EP3143307A1 - Engrenage différentiel à déverrouillage automatique - Google Patents

Engrenage différentiel à déverrouillage automatique

Info

Publication number
EP3143307A1
EP3143307A1 EP15730243.1A EP15730243A EP3143307A1 EP 3143307 A1 EP3143307 A1 EP 3143307A1 EP 15730243 A EP15730243 A EP 15730243A EP 3143307 A1 EP3143307 A1 EP 3143307A1
Authority
EP
European Patent Office
Prior art keywords
gear
differential
gears
rotary
planetary gear
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Withdrawn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
EP15730243.1A
Other languages
German (de)
English (en)
Inventor
Albrecht Baumann
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
Application filed by Individual filed Critical Individual
Publication of EP3143307A1 publication Critical patent/EP3143307A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears

Definitions

  • the invention is directed to a differential gear similar to the design of a planetary gear for largely power neutral exchange of rotational energy between at least three rotary joints, with at least one planetary gear and at least one sun or ring gear meshing with at least one planetary gear in its axial direction offset three with one each circumferential region each having a different radius, r 2 , r 3 has: nr 2> n ⁇ r 3l r 2 £ r 3 , and wherein with each toothed peripheral region of the / of the planet gears each a sun or ring gear meshes, with each rotatably coupled or connected to a rotary connection of the differential gear, as well as to a method for operating such a differential gear.
  • Differential gears can be operated as a distributor or summing gear, that is, either a rotary joint is driven and two rotary joints each serve as an output and impart rotational movement to different branches, or two rotary joints are driven and one rotary joint serves as an output.
  • differential gears In a bevel gear differential, a plurality of bevel gears are mounted with radially oriented axes in a rotatable about an axis, driven differential carrier, which mesh bevel gears on the two output axes; Also, a planetary gear with a sun gear, a ring gear and one or more planetary gears can be used as a differential; in a spur gear always engage two toothed planetary gears, each of which meshes with another, serving as an output sun gear; the drive is via the planet carrier; furthermore, there are also helical gear, etc.
  • each planet gear meshes with a total of three sun or ring gears, however, with none of the other planetary gears.
  • the different diameter ranges cause each one Sun or ring gear via another gear ratio üi, ü 2 , ü 3 is coupled to a planetary gear: üi ⁇ ü 2 , üi ü 3 , ü 2 ⁇ ü 3 .
  • differential gear create, for example, in motor vehicles as differential one degree of freedom in the coupling of two driven wheels to a common drive shaft by allowing relative speeds between the two driven wheels, which only allows a largely frictionless cornering, yet known to turn the outer wheel slightly faster than the inside of the bend. This can also be interpreted such that the drive shaft always rotates at a medium speed ni, based on the speeds n 2 , n 3 of the two driven wheels.
  • n 2 n ⁇ ⁇ + ⁇
  • n 3 ni - ⁇
  • a typical differential has three discs: the middle, coupled to the drive shaft rotates with ni; rotatably mounted therein rotatable pinions which rotate with ⁇ about their own axes and mesh with teeth on the two lateral discs;
  • ⁇ can be both positive and negative. This means that ⁇ can adapt to the respective circumstances, for example the Turning radius. This is almost always good on dry roads.
  • a generic differential gear has at least one planet - offset in its axial direction - three with each provided with a continuous toothing peripheral regions each having a different radius r- ⁇ , r 2 , r 3 : h ⁇ r 2 , ri ⁇ r 3 , r 2 r 3 , wherein each sun or ring gear meshes with each toothed peripheral region of the / of the planet gears, which is rotatably coupled or connected to a respective rotary connection of the differential gear.
  • a planetary gear always rolls against either all sun or ring gears meshing with it or against no combing sun or ring gear.
  • the transmission states according to the invention mutually largely exclude each other. This means two things: On the one hand occurs - apart from the short transition phases between the two states - in the transmission state "compensation movement” no blockage, even a compensatory movement braking effect is virtually zero, ie, the differential fits an external acting requirement for a compensatory movement On the other hand occurs - apart from the short transition phases between the two states - in the transmission state "blocking" no compensation movement more, ie, the two rotary joints, their sun or ring gears with the peripheral regions of at least one planetary gear combing the smallest and largest radius, move completely synchronously, ie at the same speed, without a slip.
  • the radius of the pitch circle is always to be referred to as the radius of a toothed element - ie sun gear, planet gear, ring gear or other gear - so the circle on which touch the teeth of meshing gears.
  • the considerations with three ring gears are analogous.
  • the sun (or hollow) wheel with the mean radius rs.mittei corresponds in the application in a vehicle to the coupled with the drive shaft rotary connection "1", the other two sun (or hollow) wheels with the largest and smallest radius rs.max, r s , min the rotary joints "2", "3" for the vehicle wheels to be coupled.
  • Vp min Vs ma ⁇ Vp
  • medium Vs medium ⁇ Vp
  • ma x Vs, m j n
  • v means the speed at the circumference of the gear in question, actually the speed on the contact circle between intermeshing gears or gears, and taking into account that naturally meshes with the smallest portion of a planetary gear, the largest sun gear, and vice versa.
  • the peripheral velocities v s of the sun gears in a coordinate system related to the transmission chassis directly correspond to the respective rotational speed
