EP1606535A1 - Dispositif de transmission - Google Patents

Dispositif de transmission

Info

Publication number
EP1606535A1
EP1606535A1 EP04723162A EP04723162A EP1606535A1 EP 1606535 A1 EP1606535 A1 EP 1606535A1 EP 04723162 A EP04723162 A EP 04723162A EP 04723162 A EP04723162 A EP 04723162A EP 1606535 A1 EP1606535 A1 EP 1606535A1
Authority
EP
European Patent Office
Prior art keywords
gear
axis
planet
power transmission
tracks
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Withdrawn
Application number
EP04723162A
Other languages
German (de)
English (en)
Inventor
Klaus Plath
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE2003114069 external-priority patent/DE10314069A1/de
Application filed by Individual filed Critical Individual
Publication of EP1606535A1 publication Critical patent/EP1606535A1/fr
Withdrawn legal-status Critical Current

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
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers

Definitions

  • the invention relates to a gear device of the type specified in the preamble of claim 1.
  • Gear devices of this type are generally designed as planetary gears (e.g. Johannes Looman “Fundamentals, constructions, applications in vehicles”, 3rd edition, volume 26; Herbert W. Müller “The epicyclic gear”, calculation, application, design, volume No. 28).
  • they In their simple construction, they have a first movable track in the form of the outer circumference of a sun gear, a second movable track in the form of the inner shell of a ring gear surrounding the sun gear and at least one planet gear arranged between these tracks and rotatably mounted on a planet gear carrier (web).
  • the circumference of the planet gear is in operative connection with both the sun gear and the ring gear, which is understood here as, for example, a tooth engagement (gear transmission) or a rolling system (friction gear transmission), and is rotatably supported on a bearing axis, which is also a power transmission axis and can run on a third track arranged between the two tracks.
  • the planet gear is supported and guided by a carrier element between the path which is formed by the outer circumference of the sun gear and the path which is formed by the inner shell of the ring gear.
  • the three orbits are concentric or coaxial circular orbits with fixed distances in planetary gears. However, they can also have a linear or arcuate course, likewise at constant distances from one another and in a parallel arrangement.
  • Gear devices of this type are also referred to as three-shaft gears, in particular as three-shaft planetary gears.
  • three-shaft gear of the type of interest here have no fixed path, d.
  • Sun gear, ring gear, planet gear and power transmission axis are movably mounted, so that two shafts can be used for the drive and one shaft for the output or vice versa two shafts for the output and one shaft for the drive.
  • the power transmission in the area of the carrier element or web takes place in the known transmission devices, regardless of whether this is used as the drive or output element of the transmission, always via the bearing axis located in the center of the planet gear, about which the planet gear is rotatably mounted on the carrier element. Bearing axis and power transmission axis thus coincide. In addition to guiding the planet gear axis, the web therefore also serves to transmit power.
  • the tracks on which the bearing axis and the power transmission axis move have the same constant distance from the center of the sun gear, this distance being equal to the sum of the sun gear and the planet radius. Because of this, the forces transmitted by the planet gear are always divided in half between the sun gear / planet gear and the planet gear / ring gear. There is therefore only one specific point for the force transmission or force dissipation in the area of the planet gear. In addition, the path that is transferred to the hoist gear when the planet gear carrier rotates about the central axis of the planetary gear is always twice as large as the path that the bearing or power transmission axis of the planet gear has describes about the central axis of the planetary gear.
  • the technical problem of the present invention is to design the transmission device of the type described in the introduction in such a way that it is dimensioned more flexibly than before, the power transmission is improved, and a circular or linear path for the power transmission axis can nevertheless be implemented as required.
  • the invention has the advantage that, despite its eccentric and particularly advantageously adjustable arrangement on the bearing axis, the power transmission axis can always be guided on a path that is parallel to the other paths and in particular the path on which the planet carrier is also moved , In addition, there are favorable power transmission ratios, since the power transmission axis can be arranged much closer than before to one of the moving tracks as required.
  • the new gear device thus enables many previously unrealizable constructions as well as the use of smaller or larger planet and hoist gears under otherwise identical conditions.
  • the invention also has the advantage that the eccentrically arranged force axis on the bearing axis of the planet gear describes a path running parallel to the path of the bearing axis.
