WO2021083788A1 - Transmission de différentiel à roues coniques - Google Patents

Transmission de différentiel à roues coniques Download PDF

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Publication number
WO2021083788A1
WO2021083788A1 PCT/EP2020/079775 EP2020079775W WO2021083788A1 WO 2021083788 A1 WO2021083788 A1 WO 2021083788A1 EP 2020079775 W EP2020079775 W EP 2020079775W WO 2021083788 A1 WO2021083788 A1 WO 2021083788A1
Authority
WO
WIPO (PCT)
Prior art keywords
differential
bevel gear
bevel
gear
shift sleeve
Prior art date
Application number
PCT/EP2020/079775
Other languages
German (de)
English (en)
Inventor
Martin Bloder
Original Assignee
Technische Universität Graz
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 Technische Universität Graz filed Critical Technische Universität Graz
Publication of WO2021083788A1 publication Critical patent/WO2021083788A1/fr

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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
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3462—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear with means for changing distribution of torque between front and rear wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
    • B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
    • B60K2023/0816—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch for varying front-rear torque distribution with a central differential
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears

Definitions

  • the present invention relates to a bevel gear differential gear comprising a differential cage, inside of which two bevel gears are arranged opposite one another, the bevel gears each being rotatably mounted about an output axis, the bevel gear differential gear further comprising at least one differential bevel gear which is rotatably mounted in the differential cage about a differential bevel gear axis is.
  • bevel gear differentials have been established for this purpose.
  • the latter have bevel gears inside a differential cage, which are non-rotatably connected to side shafts that are to be driven and are located at least in sections outside the differential cage.
  • the differential carrier is driven by an external wheel.
  • the bevel gears are connected in the differential cage via at least one bevel gear which is rotatable about a bevel gear axis and which only then revolves around its
  • Pinion pinion axle rotates when the wheels turn and so the side shafts rotate at different speeds, especially when cornering.
  • the essence of the present invention consists in using the at least one differential bevel gear and / or at least one of the bevel gears instead of costly additional shifting elements in order to selectively cancel or establish the frictional connection to the side shafts (from the drive force transmitted to the differential carrier).
  • a bevel gear differential gear it comprises a differential cage, inside of which two bevel gears are arranged opposite one another, the bevel gears each being rotatably mounted about an output axis, the bevel gear differential gear further comprising at least one differential bevel gear which is rotatably mounted in the differential cage about a differential bevel gear axis
  • the at least one bevel gear is displaceable along its bevel gear axis and / or at least one of the bevel gears along its output axis between an engagement position and a release position, wherein in the engagement position, but not in the release position, the at least one bevel gear is in engagement with the two bevel gears and connects them to each other.
  • the at least one differential bevel gear can compensate for unequal speeds of the bevel gears.
  • the rotational connection of the bevel gears via the at least one differential bevel gear ultimately creates the frictional connection between the side shafts connected to the bevel gears in a rotationally fixed manner and the differential carrier, so that the side shafts are driven when the differential carrier is driven.
  • the differential cage can be driven in a manner known per se via an outer wheel which is non-rotatably connected to the differential cage or is part of it.
  • the bevel gear differential gear according to the invention can thus be used in a vehicle for optionally switching the drive of an axle on and off.
  • the drive of the axle is switched on. If, on the other hand, the at least one differential bevel gear and / or at least one of the bevel gears are in the respective release position, the drive of the axle is switched off.
  • the displaceable arrangement of the at least one differential bevel gear along its differential bevel gear axis means that it can be moved parallel to the
  • Differential bevel gear axis and thus radial mobility in relation to the differential carrier can be achieved, for example, by mounting the differential bevel gear on a bearing pin so that it can be rotated as well as be displaceable along the longitudinal axis of the bearing pin.
  • the displaceable arrangement of at least one of the bevel gears means a mobility parallel to the output axis of the respective displaceable bevel gear and thus a radial mobility in relation to the differential carrier.
  • Such mobility can be achieved, for example, in that the respective bevel gear is mounted on a section of the associated side shaft by means of sliding teeth, so that the bevel gear can be displaced along the longitudinal axis of this section.
  • the bevel gear differential gear according to the invention thus results in a weight and cost reduction due to the omission of additional shift elements in comparison with known systems.
  • no additional force-transmitting shifting elements, such as dog clutches or the like, are necessary in the vicinity of the differential.
  • There is also a reduction in the remaining Drag torque is achieved in comparison to systems that only release or switch one side shaft.
  • bevel gear differential In a preferred embodiment of the bevel gear differential according to the invention it is provided that at least two differential bevel gears are provided. This enables the transmission of particularly high torques to the bevel gears or the side shafts.
  • differential bevel gears can be provided here.
  • the arrangement can be such that two differential bevel gears are located symmetrically opposite one another in the differential carrier.
  • bevel gear differential gear In a preferred embodiment of the bevel gear differential gear according to the invention, it is provided that exactly two differential bevel gears are provided, which are arranged opposite one another. Such a, preferably symmetrical, arrangement is favorable in terms of production technology and has become well established in vehicle construction.
  • the two differential bevel gears are rotatably and displaceably mounted on the same bearing pin in this case.
  • a preferred embodiment of the bevel gear differential gear provides that at least one actuating element is provided for the at least one differential bevel gear and / or at least one of the bevel gears, whereby the at least one actuating element is movably mounted and wherein the at least one actuating element has an inner section which is operatively connected to the differential bevel gear and / or the bevel gear, and an outer section which protrudes outward through the differential carrier in such a way that the outer portion can be contacted from outside the differential carrier is in order to be able to move the actuating element from the outside at least from a first position into a second position or vice versa.