  • the circumferential velocities v p at a peripheral region of a planetary gear can also each have a component owing to the relative rotational speed ⁇ of the planet carrier relative to the transmission chassis.
  • vs max n 2 * 2TT r s , max Vs, medium ⁇ * ni * 2TT r s. Average ⁇ Vs.min - n 3 * 2 ⁇ r s , min >
  • n s ' n s - n PT , or
  • n 2 ' n 2 -n P T
  • Tp.min Ts.ma * ⁇ '/ ⁇ ' ⁇ r P
  • miltel Ts.
  • Middle * ⁇ '/ ⁇ ' ⁇ Tp.max fs.min * fla '/ np'
  • medium * ⁇ ' ⁇ ' ⁇ 1 Ts, medium / l " p, medium * ⁇ '/ ⁇ ' ⁇
  • ⁇ [1 + ⁇ / rp mean] ⁇ , min / ⁇ , mean * ⁇ 3 '/ ⁇ '.
  • n P 7 [n 3 - n 2 ] r s , mi (iei / [rp
  • r x may in turn depend on parameters of the gear pairing, for example on the gear geometry and / or the friction within the gearbox. A lower tendency to self-locking should have a so-called involute.
  • the invention recommends hardening at least the tooth flanks and thereby making them as wear-resistant as possible.
  • the planet gears can roll defined defined, it may be advantageous to store them by means of a planet carrier; a flying bearing of the planet gears would be conceivable, but could lead to unpredictable jamming.
  • a possible precisely defined and low-friction bearing of the planet gears on a planet carrier can be accomplished by means of rolling bearings, although in principle, plain bearings are conceivable.
  • the invention does not necessarily aim at a virtually frictionless storage; it rather depends on an over the operating period about constant friction value to always the equation
  • the differential gear according to the invention allows, for example, cornering, with the outside wheel rotating faster than the inside of the cam, although both are driven, while not losing the grip of a wheel.
  • the use as a differential in a driven axle of a vehicle is only one example of an application of this differential.
  • the differential gear automatically locks and thus rotates this output gear dynamically at the same speed as the other output gear and the drive shaft, regardless of whether the differential is currently a driving or braking torque transmits or the drive train is in a kind of idling or torque freedom.
  • Self-locking means nothing else than that the internal friction of a rolling counteracts the planetary gearing; This effect can also be interpreted as a kind of clamping, which can not be solved with even the highest drive torque.
  • the design according to the invention thus aims to make the differential so that a drive on only a sun or ring gear alone is not able to overcome the self-fed (with him) clamping action.
  • the effect according to the invention can also be described by the fact that the at least one planetary wheel is subject to a self-locking moment D H , which is produced by subtracting oppositely directed torques DA>0> (-D B ) acting on those two rotary connections;
  • D B does not:
  • the transmission dimensioning according to the invention can be achieved that the locking effect not only at high differential speeds at the two rotary joints, which are coupled to the extreme gear areas of at least one planetary gear used, but extends down to synchronous operation, ie, it acts This is a positive lock, similar to a manually lockable differential.
  • This is a positive lock, similar to a manually lockable differential.
  • there is no differential speed between two abraded wheels of a vehicle even if one completely loses traction. Even if this happens in a curve where the two wheels initially have different speeds. In that case, that wheel which tends to spin as a result of a lack of traction is braked with the driven shaft until a synchronous speed is reached.
  • all planetary gears are made of a convexly curved base body. The planet gears themselves are therefore not designed as ring gears.
  • the invention further provides that for a provided with an all-round toothing peripheral region of a planetary gear and the sun gear meshing therewith the product of the relevant module mi, m 2 , 1TI3, multiplied by the total number of teeth ⁇ , - ⁇ , z Pi2 , zp, 3 and zs, i, zs, 2, zs, 3 of each pairing, identical for two or three pairings of each planetary gear toothing and the respective sun gear is:
  • the invention provides that for a with a running all around teeth provided peripheral portion of a planet gear and meshing therewith ring gear, the product of the respective module rr »i, m 2, m 3, multiplied by the difference between the numbers of teeth z Pi i, zp, 2, zp, 3, and z H.
  • the invention can be further simplified by having two or three circumferential regions of a planetary gear, each with a pair of different radii ⁇ 2, h ⁇ r 3 , r 2 r 3, each having a continuous toothing, with the same modules mi, m 2 , m 3 :
  • ITH m 3 , and / or
  • the axes of all planet gears should run parallel to each other.
  • the common axial direction is preferably parallel to the central axis of a sun or ring gear.
  • the invention can be further developed to the effect that the axes of all planetary gears are on the outer surface of a circular cylinder of radius e, under an eccentricity e to the central axis z.
  • the same eccentricity of all planet gears ensures that all planetary gears can be made identical and mesh with the same sun gear.
  • the lever which determines the torque available for a rotational acceleration of the planetary gear decreases.
  • the state of self-inhibition can be achieved sooner.
  • the planetary gears may be mounted in a planet carrier.
  • Such storage ensures that none of the planetary gears can jam and thus always prevail with respect to the rotational movement and / or acceleration of the planet gears defined conditions.
  • Such a planet carrier should be freely rotatable about a central axis, in turn, not subject to the risk of jamming. In such an embodiment, therefore, the movement of the planet carrier is not coupled to another element.
  • the cavity inside the gear unit is not filled at all, but that the bearing points and / or (bearing) points to be lubricated are directly supplied with lubrication lines or bores or with spray lubrication.