  • the eccentrically arranged power axis on the bearing axis results in many previously unrealizable designs as well as the use of smaller ring gears and planet gears with the same torque and the same sun gear diameter.
  • Another advantage is that one drive shaft can be driven internally by the transmission itself, as explained in more detail below. This means that no external drive is required, and even a three-shaft epicyclic gearbox can be used as the crank drive, because the third shaft is no longer a disruptive part of the crank movement.
  • the internal drive of this shaft can be coupled to an external drive for this drive shaft, so that the two drive shafts mutually support (supplement) each other in their drive work.
  • the drive does not have to take place solely by an eccentric force axis on the bearing axis, but can also take place directly on the support element by means of a force application.
  • This arrangement has the same radius, seen from the center of the sun gear, as an eccentrically arranged force axis on the bearing axis.
  • Figure 1 is a schematic representation of a conventional planetary gear with three shafts.
  • Figure 2 is a schematic representation of a transmission device according to the invention in the form of a planetary gear with three shafts and an eccentric power transmission axis.
  • Figure 3 is a schematic representation of a composite planetary gear according to the invention with internal and external drive for the outer sun gear.
  • Figure 4 is a schematic representation of a composite planetary gear according to the invention with drive of the inner planet gear via a second ring gear arranged in parallel.
  • Fig. 5 is a schematic representation of a composite planetary gear according to the invention corresponding to Figure 3, but with changed dimensions.
  • FIG. 6 shows a schematic illustration like FIG. 4, but with a changed dimensioning analogous to FIG. 5;
  • Fig. 7 is a schematic cross section through the planetary gear according to Fig. 3;
  • 11 and 12 each show a schematic front view of drive options for the planetary gear according to the invention.
  • FIG. 13 and 14 are schematic front views of one application form of the planetary gear according to the invention as a crank mechanism
  • Fig. 15 and 16 training forms of the bearing axis and the bearing of the planet gear
  • FIG. 17 shows a schematic illustration of a transmission according to the invention which is used in an elevator where a second moving path is realized by a rotating chain or toothed belt;
  • Fig. 18 is a schematic representation of a transmission according to the invention as in Fig. 17 with a special feature that the drive for the gear is carried out on the carrier element of the gear;
  • Fig. 19 is a schematic representation of a transmission according to the invention where the second movable path is realized in that a rack is driven by a gear with a motor;
  • Fig. 20 is a schematic representation of a transmission according to the invention as in Fig. 19 with the special feature that the drive for the gear on the carrier element of the 2004/085880
  • a conventional gear device in the form of a three-shaft planetary gear includes a sun gear 1, a ring gear 2 and at least one planet gear 3.
  • the ring gear 2 is connected to a first, outwardly and e.g. Shaped as a hollow shaft A and rotatably mounted about a central axis 4 of the planetary gear.
  • the sun gear 1 is e.g. B. provided with an external toothing, which forms a first movable, substantially circular path, while the ring gear 2 z. B. is provided with an internal toothing which forms a second, substantially circular and also movably mounted path, which is arranged coaxially and parallel to the first path and surrounds it with a preselected distance.
  • the planet gear 3 is arranged between the two tracks so that it is operatively connected to the two tracks at substantially diametrically opposite locations, e.g. is provided with an external toothing which meshes with the toothing of the two tracks of the sun gear 1 and ring gear 2.
  • the planetary gear also has, for each planet gear 3, a bearing axis 5, only shown schematically, which is attached to a planet gear carrier or web 6 and is arranged at a distance parallel to the center axis 4.
  • the bearing axis 5 or the bearing connected to it serve for the rotatable mounting of the planet gear 3.
  • the planet gear carrier 6 supports the bearing axis 5 expediently on both sides of the planet gear 3 with arms 6a, 6b which are rotatably mounted about the central axis 4, at least one arm (e.g. 6b) can be rotated by a second shaft B.
  • the sun gear 1 is also connected to a third shaft C, e.g. is rotatably supported in the first shaft A.
  • the bearing axis 5 which generally has a small diameter, is at the same time a force transmission axis which is the 2004/085880
  • Circular movement of the carrier 6 or the force acting on the bearing axis 5 of the planet gear 3 converts into a corresponding rotary movement of the ring gear 2.
  • the central axis 8 of the planet gear 3, which is coaxial with the bearing axis 5, is at the same time its axis of rotation, about which it executes a rotational movement when the sun gear 1 orbits.