  • the at least one actuating element can be constructed in several parts.
  • the actuating element is preferably designed in one piece.
  • the operative connection between the actuating element or the inner section of the actuating element and the differential bevel gear and / or the bevel gear can be implemented in a manner known per se, for example by form fit, force fit or a combination of form fit and force fit.
  • the operative connection can be established by means of a spring element.
  • Another example would be a magnetic coupling between the inner section and the differential bevel gear and / or the bevel gear.
  • the outer section does not have to protrude outwards from the differential carrier, but can also be flush with the Lock the differential carrier to the outside.
  • the outer section can in any case be contacted from the outside in order to be able to move the actuating element from the outside at least from the first position into the second position. "At least" is to be understood to mean that, on the one hand, other movements, in particular from the second position to the first position, can also be possible the second position can be achieved by the action from the outside on the outer section.
  • the movement of the actuating element between the first and second positions does not have to be a linear movement, but can also be a rotary movement or a combination of linear and rotary movement.
  • the first position of the at least one actuating element can, for example, with the release position of the one
  • the first position of the at least one actuating element can be associated, for example, with the release position of at least one of the bevel gears.
  • the second position of the at least one actuating element is typically associated with the engagement position.
  • the actuating element moves the at least one differential bevel gear and / or at least one of the bevel gears from the release position to the engagement position during the transition from the first to the second position or during the transition from the second to the first position.
  • the return movement of the at least one differential bevel gear and / or of the at least one of the Bevel gears can optionally be provided with a further mechanism, for example a spring mechanism known per se.
  • the actuating element can also be provided for the return movement.
  • the operative connection between the inner section of the actuating element and the differential bevel gear and / or the bevel gear can be both positive and magnetic, the positive connection being used for movement in one direction and the magnetic connection for movement in the other direction.
  • One or more actuating elements can be provided per displaceable differential bevel gear or per displaceable bevel gear.
  • a separate actuating element can be provided for each displaceable differential bevel gear or for each displaceable bevel gear, or several differential bevel gears and / or both bevel gears can be operated / switched via a common actuation element.
  • the differential bevel gear and / or the at least one of the bevel gears is designed such that the differential bevel gear and / or the bevel gear is in the release position when the actuating element is in the first position and in the engagement position when the actuating element is in the second position , or the other way around.
  • the at least one actuating element is preferably parallel to the differential bevel gear axis of the at least one differential bevel gear and / or transversely to the output axis of the at least one of the bevel gears, displaceable. This allows a structurally simple and inexpensive implementation.
  • the at least one actuating element can in particular be displaceable normal to the output shaft.
  • the displaceability of the at least one actuating element allows in particular a linear movement of the actuating element between its first and second position and vice versa.
  • a form fit for example, can be used as an operative connection between the inner section and the differential bevel gear or bevel gear.
  • the at least one actuating element rests with its inner section on at least one differential bevel gear and / or the at least one of the bevel gears at least in sections in order to move from the first position to the second Position and / or from the second position to the first position to press against the differential bevel gear and / or the bevel gear and to move it.
  • the respective inner section contacts the respective differential bevel gear and / or bevel gear and can thus press against the latter.
  • a further mechanism for example a spring mechanism
  • a further mechanism for example a spring mechanism
  • a further mechanism for example a spring mechanism
  • a movable, in particular displaceable, shift sleeve is provided, which is arranged outside the differential cage and can be brought into engagement with the outer section of the at least one actuating element in order to move the actuating element at least from the first position to move to the second position.
  • the shift sleeve can alternatively or additionally be rotated so that its movement is a rotary movement or a combined linear and rotary movement.
  • the shift sleeve By moving the shift sleeve, the shift sleeve can be brought into engagement with the outer section of the at least one actuating element and move the at least one actuating element. By moving the shift sleeve in the opposite direction, the engagement of the shift sleeve with the outer section of the at least one actuating element can be released again.
  • the at least one actuating element can then either be moved back by the shift sleeve during its return movement. Or the return movement of the respective actuating element can take place by an additional mechanism which is mediated, for example, by the at least one differential bevel gear or the at least one of the bevel gears.
  • the additional mechanism can, for example, be a spring mechanism known per se, which can be provided for the return movement of the at least one differential bevel gear and / or the at least one of the bevel gears, with an operative connection between the at least one differential bevel gear and / or the at least one of the bevel gears also at least one Actuating element is movable by the additional mechanism.
  • an operative connection is generally established between the shift sleeve and the respective outer section.
  • a form fit between the involved elements or a force fit or a combination thereof can be implemented here.
  • other operative connections known per se e.g. a magnetic operative connection, are alternatively or additionally conceivable.
  • the shift sleeve is displaceably mounted on the differential carrier, preferably parallel to one of the output axes. This allows a very compact design that is inexpensive in terms of production technology and costs.
  • the outer section of the at least one actuating element has a contact surface which preferably runs obliquely to one of the output axes.
  • the contact surface can promote the production of the engagement of the shift sleeve with the outer section.
  • the contact surface is particularly advantageous when the direction of movement of the shift sleeve has no or only a small component parallel to the direction of movement of the outer section or of the at least one actuating element.
  • the production of the engagement of the shift sleeve with the respective outer section is favorable if the contact surface runs obliquely to the direction of movement of the shift sleeve in order to convert the direction of movement of the shift sleeve into the direction of movement of the actuating element.
  • a Such a situation is given in particular when the direction of movement of the shift sleeve is parallel to one of the output axes and the direction of movement of the at least one actuating element is parallel to the differential bevel gear axis.
