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
  • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
  • F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
  • F16H29/16—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members
  • F16H29/18—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members in which the intermittently-driving members slide along approximately radial guides while rotating with one of the rotary members
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T74/00—Machine element or mechanism
  • Y10T74/15—Intermittent grip type mechanical movement
  • Y10T74/1503—Rotary to intermittent unidirectional motion

Definitions

• the invention relates to a satellite transmission with a drive and an output element, which enable different speed ratios by moving into any mutually concentric or eccentric positions and one of which is designed as an annular disc with a circumferential groove and the other as a star body with radial grooves, and with satellites be coupled on the ring disc and transmit the torque into the star body using transmission pins.
• a non-uniformity in the torque transmission is at least partially compensated for by varying the radii determined by the load curve and / or the effective tangential components by means of a cyclical control.
• the coupling tion elements attached to the circumference of the drive element and can occupy different running radii on the driven side by radial grooves provided there.
• the coupling elements are brought into engagement by means of various, direction-switched force and / or form-fitting effects in such a way that that coupling element always takes over the torque that leads to the highest angular velocity in the output element.
• the clamping elements can also have contact bodies with a non-circular cross-section, with a surface section of the contact body with its radius of curvature being approximately matched to the surface curvature of the ring groove wall of the ring disk, with which the surface sections of the contact bodies mentioned in the torque-transmitting position provide a frictional, flat contact form, so that the Hertzian pressure is minimized, the ratio of the radii should be between 0.6 and 1.4.
• the different radii which cause the translation fluctuations are due to the fact that the satellite on the one hand rotates on the circumference of the annular disc, but on the other hand is connected to the star body in the form of the radial groove.
• the transmission pin therefore executes a radial sliding movement within the load curve, that is to say in the locked state of the satellite, and thus changes the effective radius of the translation.
• the gearbox is installed in such a way that the torque is transmitted from the ring disk to the star body (a star disk)
• the effective radius in the star disk is in principle smaller than the running radius in the ring disk, since satellite gears are always fast, i.e. to higher speeds, and the ratio of the effective radii determines the gear ratio.
• the transmission pin within the load curve at a certain one
• a compensation in the drive radius means that the mentioned change of 1 mm on the drive radius is only noticeable with 5%, which would halve the negative influence of the relative change in radius. Similar considerations apply to the angular deviation of the circumferential forces. Without going into the kinematics in detail, it follows that the non-uniformity can be considerably reduced if the radius compensation takes place in relation to the circumferential path of the drive and not to the circumferential path of the output.
• each satellite in order to reduce or eliminate non-uniformities by varying the effective radii determined by the load arc, each satellite has a radial groove in which the transmission pin can be guided within the load arc at least substantially relative to the center of the ring disk.
• the radial groove is preferably designed such that at least essentially no movement of the transmission pin in the direction of the center of the star body is possible.
• the radial grooves of the satellites are so long that the total compensation path can run in these radial grooves both in the load curve and in the empty curve.
• the star disk is a disk with fixed transmission pins that slide radially in the grooves on the satellite and transmit the torque in the circumferential direction.
• the radial groove of the satellites is only so long that the compensation within the load arc is achieved by a sliding movement in this radial groove and the glide path takes place within the empty arc in grooves in the star disk or in coupling elements or other similar known transmission elements.
• the transmission pin slides more easily in the grooves of the star body in the empty arc, that is to say when the load-free path is traveled, than in the radial grooves, so that the sliding movement in the empty arc in the grooves of the star body and in the load arc in the grooves of the satellites.
• the diameter of the transmission pin is preferably larger in the part which is guided in the groove of the star body than in the part which is guided in the radial groove of the satellite.