  • a special feature of the planetary gear described is that when the shaft B is driven, the orbital movement of the ring gear 2 can be influenced by simultaneously rotating the sun gear 1 by means of the shaft A in one or the other direction.
  • the shaft A takes over the power transmission from or to the ring gear 2 and the shaft C takes over the power transmission from or to the sun gear 1, while the shaft B the force introduced or the force derived via the web 6b onto the axis 5 of the Planetary gear 3 transmits.
  • the carrier element 6a which can be designed as a ring or arm, takes over the supporting and guiding function of the planet gear 3 between the moving path of the sun gear 1 and the moving path of the ring gear 2. This guidance takes place via a connection of the rotatably mounted carrier element 6a (Arm) to the axis 8.
  • the planet gear 3 is rotatably supported on the bearing axis 5.
  • the Carrier arm 6a and the web 6b both form a connection between the central axis 8 of the planet gear 3 and a central axis 4 of the transmission.
  • the two connections of the support arm 6a and the web 6b between the central axis 8 of the planet gear 3 and the central axis 4 always result in the same (identical) distances for both connections.
  • the central axis 8 of the planet gear 3 and the central axis of the bearing axis 5 and the central axis of the power transmission axis are identical in their position and are parallel to the central axis 4 of the sun gear 1.
  • the axis center of the input and output shafts A, B and C is identical in position to the central axis 4 of the sun gear 1.
  • a disadvantage of the arrangement described is that the forces introduced in the center of the planetary gear (central axis 8) are always divided equally between the two operative connections planetary gear / ring gear and planetary gear / sun gear.
  • Another disadvantage is that the gear design always has three shafts, i.e. For each part to be driven or driven (sun gear, planet gear and ring gear) one shaft is required, which can be driven or driven as an input or output shaft from outside the gearbox. These shafts are connected to a drive motor or a part to be driven outside the gearbox.
  • the sun gear 1 and the ring gear 2 are designed as in FIG. 1.
  • the outer circumference of at least one planet gear 9 also corresponds to that of the planet gear 3 in FIG. 1.
  • the planetary gear according to FIG. 2 differs in two essential features 2004/085880
  • a first distinguishing feature is that the planet gear 6 for each planet gear 9 has a hatched axis 10 shown in Fig. 2, the outer diameter of which is only slightly smaller than the outer diameter of the planet gear 9 and is preferably larger than corresponds to half the outer diameter of the planet gear 9.
  • the planet gear 9 is designed as a ring and e.g. by means of a bearing 11, which may be designed as a ball, needle or roller bearing or the like, rotatably mounted on the bearing axis 10.
  • a second distinguishing feature is that a force transmission axis 12, which is arranged parallel to the central axis 4 of the transmission and which is arranged eccentrically to the central axis 8 of the planetary gear 9 and on the bearing axis 10, is used for the introduction or force transmission.
  • This central axis 8 corresponds to the central axis 8 in FIG. 1 and is also the axis of rotation about which the planet gear 9 can rotate on the bearing axis 10.
  • the power transmission axis 12 is e.g. connected to the drive shaft B via a lever arm 15 or the like.
  • the carrier 6, which can be rotated about the central axis 4 of the planetary gear thus serves only to receive or fasten the bearing axis 10
  • the force transmission axis 12 serves as a drive or output element via the lever arm 15, via which forces are introduced or discharged . It is important here that the power transmission axis 12 is parallel to the central axis 4 and, when moving, describes a path concentric with the other paths with a constant radius or distance from the central axis 4.
  • Binding is dependent on the respective distance of the eccentricity of the power transmission axis 12 from the central axis 8 of the planet gear 9.
  • the relieved operative connection in FIG. 2 the operative connection planetary gear 9 / sun gear 1 should then be used increasingly as a drive for the output of shaft C, which leads to the transmission from outside.
  • Fig. 3 shows a composite epicyclic gear, which is also referred to as a planetary gear coupling gear. 2, which are arranged coaxially one behind the other, the first planetary gear being the same as that of FIG. 2, while the second planetary gear comprises a sun gear 21, a ring gear 22, at least one planet gear 23 and a bearing axle 24 therefor having.
  • a power transmission axis 25 of the second planetary gear is arranged eccentrically on the bearing axis 24 in accordance with FIG. 2, but in contrast to FIG. 2 but in the vicinity of the operative connection of the planet gear 23 / sun gear 21.
  • the side of the relieved operative connection from the first planet gear 3 thus lies on the side of the loaded operative connection from the planet gear 23 and vice versa.