  • a lubricant is present in the transmission cavity, for example only 8% of the volume within the transmission cavity or less, preferably only 4% of that volume or less, in particular only 2% of that volume or less.
  • the planet carrier may also be controllable, in particular in order to influence the rotational speeds of the rotary connections.
  • This makes it possible to directly influence the properties of the differential gear according to the invention to take.
  • control can be done either purely mechanical way or by means of electronics;
  • the controller may be part of a control loop that responds to a measured quantity.
  • the planet carrier may also be provided with a circumferential toothing, similar to a sun or ring gear. In such a toothing can engage another control or drive gear, so as to act on the rotation angle and / or the rotational speed of the planet carrier.
  • a caterpillar vehicle could be steered, in particular also in the state, in that the planetary gears are forced to a rolling movement by specifying an asynchronous rotational speed of the planet carrier, that is, a different rotational speed than at the driven sun or ring gear.
  • the self-locking is canceled, and there is a compensating movement, and due to different speeds on the two tracks of the crawler vehicle in question, this performs a turn or turn.
  • the unilateral deceleration of a caterpillar is not successful because the self-locking of the differential gear according to the invention is not canceled by a unilateral action.
  • the planet carrier as the output. Possibly.
  • the speed of the planet carrier can only be tapped for measurement purposes, in order to obtain such information about the state within the transmission.
  • the invention can be further developed in such a way that the rotational connections coupled to the tooth regions with the smallest radius r P , min ⁇ rp.mittei and with the largest radius r P , ma x> r P, strive away from one another, preferably in approximately opposite directions , in particular coaxial with the central axis z. Since the radii of these two toothed areas have the greatest possible difference, a relative displacement is possible between them, corresponding to the driven wheels of a vehicle.
  • the invention prefers to arrange the respective rotary connections approximately mirror-inverted, ie at the two end faces of a central axis of the differential gear according to the invention.
  • rotary terminals are arranged coaxially to a central axis, they are aligned with each other, and accordingly no wobbling motion can occur, especially if the two, connected to the differential gear according to the invention are both balanced, so that they can cause no imbalance.
  • a toothed region with a mean radius rp, with t e i, with rp min ⁇ rp, m ittei ⁇ ⁇ 3 ⁇ should be coupled to a rotary connection, which lies radially inside or radially outside of the other two rotary connections.
  • a rotary connection which lies radially inside or radially outside of the other two rotary connections.
  • the rotary connection of a ring gear radially outward, the rotary connection of a sun gear are radially within the other rotary connections.
  • a connection located radially inside the other rotary connections can be understood, for example, to mean a central axis which is located within one or both of other tubular rotary connections.
  • a toothed portion having an average radius rp.mittei, rp, m j n ⁇ rp.mittei ⁇ ⁇ 13 ⁇ is coupled to a pivot connection, whose axis of rotation with the axes of rotation of one or both other rotary connections ⁇ angle ⁇ includes, with
  • a further design specification states that at least one toothing region, preferably a toothed region with a mean radius rp.miuei, with r P , min ⁇ rpmittei ⁇ rp, ma x, can be coupled to the relevant rotary connection via a deflection gear, preferably via a Bevel gear or worm gear.
  • the rotational axis of a rotational movement can be deflected by 90 °, according to the previously described, T-shaped arrangement of two axial and one radial axis of rotation.
  • a worm gear on the other hand provides a deflection of a rotation about a central axis of the worm wheel in a rotation about a tangential axis of rotation of the worm.
  • the rotary connections can be mounted in a housing, preferably in each case at least two spaced bearing points, in particular by means of rolling bearings.
  • the rotational connections coupled to the toothing regions with the smallest radius r Pimin ⁇ rp run coaxially with the rotary connection coupled to the toothing region of medium radius rp mmei with ( e i and with the largest radius r P , ma > rp.mmei
  • the third rotary connection is preferably located on the central axis, which may be an axially flanged motor to the housing, possibly via a gearbox.
  • the invention undergoes an advantageous development in that one or preferably both, to the toothed areas with the smallest radius ⁇ ⁇ 1 ⁇ ⁇ rp.mittei and with the largest radius r P , ma x> rp > coupled with tei rotary joints with a rotary connection each one another Differential gear, rotatably coupled or connected.
  • This makes it possible to expand the field of application of the invention. To think this is, inter alia, to a motor vehicle with all-wheel drive, a central differential gear coupling two cardan shafts to the front and rear axles to a drive motor, while the two other differential gear each couple the two wheels of the front or rear axle to the propshaft in question.
  • Such a conventional differential gear may be formed as an axial differential gear, the rotary joints are coupled together via bevel gears, or as a planar differential gear in the manner of a planetary gear.
  • the free rotary joints of the coupled differential and differential gear can be rotatably coupled or connected or integrated with one gear. There then takes place the input or output of the rotational energy via meshing with the respective gear or otherwise coupled transmission elements.
  • a particularly clear arrangement results when the gears are arranged parallel to each other at the free rotational connections of the coupled differential and differential gear to a common axis of rotation.
