponds to the radius of the bearing discs 337, 338, so that it rests flat against the differential carrier 303 ,
• FIGS. 18 to 20 show a further exemplary embodiment and will be described jointly below.
• the differential arrangement shown largely corresponds to that of Figures 15 to 17.
• the third and fourth pins 369, 370 are made separately from each other and are connected at their inner ends to the first pin member 372.
• the third and fourth pins 369, 370 have at their inner ends in each case a plug projection 398, 399, with which they are inserted into a central through-bore 400 of the first pin member 372.
• Figure 21 shows a similar embodiment as in Figure 14, the description of which reference is made.
• the reference numbers of corresponding components are again increased by 50.
• all four pins 417, 418, 419, 420 are connected in the circumferential direction with the differential carrier 403, so that a torque is transmitted to them.
• the first and the second pin 417, 418 form a common cylindrical first pin member 422, that in diametrically opposite holes 424, 425 of the differential carrier 403 is inserted.
• the third and fourth pins 419, 420 are designed separately and inserted with their inner ends in a support member 423.
• the carrier element 423 is designed substantially annular and has an axis of rotation coaxial opening 446 and four radial holes 421.
• the holes 421 lie on a common axis, wherein the first pin part 422 is inserted into a first pair of holes and the third and fourth pin 419, 420 in the transverse thereto bores.
• the third and fourth pins 419, 420 are each formed integrally with the associated bearing plate 437, 438, which are seated without clearance in the mounting holes 416
• FIGS. 1 to 6 corresponds largely to the embodiment described in FIGS. 1 to 6, to the description of which reference is made to the extent of similarities.
• Corresponding components are provided with reference numerals increased by 450.
• the differential arrangement shown here is designed in the form of a bevel gear differential instead of a Kronenraddifferentials. It can be seen that the differential gears 458 and the side shaft gears 459, 460 are designed in the form of bevel gears. The mounting holes are in a different cutting plane and are therefore not visible here.
• the spider assembly 457 largely corresponds to that of FIG. 2. It is understood that the inventive concept does not refer to that shown Bevel gear is limited. Rather, other features of the crown gear differentials described above could be transferred to a bevel gear differential, without departing from the spirit of the invention.

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• Engineering & Computer Science (AREA)
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• 2005
  • 2005-08-08 DE DE102005037397A patent/DE102005037397B4/de not_active Expired - Fee Related
  • 2005-08-08 DE DE202005021401U patent/DE202005021401U1/de not_active Expired - Lifetime
• 2006
  • 2006-07-22 CN CNA200680037253XA patent/CN101283202A/zh active Pending
  • 2006-07-22 US US12/063,431 patent/US20100093483A1/en not_active Abandoned
  • 2006-07-22 JP JP2008525420A patent/JP2009505002A/ja active Pending
  • 2006-07-22 WO PCT/EP2006/007227 patent/WO2007017079A1/de not_active Ceased

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