  • This type of arrangement of the eccentric power axes to each other has the advantage that the respective relieved side of the planet gear (as seen from the center of the planet gear axis) is driven by the more heavily loaded side of the other planet gear. 2004/085880
  • the two planetary gears are coupled in that the bearing axis 10 of the first gear is connected to the ring gear 22 of the second gear via a coupling element 26.
  • the coupling element 26 is rotatably mounted with a hollow shaft AI on the shaft C, which here firmly and coaxially connects the two sun gears 1, 21.
  • the shaft C is also passed through the sun gear 21 and ends as a freely accessible shaft C1.
  • the shaft A provided on the ring gear 2 is guided in FIG. 3 over the second planetary gear and in turn is partially designed as a hollow shaft, which rotatably receives the shaft Cl here.
  • a coaxial shaft B1 is also provided coaxially between the shafts Cl and A, which is connected to the bearing axis 24 via the force transmission axis 25 and is also guided outwards from the transmission.
  • the shaft Bl is stationary, e.g. is firmly connected to a gear housing, as indicated schematically in Fig. 3.
  • the planet gear 3 and the ring gear 2 are carried along by the power transmission axis 12.
  • the ring gear 2 drives the second ring gear 22 with the same direction of rotation via the coupling element 26.
  • the ring gear 22 tries to take the second bearing axis 24 with it.
  • the second planet gear 23 transmits the movement of the ring gear 22 to the second sun gear 21 and rotates it in the opposite direction. Since the sun gear 21 is fixedly connected to the first sun gear 1, it is therefore also driven with a direction of rotation which is opposite to that of the drive shaft B.
  • the type of drive in FIG. 3 could be referred to as an internal sun gear drive, since an external drive for the sun gear 1 is no longer required.
  • the outward shaft Cl is therefore superfluous in this application and is used to support the sun gear 21.
  • FIG. 4 corresponds to that of FIG. 3 except for the difference that the second ring gear 22 is driven directly by means of a coupling element 27 from the first ring gear 2. Since the shaft B1 is again held firmly, the ring gear 22 transmits its movement via the rotating planet gear 23 to the sun gear 21 with the opposite direction of rotation. The connection of the bearing axis 10 to the ring gear 22 is omitted here.
  • the position or arrangement of the tooth engagement should preferably be chosen so that the two tooth engagements of the planet gears 9 and 23 to the ring gear 2 and 22 are identical to the central axis of eccentrically arranged pins 28 on a lever arm 29 (identified by the dashed 30 line in FIG. 3). Furthermore, the position (arrangement) of the central axis of the eccentrically arranged power axis 25 on the bearing axis 24 should be identical to the position of the active connection sun gear 1 / planet gear 9 (identified in FIG. 3 by a broken line 31). Both forms of arrangement are indicated in FIGS. 3 and 4 by the dashed lines 30 and 31.
  • FIG. 5 corresponds in its basic structure to FIG. 3 Fig. 5, the outer diameter of the sun gear 1 and the planet gear 9 and the outer diameter of the bearing axis 10 of the planet gear 9.
  • the eccentric position of the power transmission axis 25 on the bearing axis 24 was changed to a central position on the bearing axis 24.
  • the central power transmission axis 25 here also has a U-shaped arm 32 which extends as far as the operative connection of planet gear 9 / ring gear 2 or planet gear 23 / ring gear 22 (identified in FIG. 5 by a broken line 33).
  • the central axis of the power transmission axis 25 on the bearing axis 24 has the same distance (radius) from the central axis 4 as the operative connection from the first planet gear 9 to the first sun gear 1 (dashed line 34 in FIG. 5).
  • An internal drive of the first sun gear 1 as in FIG. 3 is also possible in FIG. 5.
  • the bearing axis 24 of the second planetary gear 23 can, depending on the desired translation, be arranged rotatably or held in place, which also applies to FIGS. 3 and 4.
  • FIG. 6 corresponds to FIG. 4 except for the differences that the first planet gear 9 has a smaller diameter and the second power transmission axis 24 has the U-shaped arm 32 according to FIG. 5.
  • Fig. 7 shows schematically the assembled transmission according to Figs. 3 and 4 from the front end, i.e. 3 from the left.
  • the eccentrically arranged force axes 12 and 25 on the two bearing axes 10 to 24 are offset (opposite one another), as described in FIGS. 3 and 4.
  • Figure 7 shows the direction of rotation of the first and second sun gears 1, 21 and the direction of rotation of the ring gears 2, 22 and the direction of rotation of the first and second planet gears 9 and 23 respectively.
  • the two arrowheads on the two power axes 12, 25 are the Direction of the opposite force of the two can be seen.
  • axes 12, 25 is determined by the position of the arrangement of the eccentric power axis on the bearing axis of the planet gear.
  • the position of the eccentricity on the bearing axis determines the direction of the force on the force axis.