  • Such an arrangement has a high degree of symmetry, so that neither wobble nor unbalance movements are to be feared; Moreover, it is in many applications, such.
  • the gears are rotatably coupled to the free rotational connections of the coupled differential and differential gear via one or more chains with an eccentrically mounted gear.
  • these eccentric gears may have equal eccentricities with respect to the central center axis, but be offset in different radial directions from the central axis. for example, at the same intermediate or center angles.
  • four adjacent eccentric gears would each include an intermediate angle of 90 ° with each other, with five eccentric gears would result in an intermediate angle of 72 °, with six eccentric gears an intermediate angle of 60 °.
  • Such a geometry in turn would not affect the symmetry of the overall arrangement.
  • eccentrically mounted gears per a pivot or knee joint or other radial adjustment is arranged, so that the eccentricity e the eccentrically mounted gears is variable. If this ensures that the eccentricity e of all these eccentric gears are adjusted uniformly, the symmetry and thus the concentricity do not suffer. This can be effected for example by a common adjusting device.
  • the eccentric gears could be mounted on levers pivotable about their (inner) decentralized axes; the peripheral ends - or other areas - of this pivotable lever could in turn be stored in, for example, radially extending slots or slots of a common disk.
  • a radial adjustment of the (outer) eccentric gears could be effected.
  • the eccentric gears may also be coupled to a central adjusting device, for example via a central gear meshing with bearing bodies mounted in a decentralized disc and thereby radially displaced the decentrally mounted on the bearing bodies gears, in particular by rotation of the bearing body to their to the central gear prallelen axes.
  • the eccentrically mounted gears are wrapped by a common chain outside or are. Such a chain is responsible for imparting rotational movements to the decentralized gearwheels around a central axis when the entirety of all eccentrically mounted gearwheels meshing therewith, which can then be combined in the center via the compensating and / or differential gears according to the invention.
  • the eccentric gears can learn e different rotational speeds depending on the set eccentricity, so that at the same input speed depending on the adjusted eccentricity different output speeds are selectable. Since the eccentricity can be infinitely varied, this results in a continuously variable transmission.
  • the common chain should be held by a tensioning device under tension to be able to tightly surround the star of the eccentric gears regardless of their eccentricity e each. It is therefore an open chain with two ends, one of which may be fixed, for example on a housing or chassis of the transmission, while the other is movable by means of the tensioning device, but is always kept under tension, ie, in one direction pulled to the first, fixed end.
  • the crankshaft always rotates in the same direction, as od on the housing, chassis od.
  • "front" chain end are used while the following, in the direction of rotation "rear” chain end is tensioned.
  • FIG. 1 shows a longitudinal section through a first embodiment of a differential gear according to the invention, wherein the rotary connection is made to the different radius regions of the planet gears via sun gears;
  • Fig. 2 is a of FIG. 1 corresponding sectional view of a second
  • Differential gear with the basic structure of Figure 1 as part of an extended differential gear with more than three rotary joints, shown in a section along the longitudinal axis of a central input or output axis.
  • Fig. 4 is a continuously variable transmission, wherein the extended transmission of FIG. 3 for
  • Insert reaches, in a view in the direction of the longitudinal axis of Fig. 3; and FIG. 5 a longitudinal section through the continuously variable transmission according to FIG. 4, wherein the widened differential gear according to FIG. 3 can be seen.
  • the differential gears 1 and V of Fig. 1 and 2 have a similar function and have many structural similarities, which are initially to be treated together:
  • Both differential gear 1; 1 ' are each housed in a housing 2, which encloses an inner cavity 3 and in each case has three passage points 4, 5, 6 for a total of three rotary connections 7, 8, 9.
  • Each housing 2 each has an approximately cylindrical shape with a cylinder jacket 10 which is closed at both ends by a preferably circular face plate 1 1, 1 2.
  • a passage point 4 for a rotary connection 6 is located on the cylinder jacket 10, the other two passage points 5, 6 for the remaining rotary connections 8, 9 are located in a respective end plate 1 1, 12, in a common alignment, preferably in the center of respective end plate 1 1, 12th
  • the housing 2 may have a perpendicular to the respective surface region of the housing 2 outwardly projecting sleeve projection 13, wherein two bearings, preferably bearings 14, are arranged offset in the longitudinal direction of the respective sleeve 3, for example in all-round wells, such as grooves or grooves, on the inside of the housing 2 and the respective sleeve 13 is inserted.
  • the inner rings of the bearings or roller bearings 14 each encompass an axis of rotation 15, 6, 1 7 as outwardly projecting rotary connection 7, 8, 9.
  • the two end-side axes of rotation 1 6, 17 are aligned, the mantej worne axis of rotation 1 5 extends at a right angle to it ,
  • the common axis of rotation of the two aligned axes of rotation 1 6, 1 7 is concentric with the housing shell 10 and is intended below as the main axis of the differential gear 1; 1 'are called.
  • All axes of rotation 15, 16, 1 7 terminate in the interior 3 of the housing 2 and are preferably provided in the region of its inner end with a toothed transmission element.
  • the two embodiments 1 differ; 1 'from each other, which is why in the following first on the Fig. 1 should be discussed alone.