  • the shift sleeve can have a counterpart section which is designed as a counterpart to the contact surface with a corresponding bevel and is provided for contacting the contact surface.
  • the run-on surface is preferably designed to be flat, but a curved run-on surface is also conceivable.
  • the shift sleeve has a contact surface in order to facilitate the production of the engagement of the shift sleeve with the outer section of the at least one actuating element.
  • the contact surface preferably runs obliquely to the direction of movement of the shift sleeve, in particular to the output shafts. It also applies to the contact surface of the shift sleeve that the contact surface is preferably designed to be flat, but a curved contact surface is also conceivable.
  • the contact surface of the shift sleeve as a counterpart to the contact surface of the Outer portion of the at least one actuating element is formed.
  • a switching ring is provided as the actuating element, that the switching ring has at least one ramp with eccentric geometry, the at least one ramp forming the inner section of the actuating element, so that the switching ring has at least one switching ring bracket , wherein the at least one switching ring bracket forms the outer section of the actuating element, and that the switching ring can be moved from the first position to the second position and vice versa by rotating through a switching angle relative to the differential carrier.
  • the switching ring rotates accordingly in principle with the differential carrier.
  • the switching ring can be provided for switching the at least one differential bevel gear, with one plane of the switching ring being normal to the output axis (s).
  • At least one intermediate piece is typically provided on which the ramp slides.
  • the at least one intermediate piece presses according to the Ramp contour against the at least one differential bevel gear or the at least one of the bevel gears in order to move it axially.
  • two ramps can be provided which press against the two bevel gears or two differential bevel gears via two intermediate pieces.
  • the at least one ramp is typically designed eccentrically, it also being possible for a plurality of sections with different radii to be provided. For example, it would be conceivable to provide two eccentric sections which are curved in the same direction, the two sections having different radii of curvature and being connected via a connecting section with opposite curvature. In principle, however, almost any combination of straight lines, circular arcs, elliptical arcs and / or the like is possible for the respective geometry of the at least one ramp.
  • the provision of the shift ring allows a dramatic shortening of the path that the shift sleeve has to be moved in one direction of actuation towards the shift ring, while at the same time the force required for this movement of the shift sleeve can be limited to an acceptable level, since the ramp geometry and the switching angle a correspondingly further path can be associated with the operative connection.
  • the switching angle is typically in the range from 45 ° to 180 °, preferably in the range from 60 ° to 120 °, for example 90 °.
  • the shift sleeve can be moved in the actuating direction by means of an electromagnet.
  • the shift sleeve has at least one friction cone
  • the at least one shift ring plate has a friction surface that the shift sleeve can be moved in an actuating direction towards the switching ring and that by moving the switching sleeve in the actuating direction, the at least one friction cone can be brought into engagement with the friction surface of the at least one switching ring bracket when the switching ring is in the first position around which the differential cage is located brake the rotating switching ring and move it relative to the differential cage by the switching angle into the second position.
  • the ramp geometry can be designed so that the switching ring then no longer presses against the at least one differential bevel gear or against the at least one of the bevel gears via the intermediate pieces in such a way that it is fixed in the engagement position.
  • the at least one differential bevel gear or the at least one of the bevel gears can then be pressed into the release position via at least one suitable spring element, in particular via at least one axially arranged compression spring.
  • At least one spring in particular at least one torsion spring, is provided, which by the movement of the switching ring from the first position into the second position is tensioned in order to be able to move the switching ring back into the first position by releasing the spring.
  • the spring allows rapid switching or moving of the switching ring back from the second position to the first position.
  • the switching ring can push or press the at least one differential bevel gear or the at least one of the bevel gears into the engagement position via the at least one intermediate piece.
  • At least one, in particular spring-loaded, locking element is provided, that the at least one switching ring tab has a locking contour and that the locking element with the locking contour by moving the switching ring from the first position into the second position can be locked to hold the switching ring in the second position.
  • the at least one spring-loaded locking element can be, for example, at least one locking spring.
  • the switching ring is prevented from moving back or rotating back into the first position, in particular due to the spring force of the spring or torsion spring.
  • the shift sleeve can initially be moved back into a starting position or non-engagement position in which the shift sleeve is not in engagement with the shift ring or the at least one shift ring tab, i.e. against the direction of actuation, for example by means of a spring provided for this purpose.
  • the actuator is not necessary (and also no actuator of its own) to move the selector sleeve back.
  • this opens up the possibility of releasing the lock again by actuating the selector sleeve again, i.e. by moving the selector sleeve again in the direction of actuation and thus triggering the movement of the switching ring back into the first position (by the spring or torsion spring).
  • the same actuator can of course be used for the renewed movement of the shift sleeve in the actuation direction as for the previous movement in the actuation direction. Since only one actuator is required, which is also only required for moving the shift sleeve in one direction, the actuator can be designed to work very easily and very quickly, for example as an electromagnet.
  • the locking contour of the at least one switching ring tab has a contact section in order to be able to slide the locking element on the contact section when the switching ring is moved from the first position to the second position, and that behind a latching section of the locking contour is provided for the contact section in order to be able to lock the locking element with the latching section when the switching ring has been moved from the first position to the second position.
  • the contact section ensures problem-free movement of the switching ring from the first to the second position.
  • the locking section in turn ensures reliable locking of the locking element with the locking contour after or immediately after the Switching ring (from the first position) has been moved to the second position.
  • the latching section is arranged behind the run-on section.
  • the shift sleeve can be set up to release the lock by moving it again in the actuation direction after the shift sleeve has been moved into the disengaged position, for example (by means of a spring) after the previous movement in the actuation direction, in order to prevent the movement of the Switching rings back into the first position by means of the at least one spring or torsion spring - with a very short switching time and relatively low actuation force.