  • the direction of the force acting on the force axis 12 is equal to the direction of rotation of the ring gear 2. If the force axis 25 moves in the direction of the sun gear 21, the direction of the force acting on the force axis 25 is the same as the direction of rotation of the sun gear 21.
  • the two paths of the force axes 12 and 25 can be recognized by the dashed line 30a, which each run through the central axis of the two force axes 12 and 25 and lie parallel to one another.
  • the force acting on the radius of the operative connection of the planet wheel / sun wheel is realized by an extended arm 29 with a pin 28 attached.
  • the central axis of the second force axis 25 on the second bearing axis 24 of the planet gear 23 is exactly on the radius of the operative connection of the first sun gear 1 / first planet gear 9 (identified by the broken line 31 as described in FIGS. 3 and 4).
  • FIG. 8 shows a planet gear 9 with an enlarged bearing axis 10 and the different possible variations of the eccentrically arranged power transmission axis 12 on the bearing axis 10.
  • the force transmission axis 12 can also be arranged displaceably on the bearing axis 10.
  • the power transmission axis 12 can be technically realized, for example, by the central axis of a pin projecting perpendicularly from the bearing axis 10. After one Particularly preferred embodiment of the invention, this pin, as indicated in Fig. 8, is slidably mounted along a diameter on the bearing axis 10, so that the power transmission axis 12 more or less as required from the axis of rotation 8 (Fig. 2) of the planet gear 9 arranged remotely and in a variety of possible positions (eg 12a, 12b, 12c or 12d) can be brought.
  • a pin that realizes the force transmission axis 12 can be displaced in a diametrically extending groove of the bearing axis 10 and can be fixed with a clamping screw or the like.
  • the power transmission axis 12 is of course set to a predetermined fixed distance from the axis of rotation 8.
  • FIG. 9 shows a conventional three-shaft planetary gear (as described in FIG. 1) with an output element 36 rolling on the outer circumference of the ring gear 2.
  • the forces introduced in the center of the axis of the planet gear 3 are each divided Half on the operative connection planet gear / sun gear and planet gear / ring gear. This results in the following distribution of forces on the planet gear.
  • the force F2 is twice as large as the opposite force Fl at the external operative connection of the planet gear 3 / ring gear 2 or ring gear 2 / output element 36 are movably or rotatably mounted, would have to be applied to the assumed static balance with a correspondingly large force on the sun gear or ring gear (counterforce).
  • the transmission shown in FIG. 9 has only a single point of force introduction on the bearing axis 5 in the center of the planet gear 3. This point is identical to the central axis of the bearing axis 5. It is also important in this context that the size of the sun gear 1 and the ring gear 2 is determined by the diameter of the planet gear 3 and is therefore unchangeable by the determination of the introduction of force in the axis center of the planet gear 3.
  • the outer circumference of the sun gear 1 is in the example 004/085880
  • the inner shell of the ring gear 2 is 282.6 mm.
  • the outer diameter of the planet gear 3 is 94.2 mm.
  • the outer diameter of the driven element 36 is 94.2 mm.
  • the length of the path of the central axis of the power axis and the bearing axis 5 with one revolution around the sun gear 1 is 188.4 mm.
  • a rotation of the planet gear 3 around the sun gear 1 and at the same time a rotation of the sun gear 1 in the opposite direction of rotation of the ring gear 2 results in a transmission ratio of 1: 5 on the output element 36.
  • FIG. 10 shows a three-shaft planetary gear transmission according to the invention as described in FIG. 2 with one change: the ring gear 2 drives an output element 37 on its outer circumference.
  • the eccentric force axis 12 on the bearing axis 10 was placed on the radius of the operative connection of the planet gear / ring gear / output element.
  • the outer circumference of the sun gear 1 is 94.2 mm.
  • the inner shell of the ring gear 2 is 188.4 mm.
  • the outer diameter of the planet gear 9 is 47.1 mm.
  • the outer diameter of the driven element 37 is 94.2 mm.
  • the length of the path of the central axis of the force axis 12 with one revolution around the sun gear 1 is 188.4 mm.
  • Fig. 11 shows an inventive three-shaft planetary gear with two 2004/085880
  • Opposite planet gears 9 The two eccentrically arranged power transmission axles 12 on the two bearing axles 10 are connected to one another by means of a connecting part 38 via the center of the sun gear 3.
  • the connecting part 38 has in the center of the sun gear 1 a shaft 39 for driving or driving the two planet gears 9.
  • the shaft 39 is arranged axially parallel to the force axes 12 of the planet gears 9.
  • the direction of rotation of the drive shaft 39 is opposite to the direction of rotation of the sun gear 1.
  • the dashed line 40 shows the path of the central axes of the power transmission axes 12 running parallel to the ring gear 2 and sun gear 1.
  • FIG. 12 shows a three-shaft planetary gear transmission according to the invention as in FIG. 11 with the special feature that the power transmission axes 12 are no longer arranged on the bearing axes 10.