  • the two mutually aligned axes of rotation 16, 17 each carry a front-toothed gear; these have in the differential gear 1; Both sun gears have different radii rs.min, rs, ma x-
  • this right-angled rotation axis 15 carries at its inner end a bevel gear 20, the jacket tapers inwardly.
  • This rotary member 21 has a radially inner sleeve portion 22 which is rotatably mounted on one of the two mutually aligned axes of rotation 16, 17 by means of bearings, preferably by means of two offset in the axial direction bearing, in particular by means of rolling bearings 23.
  • bearings 23 are located between the rolling bearings 14 of the respective axis of rotation 17 on the one hand and the sun gear 19 on the other.
  • annular disk 24 connects, which is rotatably connected to the sleeve portion 22 or formed together with that or integrated.
  • This annular disc 24 extends parallel to the relevant housing end face 12 radially outward; their outer circumference is located just inside the housing shell 10.
  • toothing 26 is formed on the side facing the bevel gear 20 side of the annular disk 24 or integrally formed on the peripheral edge or connected, extending in the direction of the bevel gear 20 toward the second sleeve portion 25 a toothing 26 which meshes with the bevel gear 20.
  • the lateral surfaces of the teeth 20, 26 extend along conical surfaces whose opening angles are each about 90 °, so that the cross-sections of these lateral surfaces each extend at an angle of 45 °, based on the main axis of the differential gear first
  • the inner sleeve has at its free end, that is to say remote from the circular disk 24, an all-round toothing on its outer surface, which can be regarded as a third sun gear 27 of the differential gear 1.
  • the radius rs.mittei this Sonnrenrades 27 is between the radii rs.min, rs.max those of the other two sun gears 18, 19: rS, min ⁇ r S, medium ⁇ rs.ma -
  • the arrangement is such that the three sun gears 18, 19, 27 are directly next to each other.
  • the planet carrier 29 has an approximately U-shaped cross-section and therefore has a radially outer sleeve portion 30 which connects two end-side annular discs 31, 32 with each other.
  • the planet carrier 28 may be composed of two or more parts detachably; For example, one or both annular disc (s) 31, 32 may be screwed to the sleeve portion 30.
  • the planet carrier 29 is on the one hand in the region of the radially inner edges of its two annular discs 31, 32 on the two-toothed rotary member 21, on the other hand on the opposite axis of rotation 16 of the planet.
  • the planet carrier 29 is designed such that it has all three sun gears 18, 19th , 27 encompasses the outside.
  • its sleeve portion 30 is longer than the sum of the thicknesses of the three sun gears 18, 19, 27.
  • the lengths of the planet gears 28 correspond approximately to the axial length of the sleeve portion 30, so that the planet gears 28 along all three sun gears 18, 19, 27 extend.
  • Each planetary gear 28 has three toothed portions 33, 34, 35, which each have different radii rp, mi n ⁇ rp, m ittei ⁇ r P , max .
  • the smallest planetary radius rp, min is assigned to the largest sun gear radius rs.max, and vice versa.
  • the coat-side rotary connection 7 the gear pairing with the middle radii rp, with tei, r s .mittei assigned.
  • the direction of rotation and speed of the planet carrier 29 relative to the rotary member 21 determines the transmission behavior of the differential gear 1:
  • the planet carrier 29 could even rotate in the opposite direction as the rotary member 21; this would then be classified in the above sense as a slower rotation of the planet carrier 29 relative to the rotary member 21. It is even the application conceivable that the rotary connector 7 is temporarily braked, so that the rotary member 21 is stationary. To think this would include, inter alia, the drive of a tracked vehicle such as an excavator od. Like., The two caterpillars are coupled via a clutch and inventive differential gear to a motor. If the engine is switched off or disconnected, the tracked vehicle is stationary. If this now turn on the spot, the caterpillars must be driven in opposite directions. For this purpose, the planet carrier 29 can be set in rotation, the direction of rotation of which predetermines the direction of rotation of the tracked vehicle. In this case, the planet carrier 21 would rotate faster than the stationary rotating part 21st
  • the inhibition within the transmission is set such that for each externally applied torque between the shell-side rotary connection 7 and one of the two end-side rotary connections 8, 9 occurs self-locking, ie, such torque is not able to deviate from zero relative speed between the planet carrier 29 on the one hand and the rotary member 21 to bring about;
  • the differential remains in a synchronized state and locks, i.e., the two aligned axes of rotation 16, 17 always rotate at the same speed, ie, for example, when a connected to such a rotation axis 16, 17 vehicle wheel loses traction.
  • the differential gear 1 In this case, the planet gears 28 roll together on the sun gear 19.
  • the rotary member 21 ' has a U-shaped cross section similar to the planet carrier 29 of Fig. 1, and is mounted on the two axes of rotation 16, 17 on the inner edges of its two annular discs 36, 37, which form the legs of the U-shaped cross-section ,
  • a conical toothing 26 ' On the outside of the sleeve-shaped middle part 38 is a conical toothing 26 ', on its inside a ring gear 27'.
  • the planet carrier 29 ' is mounted on the two mutually aligned axes of rotation 16, 17, between the molded thereon ring gears 18', 19 '.
  • the direction of rotation and speed of the planet carrier 29 'relative to the rotary member 21' also determines the transmission behavior of the differential gear 1 ':