  • the at least one differential bevel gear or the at least one of the bevel gears is brought back into the engagement position by means of the at least one spring element or the at least one compression spring.
  • the shift sleeve has at least one unlocking section, the unlocking section - in particular by moving the shift sleeve in an actuation direction towards the shift ring when the shift sleeve is not initially in engagement with the at least a switching ring strap - can be brought into engagement with the at least one locking element in order to release the locking of the locking element with the locking contour.
  • the at least one unlocking section is designed as an unlocking cone
  • the at least one locking element is designed as at least one locking spring, to slide with a free end on the unlocking cone and so to be able to release the locking of the locking spring with the locking contour by moving the shift sleeve in one actuation direction on the shift ring when the shift sleeve is not initially in engagement with the at least one shift ring bracket.
  • the unlocking cone is arranged or designed in such a way that it comes into engagement with the at least one locking spring before the friction cone can come into engagement with the friction surface of the at least one switching ring.
  • the unlocking cone and the at least one locking spring are appropriately matched to one another.
  • the shift sleeve has at least one recess for receiving the free end of the at least one locking spring, the free end in the recess by moving the shift sleeve in the actuation direction when the shift sleeve is not initially in engagement with the at least one switching ring bracket and the switching ring in the first position is, can be arranged.
  • the switching ring can and can be moved from the first position to the second position by repeatedly moving the shifting sleeve in the actuation direction (in particular by means of the actuator), followed in each case by moving the shift sleeve back into a starting position or non-engagement position (in particular by means of the spring) the return movement of the switching ring from the second position to the first position can be effected in order to transfer or switch the at least one of the bevel gears or the at least one differential bevel gear from the engagement position to the release position and back.
  • the output axes are congruent. The result is a particularly simple structure that is particularly relevant for use in vehicles.
  • the bevel gears and the at least one differential bevel gear are designed as gears, the gears having teeth with a tooth width that is greater than a tooth height of the teeth.
  • gearwheels creates a particularly relevant embodiment for vehicle construction in particular.
  • the outer wheel is also preferably designed as a gear wheel, in particular as a crown wheel (which can be driven, for example, via a cardan shaft) or spur gear (which can be driven, for example, via a spur gear).
  • a gear wheel in particular as a crown wheel (which can be driven, for example, via a cardan shaft) or spur gear (which can be driven, for example, via a spur gear).
  • the bevel gear differential gear according to the invention can also fulfill its function if the bevel gears and the at least one differential bevel gear are not designed as gear wheels but, for example, as friction wheels. It is also conceivable that the outer wheel is not designed as a gear but, for example, as a friction wheel.
  • Gear wheels usually have teeth with a tooth height that is greater than a tooth width, the tooth width being measured as usual along a reference line on the mean pitch cone diameter. Regardless of the usually relatively slow relative rotation of the bevel gears and differential bevel gears to one another - no relative rotation when driving straight ahead; tight corners are usually taken rather slowly, and fast corners are usually rather far, so that the relative rotation typically takes place at rather low speeds even when cornering - good switchability of the bevel gears is desirable. With a view to improved switchability between the release position and the engagement position and vice versa, provision is made for the tooth width to be larger than the tooth height. This promotes rapid meshing of the gears when shifting.
  • the bevel gears and the at least one differential bevel gear are designed as gear wheels, the gear wheels having teeth that each have a Contour have what contour
  • the elliptical geometry means that the contour of the respective tooth in the transition area at least in sections, preferably completely, forms an elliptical arc.
  • a motor vehicle comprising at least one bevel gear differential gear according to the invention for the optional activation and deactivation of the drive of side shafts connected to the bevel gears in a rotationally fixed manner.
  • the bevel gear differential gear according to the invention can be used as an axle differential gear in the motor vehicle in order to selectively switch the drive of the axle equipped with the bevel gear differential gear according to the invention on and off.
  • the outer wheel of the bevel gear differential gear is always driven or can always be driven.
  • a motor vehicle with switchable all-wheel drive can be implemented in this way.
  • FIG. 1 shows a schematic axonometric view of a first exemplary embodiment of a bevel gear differential gear according to the invention, a differential cage being shown cut open in sections and an outer wheel connected in a rotationally fixed manner to the differential cage not being shown
  • FIG. 2 shows a plan view of the bevel gear differential gear of FIG. 1 along an output axis 3 shows a sectional view according to section line BB from FIG. 2, with bevel gears with bevel gears of the bevel gear differential gear being in an engagement position
  • FIG. 5 is a schematic axonometric view of a second embodiment of the bevel gear differential gear according to the invention, the differential cage being shown cut open in sections and the outer gear not being shown
  • FIG. 6 shows a plan view of the bevel gear differential gear of FIG. 5 along one of the output axes
  • FIG. 8 is a sectional view like FIG. 7, but with one of the bevel gears in the release position
  • FIG. 9 is a side view of a third embodiment of the bevel gear differential gear according to the invention with a switching ring as the actuating element, the differential bevel gears being in the engagement position
  • FIG. 10 is a sectional view according to the section line X-X in FIG. 9, the arrows indicating the viewing direction
  • FIG. 14b shows a detailed side view analogous to FIG. 14a after the switching ring has been moved from the first to the second position by moving the switching sleeve in an actuation direction
  • FIG. 14c shows a detailed view analogous to FIG. 14b, the shift sleeve having been moved back into a non-engagement position against the actuation direction
  • FIG. 14d shows a detailed view analogous to FIG. 14c, the shift sleeve having been moved again in the actuating direction in order to release a locking of a locking spring with a locking contour of the shift tab
  • 16 shows a schematic representation of the developed reference profile, the teeth each having a contour optimized for switching in a transition area between a tooth tip and a tooth flank
  • 17a shows an enlarged view of detail XVII in FIG. 16, the contour having an elliptical geometry
  • FIG. 17b shows a view analogous to FIG. 17a, the contour having a geometry with two different radii
  • FIG. 17c shows a view analogous to FIG. 17a, the contour having a flat bevel
  • Fig. 1 shows a schematic representation of a first embodiment of a bevel gear differential 1 according to the invention in an axonometric view, wherein a differential cage 2 of the bevel gear
  • Differential gear 1 is shown in sections for the sake of clarity. If the differential cage 2 is made in one piece, for reasons of assembly a, preferably closable, opening is actually provided, typically in the cut-open area, whereby at least one further opening can also be provided, which is for example arranged symmetrically opposite the opening. If the differential cage 2 is constructed in several parts, it would be conceivable not to provide any openings, although in this case too, of course, at least one, preferably closable, opening can be provided to facilitate assembly or, if necessary, to enable maintenance. Furthermore, for reasons of clarity, an outer wheel 8 which is connected to the differential cage 2 in a rotationally fixed manner (see, for example, FIG. 2) and via which the differential cage 2 can be driven, is not shown in FIG. 1.