  • the power transmission axes 12 are located directly on the carrier element 6 for the planet gears 9 according to FIG. 2 (ring, arm or other shapes), but nevertheless on the same radius (dashed line 41), as described in FIG. 11. They are arranged axially parallel to the central axis of the sun gear 1.
  • the power transmission axes 12 are fastened on the same radius of the respective eccentricity as in FIG. 11 on the carrier element 6.
  • a corresponding arrangement of the power transmission axis 12 on the planet gear carrier 6 can be provided in FIG. 2.
  • Fig. 13 shows a three-shaft planetary gear according to the invention, which is used as a crank mechanism for an internal combustion engine.
  • the eccentrically arranged power transmission axis 12 on the bearing axis 10 is designed as a crank pin 42 and connected to a connecting rod 43.
  • This connecting rod 43 has at its other end a connection to a piston 44 which moves back and forth in a bushing 45.
  • the force axis 42 on the bearing axis 10 moves with its central axis on the dashed line or path 46 and runs parallel to the path of the sun gear 1 and the ring gear 2.
  • the planet gear 9 is driven by a drive element 47 on the ring gear 2 and the piston then operates as a pump or compressor. critical 2004/085880
  • FIG. 14 shows a three-shaft planetary gear transmission according to the invention with a modification of FIG. 13.
  • the crank pin 42 is not arranged on the bearing axis 10 of the planet gear 9, but is offset directly on the carrier element 6 and preferably by 180 ° with respect to FIG. 13.
  • crank pin 42 with its axis center is on the same radius as in FIG. 13, and its path (dashed line 48), as in the other exemplary embodiments, runs at a constant distance and parallel to the path of the sun gear 1 and the ring gear 2.
  • FIG. 16 shows a bearing axis 50 in a combination of cross and rod shape, on which the planet gear 9 is rotatably arranged by roller bearings 51.
  • Fig. 17 shows a first, linearly movable web 61, which can be interpreted as a development of the outer circumference of the sun gear 1 according to FIG. 2. It is parallel and at a distance from a second, also linearly movable track 62, which can be understood as a development of the inner circumference of the ring gear 2 according to FIG. 2.
  • a planet gear 63 is arranged between the two tracks 61, 62, the circumference of which is on the one hand at a point 64 with the movable track 61 and, on the other hand, is operatively connected to the movable track 62 at a diametrically opposite point 65.
  • the planet gear 63 is designed as a narrow ring which is rotatably mounted on a bearing axis 67 by means of a bearing 66, the outer diameter of which is preferably only slightly smaller than the outer diameter of the planet gear 63.
  • a central axis 68 of the bearing axis 67 is at the same time the axis of rotation of the planet gear 63.
  • the bearing axis 67 can be fastened to a support (not shown in detail) which is displaceably mounted parallel to the tracks 61, 62.
  • the bearing axis 67 is also provided with an eccentrically arranged to the central or rotational axis 68 of the planet gear 63, power transmission axis 69 which, for. B. is realized as a pin which protrudes perpendicularly from the bearing axis 67 formed as a circular disc.
  • a guide element 70 which is displaceable parallel to the tracks 61, 62 and which is coupled to the force transmission axis 69 or the pin and which is displaceably mounted in corresponding bearings 71, is used for driving or driving.
  • the linear movement initiated with the guide element 70 can be converted into a rotary movement by means of a wheel 72 which is operatively connected to the outside of the movable track 62, and conversely the rotary movement of the wheel 72 can also be converted into a linear movement of the guide element 70.
  • a wheel 72 which is operatively connected to the outside of the movable track 62
  • the rotary movement of the wheel 72 can also be converted into a linear movement of the guide element 70.
  • the guide element 70 is designed and guided by means of the bearings 71 in such a way that on the one hand it can only be moved parallel to the tracks 61, 62, on the other hand the force transmission from the guide element 70 to the bearing axis 67 or vice versa takes place in the region of the force transmission axis 69 the force direction parallel to the tracks 61, 62 runs through the force transmission axis 69. Therefore, the guide element 70 and the bearing axis 67 could also be produced in one piece without the formation of a bearing journal. So that no undesirable leverage effects are obtained between the guide element 70 and the bearing axis 67 or the bearing journal 69, its central axis is expediently exactly on a dashed line 70a, along which the guide 2004/085880
  • the web 61 is z. B. formed by an encircling chain 73 which is connected to the planet or Gear 63 forms the operative connection 64.
  • the guide element 70 consists of any guide part which is supported by the bearings 71, e.g. B. roles held and z. B. is attached to the bearing axis 67.