  • the inhibition within the transmission is set such that for each externally applied torque between the shell-side rotary connection 7 and one of the two end-side rotary connections 8, 9 occurs self-locking; while the gear ratios r P, mn : r s , max on the one hand and rp.max: rp, mjn on the other hand between the two gear pairings of the two extreme ring gears 18 ', 19' and / or the aligned axes of rotation 16, 17 is so large that for between these ring gears 18 ', 19' or axes of rotation 16, 17 acting from outside torques no self-locking occurs; each with the consequences described above with respect to the embodiment 1 of FIG.
  • the differential 1 also permits cornering, with two driven wheels rotating at different speeds, while a wheel alone can not twist even in the event of loss of traction.
  • FIG. 3 shows a particular application of a differential gear 1 according to the invention in an extended gear 40:
  • a differential 1 " which has the same structure as the transmission 1 of Fig. 1.
  • the sun gear 27 "with the mean radius rs .stoff is in this case connected directly to a complete arrangement passing through the central axis 41.
  • the two other sun gears 18 ", 19” are each end of one of two tubular, guided on the central axis 41 and preferably mounted thereon axes 16 ", 17" is formed.
  • a further differential gear 42, 43 of conventional design arranged, each consisting of a central differential cage 44 which is rotatably connected to the relevant axis 16 “, 17", and two in the axial direction in contrast offset differential disks 45, 46, each with one of the central differential cage 44 facing, circumferential toothing, which mesh with different differential bevel gears which are mounted in the differential cage 44 to rotate about the central axis 41 about radial axes.
  • the two differential disks 45, 46 of both differential gear 42, 43 are provided on their outer circumference, each with a toothing 47. In this way, one thus already obtains four outer rotary connections 47, in addition to the inner rotary connection 41.
  • sun gears 18 ", 19” can also rotate with rotational speeds deviating from all rotary connections 41, 47. It therefore makes sense, these sun gears 18 “, 19” side of the planet carrier according to the invention 29 “ in the form of disks 48 to enlarge to the outside and to be provided at its periphery also with a completely running toothing 49. Thus, it is finally possible to record and combine a total of six different rotational movements via the rotary connections 47, 48 and to provide them on an output shaft 41.
  • An application area for the extended transmission 40 from FIG. 3 forms the continuously variable transmission 50 according to FIGS. 4 and 5.
  • the extended transmission 40 from FIG. 3 can be recognized again.
  • the central axis 41 which is connected to the central sun gear 27 "of the transmission 40 of FIG. 3, is located in FIG. 4 in the center of an example six-armed star 51, the arms 52 each have two pairs of eccentric gears 53, 54, 55 , 56.
  • a radially further inside gear 53 is still within a housing 57 enclosing the widened gear 40, which may for example have the shape of a cylindrical box, with a lateral surface 58 and two end surfaces 59, 60 terminating the latter.
  • the housing 57 may in turn be rotatably mounted so that it is rotatable about the central axis 41, and may for example have a completely running toothing, about which it receives its rotary drive.
  • each one of the six gearings 47, 49 is coupled to the various rotary terminals of the widened gearbox 40 via an endless chain 61.
  • These gears 53 are rotatably connected to one of six, parallel to the central axis 41, eccentrically mounted within the housing 57 rotary shafts 62.
  • These rotary shafts 62 pass through an end face 60 of the housing 57.
  • a further pair of gears 55, 56 each mounted, which are rotatably connected to each other by a rotary shaft 64.
  • a gear 55 is in a common plane with the relevant, further inside gear 54, and is rotatably coupled via an endless chain 65 with this gear 54.
  • the free gears 56 are largely surrounded by another chain 66 outside.
  • This chain 66 referred to below as the main chain, is not endless, but has two ends. Of these, one is anchored to the chassis 67 of the continuously variable transmission 50, for example to an extension 68 of this chassis 67, while the other end is coupled to the chassis 67 via a spring element 69 shortened in FIG.
  • the spring element 69 allows the main chain 66 to adapt to different pivot positions of the lever 63.
  • a first pivot position of the lever 63 is shown in solid lines, wherein the outer rotary shafts 64 are relatively far outward - the arms 52 are nearly stretched - and with dashed lines, a second pivot position of the lever 63 is indicated, wherein the outer rotary shafts 64 are located further inside, as the arms 52 are more angled.
  • a hexagon circumscribed to the star 51 has a larger circumference than in the second case, and it is precisely this fact that accounts for the adjustment provided by the spring-tensioning element 69.
  • the gears 56 rotate faster or slower at the same rotational speed of the housing 57 and share this larger or smaller speed of the output shaft 70 with.
  • the shaft extension 70 can be used as the output shaft of the continuously variable transmission 50.
  • the eccentrically adjustable gears 56 is selected to the radii of the teeth 47, only one speed in one direction, possibly to a stop, or in both directions can be constructed at the output. If the rotational speed on the shaft 41, 70 never becomes zero, a further planetary gear 71 may be provided on the continuously variable transmission 50. This can be arranged on the main chain 66 facing away from front side 59 of the housing 57.
  • the central axis 41 occurs in the form of another stub shaft 72 to the outside and there carries a sun gear 73 of the planetary gear 71, with which it is rotatably connected.
  • Whose ring gear 74 is incorporated as a trough-shaped, circular recess 75 with a toothing in its peripheral edge directly into the outer side 76 of the housing face 59.
  • an opposing direction of rotation may optionally be generated on the secondary output or output shaft 81 in relation to the input direction of rotation on the housing 57.