  • two bevel gears 3 are arranged opposite one another.
  • the bevel gears 3 are each around an output shaft 5 rotatably mounted, the output shafts 5 of the two bevel gears 3 being congruent in the illustrated embodiments or, in other words, only one output shaft 5 being provided for both bevel gears 3.
  • the bevel gears 3 are non-rotatably connected to a respective side shaft 6, the output shafts 5 being the axes of rotation of the side shafts 6.
  • the differential carrier 2 When the differential carrier 2 is driven via the outer wheel 8, the differential carrier 2 also rotates about the output shafts 5.
  • the bevel gear differential 1 further comprises at least one differential bevel gear 4, which is mounted rotatably about a differential bevel gear axis 7.
  • exactly two differential bevel gears 4 are provided, which are arranged opposite one another in the differential cage 2 so that the differential bevel gear axles 7 are congruent or, in other words, there is only one differential bevel gear axle 7 for both differential bevel gears 4. Accordingly, a single, continuous bearing pin 13 is sufficient for the rotatable mounting of the two differential bevel gears 14, the
  • Differential bevel gear axis 7 is congruent with the longitudinal axis of the bearing pin 13.
  • the at least one differential bevel gear 4 can be displaced along its differential bevel gear axis 7 and / or at least one of the bevel gears 3 along its output axis 5 between an engagement position 9 and a release position 10, wherein in the engagement position 9, but not in the release position 10, the at least one differential bevel gear 4 meshes with the two bevel gears 3 and connects them to one another. That is, in the engagement position 9, the bevel gears 3 and the at least one differential bevel gear 4 are in engagement with one another.
  • the differential cage 2 is driven (via the outer wheel 8), the side shafts 6 are correspondingly driven, the bevel gear differential gear 1 being the usual one
  • the at least one differential bevel gear 4 compensates for the unequal speeds of the bevel gears 3.
  • FIGS. 5, 6, 7 and 8 illustrate the second embodiment, in which only one of the two bevel gears 3 is displaceable.
  • the other bevel gear 3 and the two differential bevel gears 4 cannot be displaced in the second exemplary embodiment.
  • embodiment variants are also conceivable in which both the at least one differential bevel gear 4 and at least one of the bevel gears 3 can be displaced.
  • the bevel gears 3, the differential bevel gears 4 and the outer gear 8 are designed as gear wheels.
  • FIGS. 3 and 4 are a schematic sectional view according to the section line BB from FIG. 2, the arrows in FIG. 2 indicating the viewing direction.
  • the two differential bevel gears 4 are not only rotatably mounted on the bearing pin 13, but also displaceably parallel to the differential bevel gear axis 7 so that they can be moved back and forth between the release position 10 and the engagement position 9.
  • FIG. 3 shows the engagement position 9, in which the two differential bevel gears 4 are each in engagement with two bevel gears 3 and connect the latter to one another in a rotational manner.
  • the two arrows pointing towards one another in FIG. 3 indicate the direction of movement of the two
  • FIG. 4 shows the two differential bevel gears 4 in their release position 10, in which there is no engagement of the differential bevel gears 4 with the bevel gears 3 and the bevel gears 3 are therefore not rotationally connected to one another.
  • the two arrows pointing away from one another in FIG. 4 indicate the direction of movement of the two differential bevel gears 4 from the engagement position 9 into the respective release position 10.
  • an actuating element 11 is provided for each differential bevel gear 4.
  • the actuating elements 11 are also mounted displaceably on the mounting bolt 13 parallel to the differential bevel gear axis 7, whereby they can be moved back and forth between a first position 17 and a second position 18.
  • the actuating elements 11 comprise facing inner sections 14, between which the two
  • Differential bevel gears 4 are arranged. Contact specifically the inner sections 14 the differential bevel gears 4 or the inner sections 14 rest at least in sections on the differential bevel gears 4, whereby a form-fitting operative connection between the differential bevel gears 4 and the inner sections 14 is provided.
  • the inner sections 14 are connected to the differential bevel gears 4 in a fixed or at least rotationally fixed manner (e.g. by claws) to establish the operative connection, the actuating elements 11 then also having to be rotatably mounted on the bearing pin 13 around the differential bevel gear axis 7.