  • the web 61 can be moved back and forth in the direction of the arrow with the aid of a gear 74 which is at least partially wrapped around by the web 61.
  • the active connection 64 defines the unloaded side.
  • the power transmission axis 69 also moves parallel between the two movable tracks 61 and 62.
  • the gear 63 with the guide member 70 moves between the two movable tracks 61 and 62, whereby the gear 63 between the two movable tracks 61 and 62 is rotated and moved.
  • the gear 63 rolls over the second movable path 61, the drive of the second movable path 61 always running counter to the displacement of the gear 63.
  • the drive on the gear 63 via the first movable track 62 always has the same direction as the displacement of the gear 63 on the guide element 70.
  • the arrangement of the eccentric force axis 69 on the bearing axis 67 is always such that it is as far as possible on the first Movable track 62 (output track) sits.
  • a displacement of the eccentric force axis 69 onto the operative connection 65 between the gear 63 and the first movable track 62 (driven track) is possible by means of a
  • Lever arm possible which is arranged on the bearing shaft 67 or on the guide element 70 and has a bolt for the introduction of force.
  • the arrangement of the eccentric power transmission axis 69 on the center line 70a of FIG. 17 has proven to be advantageous because it reduces additional disadvantageous leverage effects that exist between the gear 63 on the bearing axis 67 and the guide part 70. In other words, by a staggered arrangement between the eccentric force axis 2004/085880
  • the drive in FIG. 17 thus takes place on the one hand via the eccentric force axis 69 on the bearing axis 67 and on the other hand via the second movable track 61, which is formed by the rotating chain 73.
  • the drive takes place via the first movable track 62, which is formed by the rack 75.
  • FIG. 18 corresponds to FIG. 17 with a modification: a power transmission axis 81 is arranged on the guide part 70 on the center line 70a.
  • the second movable path 61 in FIG. 19 is realized by a rack 83 , which is mutually driven by a gear 84.
  • the drive always takes place in the opposite direction to the displacement of the guide part 70 with the bearing axis 67 and the gear 63.
  • the output on the gear 63 via the first movable track 62 is a revolving chain 85 which is held and guided by guide rollers 86 and 87.
  • the revolving chain 85 drives a gearwheel with cable winch 87, on which a cable 88 is arranged, which serves to raise and lower a weight 89.
  • the drive in FIG. 19 thus takes place on the one hand via the eccentric force axis 69 on the bearing axis 67 and on the other hand through the second movable track 61 which is formed by the rack 83.
  • the output takes place via the first movable track 62, which is formed by the revolving chain 85 becomes.
  • FIG. 20 corresponds to FIG. 19 with a modification: a force transmission axis 90 is arranged on the center line 70a of the guide element 70.
  • the second moving track 62 is formed by a gear wheel, which both can be movable as well as fixed or held.
  • This gearwheel engages with gearwheel 63 and rotates in the opposite direction of the displacement of gearwheel 63.
  • the drive gearwheel runs in a guide rail next to gearwheel 63 and drives it.
  • the drive gear and the gear 63 are fixed.
  • the invention is not restricted to the exemplary embodiments described, which can be modified in many ways. This applies in particular to the dimensions and relative arrangements of the different parts that are given by way of example.
  • the planetary gear can, for example, also be equipped with more than one or two planet gears.
  • the bearing axis can be designed differently than is indicated in FIGS. 7, 8, 15 and 16. In particular, it is possible to design the bearing axis in several parts. It can be particularly expedient to provide them with two coaxial parts lying axially one behind the other, which are connected to one another by a spring element. Forces acting on one of the parts can be absorbed in a jerky manner before they act on the other part.
  • the ring gear 2 on the outer circumference may also be advantageous to use as a drive or To form the output member, for example, by providing it with a circumferential toothing or the like.
  • the drive or output member can also consist of a plurality of coaxially arranged wheels with different diameters, in particular toothed wheels, in order to enable different transmission ratios in a simple manner.
  • the planet gear carrier 6 can be designed as a lever arm or otherwise instead of as a circular disk, as indicated in FIG. 7. It is also clear that the paths shown in FIGS. 17 to 20 do not have to be exactly straight, but can also run along an arc.
  • These tracks can consist, for example, of racks, chains, rolling surfaces or the like, which are operatively connected to planet wheels in the form of toothed wheels or friction wheels. It is also clear that the power transmission ratios can be improved further in that a crank with a crank arm arranged parallel to the power transmission axis 12 is fastened with the power transmission axis 12 etc. Finally, it goes without saying that the various features can also be used in combinations other than those described and illustrated.