• the transmission pin is preferably held at one end via a spring in the groove of the satellite in the empty sheet such that this groove has a sufficiently clear path for radial compensation in the load sheet.
• the resilience causes the transmission pin to slide within the blank in the star disk groove, since the resilience initially prevents it from moving in the satellite only prevents.
• the circumferential force increases suddenly, so that the satellite engages and transmits the applied torque.
• the sliding movement of the transmission pin in the star disk now experiences increased friction, whereby this effect can be enhanced by suitable design between the pin and the slot, so that the sliding resistance in the slot of the satellite becomes lower than in the star disk.
• one or each sliding block can be arranged between the transmission pin and the radial groove of the satellites or the star disk, which converts the Hertzian pressure into a full-surface contact.
• Suitable sliding blocks are described for example in EP 1 003 984 B1.
• the radial grooves in the star disk can also have a stop which defines a variably adjustable minimum radius for each transmission ratio and thus forces the transmission pin to use the radial groove on the satellite within the load curve for geometric compensation.
• the radial grooves of the star body can also be provided on separate radial guides which can execute a relative movement on a disk.
• the radial guides are preferably freely suspended in rotation.
• the movement of the radial guides is preferably controlled via a groove 31 of the ring body, the position of which is fixed relative to the eccentric displacement movement for the transmission control.
• the satellites have the toothing known in principle from DE 199 56 643 A1, which positively engages in the load path in a corresponding toothing of the ring disk designed as a ring gear, the satellite in each case during the transition from the idle path to the load arch and vice versa Pivots.
• the torque acting on the satellite in the worst possible position of the satellite and with the poorest lubrication must always be greater than the frictional torque, which results from the frictional force and the distance that the first intermeshing tooth pair of the axis of rotation of the satellite.
• FIG. 1b is a sectional view taken along line A-A in Fig. 1,
• Fig. 1 d is a detailed view of the detail C in Fig. 1 b and
• a further possibility of minimizing non-uniformities is achieved in that the radial grooves of the star disk are individually fixed to the disk in such a way that they can carry out a rotational movement and also a combined rotational-translational movement.
• This movement is controlled by a guide pin, which rotates in a cam-shaped circumferential groove, which is fixed on a fixed disc.
• the radial grooves thus always carry out the described movement at a fixed position in relation to the eccentricity, e.g. always starting at the load sheet entry and ending at or close to the load sheet exit, so that with a suitable contour of the cam groove a reduction in the non-uniformity is achieved.
• FIG. 4 shows a satellite 15 with a specific profile of a toothing 17 which is adapted to the toothing 11 of an annular disk.
• the illustration shows the transition from the empty sheet to the load sheet, in which the satellite 15 executes a pivoting movement according to arrow 22.
• the circumferential force U shown acts in the direction of the arrow on the satellite 15 via the eccentric transmission pin 21.
• the tooth force Z acts in the opposite direction via the contact of the toothing 17 of the satellite with the toothing 11 of the annular disk, so that the satellite 15 rotates in the direction of the arrow.
• the condition for secure locking is met when the torque from the pair of forces U and Z is greater than the frictional torque M r under all conditions, that is to say in the most unfavorable position of the satellite 15 and with the poorest lubrication.
• the satellite only takes up the full circumferential force when it is in full mesh (teeth 11, 17) and can never be loaded on the tooth tip. Taking into account all forces and torques, i.e.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Friction Gearing (AREA)
• Transmission Devices (AREA)
• Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
• Retarders (AREA)

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Publications (1)

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Cited By (2)

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Citations (3)

Family Cites Families (5)

• 2002
  • 2002-01-18 DE DE10201738A patent/DE10201738A1/de not_active Withdrawn
• 2003
  • 2003-01-15 JP JP2003560406A patent/JP2005515371A/ja active Pending
  • 2003-01-15 CN CNA038016389A patent/CN1596350A/zh active Pending
  • 2003-01-15 US US10/501,615 patent/US20050120816A1/en not_active Abandoned
  • 2003-01-15 DE DE50301670T patent/DE50301670D1/de not_active Expired - Fee Related
  • 2003-01-15 WO PCT/EP2003/000355 patent/WO2003060348A1/de not_active Ceased
  • 2003-01-15 AU AU2003205609A patent/AU2003205609A1/en not_active Abandoned
  • 2003-01-15 AT AT03702446T patent/ATE310187T1/de not_active IP Right Cessation
  • 2003-01-15 EP EP03702446A patent/EP1466110B1/de not_active Expired - Lifetime

Patent Citations (3)

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