  • the actuating elements 11 furthermore each have an outer section 15 which protrudes outward through the differential cage 2, corresponding recesses being provided in the differential cage 2 for the outer sections 15. By contacting and pressing the respective outer section 15 from the outside, the respective actuating element 11 can be moved from the first position 17 into the second position 18 or held in the second position 18.
  • the differential bevel gears 4 Due to the positive fit or the contact between the inner sections 14 and the differential bevel gears 4, the differential bevel gears 4 are pressed from their release position 10 into the engagement position 9 when the actuating elements 11 are moved from the first position 17 to the second position 18. For example, the differential bevel gears 4 are held in the engagement position 9 when the actuating elements 11 are held in the second position 18. Correspondingly, the actuating elements 11 are shown in the second position 18 in FIG. 3 and in the first position 17 in FIG. 4.
  • the respective actuating element 11 can be moved from the second position 18 into the first position 17 become.
  • at least one spring element (not shown for reasons of clarity) is provided in the first exemplary embodiment, which presses the differential bevel gears 4 and thus also the actuating elements 11 outwards parallel to the differential bevel gear axis 7.
  • the differential bevel gears 4 move from the engagement position 9 into their release positions 10 and the actuating elements 11 move from the second positions 18 into their first positions 17.
  • a shift sleeve 12 is provided in the first exemplary embodiment, which is mounted outside of the differential cage 2 on the differential cage 2 so as to be displaceable parallel to the output shafts 5.
  • shifting the shift sleeve 12 it can be brought into engagement with the respective outer section 15 of the actuating elements 11 in order to move the actuating elements 11 from the first position 17 into the second position 18 or to hold them in the second position 18.
  • the shift sleeve 12 contacts the outer sections 15 and presses against them.
  • the dotted arrow indicates the movement of the shift sleeve 12 parallel to the output axles 5 and towards the pinion pinion axis 7 in order to establish engagement with the outer sections 15 and the actuating elements 11 and thus also the pinion pinion gears 4 inwards parallel to the pinion pinion axis 7 or to move towards one another, whereby the actuating elements 11 are brought into the second position 18 and the differential bevel gears 4 are brought into the engagement position 9 or are held in this.
  • the outer sections 15 have flat contact surfaces 16 which run obliquely to the direction of movement of the shift sleeve 12 or obliquely to the output shafts 5 and one with the output shafts 5 Include acute angles.
  • the shift sleeve 12 has a corresponding counterpart section 21, which forms a contact surface of the shift sleeve 12 and is designed as a counterpart to the contact surfaces 16 in order to facilitate the production of the engagement of the shift sleeve 12 with the outer sections 15.
  • the contact surfaces 16 and the counterpart section 21 slide off one another, so that the actuating elements 11 are moved transversely or essentially normal to the direction of movement of the shift sleeve 12.
  • FIGS. 7 and 8 show a schematic sectional view along the section line C-C from FIG. 6, the arrows in FIG. 6 indicating the viewing direction.
  • the two differential bevel gears 4 are only rotatably mounted on the bearing pin 13.
  • One of the bevel gears 3 (shown on the left in FIGS. 7 and 8) is on the associated side shaft 6 by means of a sliding toothing 20 parallel to the output axis
  • FIG. 8 shows the displaceable bevel gear 3 in its release position 10, in which the displaceable bevel gear 3 is not in engagement with the differential bevel gears 4.
  • the bevel gears 3 are therefore not rotationally connected to one another.
  • the arrow drawn in full in FIG. 8 indicates the direction of movement of the displaceable bevel gear 3 from the engagement position 9 into the release position 10.
  • two actuating elements 11 ' are provided for the displaceable bevel gear 3.
  • the actuating elements 11 ′ are arranged opposite one another and are mounted so as to be displaceable normal to the output shaft 5, the actuating elements 11 ′ being able to be moved back and forth between the first position 17 and the second position 18.
  • the two actuating elements 11 ′ move towards one another or towards the output shaft 5.
  • the two actuating elements 11 ′ move correspondingly from one another or away from the output shaft 5.
  • the actuating elements 11 ′ are in this case along the output shaft 5 and, viewed in the direction of the bearing pin 13, at least in sections in front of the displaceable bevel gear 3 arranged when the displaceable bevel gear 3 is in the engagement position 9.
  • the actuating elements 11 comprise mutually facing inner sections 14, which contact a contact section 19 of the displaceable bevel gear 3 or bear at least sections of the contact section 19, whereby an operative connection is provided between the contact section 19 or the displaceable bevel gear 3 and the inner sections 14.
  • the contact section 19 can be designed in one piece with the rest of the displaceable bevel gear 3 or can be designed as a separate element which is connected to the rest of the displaceable bevel gear 3.
  • the actuating elements 11 ′ furthermore each have an outer section 15 which protrudes outward through the differential cage 2, corresponding recesses being provided in the differential cage 2 for the outer sections 15. By contacting and pressing the respective outer section 15 from the outside, the respective actuating element 11 ′ can be moved from the first position 17 into the second position 18 or held in the second position 18.
  • the displaceable bevel gear 3 Due to the contact between the inner sections 14 and the contact section 19, the displaceable bevel gear 3 is pressed from its release position 10 parallel to the output shaft 5 and towards the differential bevel gear axis 7 into the engagement position 9 when the actuating elements 11 'move from the first position 17 into the second position 18 can be moved.
  • the displaceable bevel gear 3 is held in the engagement position 9 when the actuating elements 11 ′ are held in the second position 18.
  • the actuating elements 11 ′ are shown in the second position 18 in FIG. 7 and in the first position 17 in FIG. 8.