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

Abstract

L'invention concerne un train planétaire comprenant, de façon courante, une roue solaire (1), une couronne de train planétaire (2) et au moins un satellite (9). L'invention est caractérisée en ce que le satellite (9) est monté tournant sur un axe de palier (10) qui est pourvu d'un axe de transfert de force (12) déterminé pour l'introduction ou la dérivation d'une force, agencé excentrique par rapport à l'axe médian dudit satellite (9). L'invention s'applique également à un dispositif de transmission présentant, à la place de la roue solaire et de la couronne (1, 2), deux voies parallèles linéaires (61, 62).
EP04723162A 2003-03-25 2004-03-25 Dispositif de transmission Withdrawn EP1606535A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10314069 2003-03-25
DE2003114069 DE10314069A1 (de) 2003-03-25 2003-03-25 Planetenringgetriebe mit gleich- oder gegeläufigem Sonnenrad
DE102004010654 2004-03-02
DE102004010654 2004-03-02
PCT/DE2004/000643 WO2004085880A1 (fr) 2003-03-25 2004-03-25 Dispositif de transmission

Publications (1)

Publication Number Publication Date
EP1606535A1 true EP1606535A1 (fr) 2005-12-21

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ID=33099297

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04723162A Withdrawn EP1606535A1 (fr) 2003-03-25 2004-03-25 Dispositif de transmission

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US (1) US20060264292A1 (fr)
EP (1) EP1606535A1 (fr)
WO (1) WO2004085880A1 (fr)

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US9879760B2 (en) 2002-11-25 2018-01-30 Delbert Tesar Rotary actuator with shortest force path configuration
DE102004053614A1 (de) 2004-11-03 2006-05-11 Klaus Plath Planetenradgetriebe
DK2232100T3 (da) * 2008-01-12 2013-01-02 Linak As Lineær aktuator
US9862263B2 (en) 2013-03-01 2018-01-09 Delbert Tesar Multi-speed hub drive wheels
US10414271B2 (en) 2013-03-01 2019-09-17 Delbert Tesar Multi-speed hub drive wheels
US9365105B2 (en) 2013-10-11 2016-06-14 Delbert Tesar Gear train and clutch designs for multi-speed hub drives
US10422387B2 (en) 2014-05-16 2019-09-24 Delbert Tesar Quick change interface for low complexity rotary actuator
US9915319B2 (en) 2014-09-29 2018-03-13 Delbert Tesar Compact parallel eccentric rotary actuator
US9657813B2 (en) 2014-06-06 2017-05-23 Delbert Tesar Modified parallel eccentric rotary actuator
US11014658B1 (en) 2015-01-02 2021-05-25 Delbert Tesar Driveline architecture for rotorcraft featuring active response actuators
WO2017221062A1 (fr) * 2016-06-21 2017-12-28 Kkd Getriebebau Ug Dispositif de transmission de force
US10464413B2 (en) 2016-06-24 2019-11-05 Delbert Tesar Electric multi-speed hub drive wheels
CN109386434B (zh) * 2018-11-22 2024-03-26 明阳智慧能源集团股份公司 一种紧凑型半直驱风电齿轮箱多轴功率分流传动结构

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Also Published As

Publication number Publication date
WO2004085880A1 (fr) 2004-10-07
US20060264292A1 (en) 2006-11-23

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