Landscapes

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

Abstract

L'invention concerne un engrenage différentiel permettant un échange neutre en puissance d'énergie de rotation entre au moins trois raccords tournants, l'engrenage comprenant au moins un pignon satellite et au moins un pignon planétaire ou une couronne venant en prise avec le pignon satellite. Au moins un pignon satellite présente trois zones périphériques décalées dans sa direction axiale, chacune munie d'une denture sur son pourtour et chacune d'un diamètre différent. Un pignon planétaire ou une couronne sont respectivement en prise avec chaque zone périphérique dentée du ou des pignons satellites, et sont accouplés ou reliés de manière solidaire en rotation à respectivement un raccord tournant de l'engrenage différentiel. L'invention concerne également un procédé de fabrication dudit engrenage différentiel ainsi qu'un perfectionnement d'un engrenage différentiel selon l'invention permettant de réaliser une transmission à variation continue, qui nécessite précisément un engrenage différentiel sans commutation présentant une complémentarité de forme entre une entrée et une sortie (mécanisme de transfert) ou entre deux entrées et une sortie (mécanisme totalisateur).
EP15730243.1A 2014-05-15 2015-05-15 Engrenage différentiel à déverrouillage automatique Withdrawn EP3143307A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014007073.5A DE102014007073B4 (de) 2014-05-15 2014-05-15 Ausgleichsgetriebe mit einer selbsttätig aktivierten Sperrung oder Hemmung der Abtriebswellen
PCT/IB2015/000696 WO2015173628A1 (fr) 2014-05-15 2015-05-15 Engrenage différentiel à déverrouillage automatique