  • the contact section 19 has a contact surface 22 which runs obliquely to the direction of movement of the actuating elements 11' or obliquely to the pinion pinion axis 7 and with the pinion pinion axis 7 includes an acute angle.
  • the actuating elements 11 ′ each have a corresponding counterpart section 23, which is designed as a counterpart to the contact surface 22.
  • the counterpart sections 23 and the contact surface 22 can slide on one another, so that the contact section 19 or the displaceable bevel gear 3 is moved transversely or essentially normal to the direction of movement of the actuating elements 11 '.
  • the respective actuating element 11 ′ can be moved from the second position 18 into the first position 17.
  • several spring elements are provided in the second embodiment
  • the shift sleeve 12 is also provided in the second embodiment, which outside of the differential cage 2 on the differential cage 2 parallel to the output axes 5 is slidably mounted. By shifting the shift sleeve 12, it can be brought into engagement with the respective outer section 15 of the actuating elements 11 'in order to move the actuating elements 11' from the first position 17 into the second position 18 or in the second position
  • the shift sleeve 12 contacts the outer sections 15 and presses against them.
  • the dotted arrow indicates the movement of the shift sleeve 12 parallel to the output axes 5 and towards the pinion pinion axis 7 in order to establish engagement with the outer sections 15 and to move the actuating elements 11 'inwards or towards one another.
  • the actuating elements 11 ' are brought into the second position 18, the displaceable bevel gear 3 being brought into the engagement position 9 or held in this position by being displaced parallel to the output shaft 5 and towards the differential bevel gear shaft 7.
  • the outer sections 15 have flat contact surfaces 16 which are inclined to The direction of movement of the shift sleeve 12 or at an angle to the output shafts 5 and enclose an acute angle with the output shafts 5.
  • the shift sleeve 12 has a corresponding counterpart section 21 which is designed as a counterpart to the contact surfaces 16 in order to facilitate the production of the engagement of the shift collar 12 with the outer sections 15.
  • the counterpart section 21 and the contact surfaces 16 slide on one another, so that the
  • Actuating elements 11 ' are moved transversely or essentially normal to the direction of movement of the shift sleeve 12.
  • a third embodiment of a bevel gear differential 1 according to the invention is shown, which has a switching ring 28, see. Fig. 10, as an actuating element for the two differential bevel gears 4, resulting in an extremely compact design.
  • the differential bevel gears 4 are shown in FIGS. 9 and 10 in the engagement position 9.
  • the differential bevel gears 4 are mounted on the bearing pin 13, a compression spring 40 being arranged on the bearing pin 13 between the differential bevel gears 4, which is compressed in the engagement position 9 by the differential bevel gears, see first position 17.
  • the switching ring 28 has two ramps 29 with eccentric geometry, which form the inner section of the actuating element and press against the differential bevel gears 4 via intermediate pieces 41 or are in operative connection with them.
  • the switching ring 28 has two switching ring tabs 30 which form the outer section of the actuating element and can be contacted by the switching sleeve 12 in order to move the switching ring 28 from the first position 17 to the second position 18 move, the second position 18 being associated with the release position 10 of the differential bevel gears 4.
  • the switching ring 28 can be rotated relative to the differential cage 2 around the output shaft 5 by a switching angle g, the switching angle g being approx. 90 ° in the exemplary embodiment shown, cf. 12. Due to the eccentric geometry of the ramps 29, the differential bevel gears 4 located in the release position 10 are pressed into the engagement position 9 or moved along the bearing pin 13 against the force of the compression spring 40 into the engagement position 9 (radially inward) when the switching ring 28 is rotated by the switching angle g from the second position 18 to the first position 17, see. Relative rotation 42 'in Fig. 12.
  • the switching ring 28 moves or rotates with the differential carrier 2 about the output shaft 5.
  • the shift sleeve 12 is moved from a non-engagement position 43 in an actuation direction 37 parallel to the output shaft 5 towards the shift ring 28.
  • an actuator for example an electromagnet (not shown), is provided.
  • two torsion springs 44 are tensioned in the exemplary embodiment shown.
  • the spring force of the torsion springs 44 can subsequently be used to move the switching ring 28 back into the first position 17.
  • two locking springs 33 are provided in the illustrated embodiment, which each lock with a locking contour 34 of the switching ring tabs 30 to keep the switching ring 28 in the second position 18 to hold.
  • the locking contour 34 has a stop section 35 on which the respective locking spring 33, more precisely a region of the respective locking spring 33 having a free end, can slide at the beginning of the relative rotation 42 of the switching ring 28.
  • the locking spring 33 locks with a locking section 36 of the locking contour 34 corresponds to the second position 18, arranged behind the run-on section 35.
  • Non-engagement position 43 can be transferred, whereby no actuator is necessary for this, but for example a simple spring (not shown) can be provided.
  • the shift sleeve 12 has an unlocking cone 38.
  • the free ends of the locking springs 33 slide on the unlocking cone 38 in order to release the locking by lifting the locking springs 33 over the respective locking section 36.
  • the tensioned torsion springs 44 then move the switching ring 28 from the second position 18 back into the first position 17, the differential bevel gears 4 being pushed back into the engagement position 9 via the ramps 29.
  • FIGS. 14a, 14b, 14c and 14d The sequence described above is illustrated in FIGS. 14a, 14b, 14c and 14d.
  • the shift ring 28 is in the first position 17 and the shift sleeve 12 is in the disengaged position 43.
  • the free end of the locking springs 33 is first arranged in a locking spring receptacle 39 designed as a groove.
  • the friction cone 31 then comes into contact with the friction surfaces 32, as a result of which the switching ring 28 is moved into the second position 18.