Publications (1)

Publication Number Publication Date
EP3143307A1 true EP3143307A1 (fr) 2017-03-22

Family

ID=53434382

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15730243.1A Withdrawn EP3143307A1 (fr) 2014-05-15 2015-05-15 Engrenage différentiel à déverrouillage automatique

Country Status (3)

Country Link
EP (1) EP3143307A1 (fr)
DE (1) DE102014007073B4 (fr)
WO (1) WO2015173628A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016203551B4 (de) * 2016-03-03 2019-06-06 Audi Ag Differentialgetriebe für ein Kraftfahrzeug
CN107448578B (zh) * 2017-07-19 2023-02-07 重庆墨龙机械有限公司 差速锁
CN109723792A (zh) * 2017-10-31 2019-05-07 罗灿 非锥齿轮差速器
JP7396238B2 (ja) * 2020-09-17 2023-12-12 トヨタ自動車株式会社 差動装置
CN112178152B (zh) * 2020-10-16 2023-02-21 魏家斌 斜齿轮差速器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE850696C (de) 1950-06-27 1952-09-25 Ernest Wildhaber Ausgleichgetriebe, insbesondere fuer Kraftfahrzeuge
DE2609377A1 (de) * 1976-03-06 1977-09-08 Gerhard Staudenmaier Selbstsperrendes verschleissloses ausgleichgetriebe
DE4436410A1 (de) * 1994-10-12 1996-04-18 Man Nutzfahrzeuge Ag Differential für Kraftfahrzeuge
ATE466215T1 (de) 2004-05-28 2010-05-15 Albrecht Baumann Stufenloses getriebe sowie verwendung und betriebsverfahren dafür
DE102006040144A1 (de) 2006-08-26 2008-02-28 Volkswagen Ag Aktives Differential

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2015173628A1 *

Also Published As

Publication number Publication date
DE102014007073A1 (de) 2015-11-19
WO2015173628A1 (fr) 2015-11-19
DE102014007073B4 (de) 2023-09-07

Similar Documents

Publication Publication Date Title
CH656197A5 (de) Differentialgetriebe.
CH626692A5 (fr)
DE2206107A1 (de) Zahnradausgleichgetriebe
DE10319684A1 (de) Verteilerdifferenzial für Kraftfahrzeuge
DE19735052A1 (de) Untersetzungsgetriebe
DE102012219212A1 (de) Differentialgetriebe
EP3143307A1 (fr) Engrenage différentiel à déverrouillage automatique
WO2010003505A2 (fr) Dispositif d'entraînement pour véhicules automobiles à quatre roues motrices
DE3710582A1 (de) Permanenter vierradantrieb fuer ein kraftfahrzeug
EP1906053B1 (fr) Engrenage différentiel autobloquant
WO2014019744A1 (fr) Différentiel à pignons droits
WO2005028236A1 (fr) Ensemble transmission
DE10353927A1 (de) Achsen-Anordnung
DE3837542A1 (de) Zentrales achsdifferentialgetriebe fuer kraftfahrzeuge
DE2545681B1 (de) Planetengetriebe
DE102016109551A1 (de) Stufenplanetengetriebe
DE102012219215A1 (de) Differentialgetriebe
WO2016058608A1 (fr) Entraînement électrique pour un véhicule ainsi que véhicule équipé de l'entraînement électrique
EP2187092A2 (fr) Engrenage coaxial
DE850696C (de) Ausgleichgetriebe, insbesondere fuer Kraftfahrzeuge
DE102012015082B4 (de) Freilaufvorrichtung mit schaltbarem Freilauf
EP3073149B1 (fr) Mécanisme de roue libre
DE102006025061A1 (de) Einrichtung zur Axialeinstellung wenigstens eines Lamellenschaltelementes
WO2016058609A1 (fr) Propulsion électrique pour un véhicule ainsi que véhicule équipé de la propulsion électrique
WO2005066521A1 (fr) Engrenage differentiel ayant une cage de frottement destinee au moment de lacet

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20161214

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20181201