  • the respective locking contour 34 is brought into engagement with the respective locking spring 33, the latter being locked in the locking section 36 when the switching ring 28 has arrived in the second position 18. 14b shows this state.
  • the shift sleeve 12 can be moved back into the disengaged position 43 by means of the spring (not shown).
  • the respective gear wheel has teeth 24 with a tooth width b that is greater than a tooth height h of the teeth 24, see shows developed reference profile of such a gear.
  • the tooth width b is measured as usual along a reference line 27 on the mean pitch cone diameter.
  • the teeth 24 each have a contour optimized for switching in a transition area between a tooth tip 25 and a tooth flank 26, see FIG. 16, which is a schematic representation of a developed reference profile of such a gear shows.
  • FIG. 17a illustrates the case that the contour has an elliptical geometry, ie that the contour of the respective tooth 24 in the transition area at least partially, preferably completely, forms an elliptical arc.
  • FIG. 17b again illustrates the case in which the contour has a geometry with two different radii R, r.
  • the radius R is larger than the radius r, the radius R being used first, and then the radius r, as seen at the transition from the head region 25 to the flank 26.
  • FIG. 17c finally illustrates the case in which the contour has a flat bevel.
  • a substantially flat transition area between the tooth tip 25 and the tooth flank 26 here, with the substantially flat tooth tip 25, encloses a bevel angle a which is only between 5 ° and 15 °.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une transmission (1) de différentiel à roues coniques comprenant une cage (2) de différentiel, à l'intérieur de laquelle sont disposées deux roues coniques (3) en regard l'une de l'autre, et chacune des roues coniques (3) étant montée rotative autour d'un arbre de sortie (5), la transmission (1) de différentiel à roues coniques comprenant en outre au moins une roue conique de compensation (4) qui est montée dans la cage (2) de différentiel de sorte à pouvoir tourner autour d'un arbre (7) de roue conique de compensation. Selon l'invention, ladite ou lesdites roues coniques de compensation (4) sont mobiles le long de leur arbre (7) de roue conique de compensation et/ou au moins une des roues coniques (3) est mobile le long de son arbre de sortie (5) entre une position en prise (9) et une position libérée (10), de sorte que, dans la position en prise (9), mais pas dans la position libérée (10), ladite roue conique de compensation (4) est en prise avec les deux roues coniques (3) et les relie l'une à l'autre.
PCT/EP2020/079775 2019-10-29 2020-10-22 Transmission de différentiel à roues coniques WO2021083788A1 (fr)

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DE102019007513.7A DE102019007513A1 (de) 2019-10-29 2019-10-29 Kegelrad-differentialgetriebe
DE102019007513.7 2019-10-29

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WO2021083788A1 true WO2021083788A1 (fr) 2021-05-06

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CN115076329A (zh) * 2022-06-13 2022-09-20 中国第一汽车股份有限公司 一种集成断开机构的差速器总成及车辆

Citations (6)

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Publication number Priority date Publication date Assignee Title
DE19716386A1 (de) 1996-04-19 1997-11-06 Tochigi Fuji Sangyo Kk Ausgleichsvorrichtung
DE19721091A1 (de) * 1996-05-21 1997-11-27 Dana Corp Zweistellungs-Antriebstrenneinrichtungen für Fahrzeuge
US6027422A (en) 1997-09-11 2000-02-22 Tochigi Fuji Sangyo Kabushiki Kaisha Switching synchronous apparatus for four wheel drive vehicle
DE102009018572A1 (de) * 2008-05-02 2009-11-05 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Getriebeanordnung mit einem Differential und einer Notentriegelungseinrichtung
DE102016220250A1 (de) * 2016-10-17 2018-04-19 Robert Bosch Gmbh Differentialgetriebe für ein Kraftfahrzeug und Verfahren zum Betreiben eines Differentialgetriebes für ein Kraftfahrzeug
DE102016221016A1 (de) * 2016-10-26 2018-04-26 Robert Bosch Gmbh Differentialgetriebe für ein Kraftfahrzeug und Verfahren zum Betreiben eines Differentialgetriebes für ein Kraftfahrzeug

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE200862C (fr) *
DE102018218536A1 (de) * 2018-10-30 2020-04-30 Zf Friedrichshafen Ag Differentialgetriebe
DE102019202599B3 (de) * 2019-02-26 2020-06-04 Audi Ag Antriebsanordnung für eine Fahrzeugachse

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19716386A1 (de) 1996-04-19 1997-11-06 Tochigi Fuji Sangyo Kk Ausgleichsvorrichtung
DE19721091A1 (de) * 1996-05-21 1997-11-27 Dana Corp Zweistellungs-Antriebstrenneinrichtungen für Fahrzeuge
US6027422A (en) 1997-09-11 2000-02-22 Tochigi Fuji Sangyo Kabushiki Kaisha Switching synchronous apparatus for four wheel drive vehicle
DE102009018572A1 (de) * 2008-05-02 2009-11-05 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Getriebeanordnung mit einem Differential und einer Notentriegelungseinrichtung
DE102016220250A1 (de) * 2016-10-17 2018-04-19 Robert Bosch Gmbh Differentialgetriebe für ein Kraftfahrzeug und Verfahren zum Betreiben eines Differentialgetriebes für ein Kraftfahrzeug
DE102016221016A1 (de) * 2016-10-26 2018-04-26 Robert Bosch Gmbh Differentialgetriebe für ein Kraftfahrzeug und Verfahren zum Betreiben eines Differentialgetriebes für ein Kraftfahrzeug

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