WO2006032295A1 - Sperranordnung mit verstellung durch magnetorheologisches fluid - Google Patents
Sperranordnung mit verstellung durch magnetorheologisches fluid Download PDFInfo
- Publication number
- WO2006032295A1 WO2006032295A1 PCT/EP2004/010787 EP2004010787W WO2006032295A1 WO 2006032295 A1 WO2006032295 A1 WO 2006032295A1 EP 2004010787 W EP2004010787 W EP 2004010787W WO 2006032295 A1 WO2006032295 A1 WO 2006032295A1
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- WO
- WIPO (PCT)
- Prior art keywords
- locking
- chamber
- differential
- coupling
- ring gear
- Prior art date
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Classifications
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- 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
- F16H48/26—Arrangements for suppressing or influencing the differential action, e.g. locking devices using fluid action, e.g. viscous clutches
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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
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- 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
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
-
- 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
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
-
- 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
- F16H2048/02—Transfer gears for influencing drive between outputs
- F16H2048/04—Transfer gears for influencing drive between outputs having unequal torque transfer between two outputs
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- 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
- F16H2048/204—Control of arrangements for suppressing differential actions
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- 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
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
- F16H2048/346—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a linear motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/40—Constructional details characterised by features of the rotating cases
Definitions
- the invention relates to a locking arrangement, in particular for use in Antriebs ⁇ strand of a motor vehicle, which may be in the form of a locking clutch or a Sperrdiffe- rentials.
- Locking clutches usually comprise at least two coupling elements which can be coupled together to transmit a torque.
- Locking differentials usually comprise an input part as well as two output parts, which are connected to one another in drive connection for transmitting a torque, wherein a compensating effect can be generated between the output parts.
- the DE 103 04 140.0-12 shows a friction clutch with two relatively rotatable coupling elements which are rotatably miteinan ⁇ by means of a disk set coupled.
- an annular chamber is formed which on the one hand is delimited by a piston for actuating the disk pack and on the other hand by a cover and is filled with a magnetorheological fluid.
- a rotor disc is arranged, which is rotatably connected to one of the coupling elements.
- US Pat. No. 6,585,616 B1 shows a differential gearbox with two controllable multi-plate clutches.
- the differential gear is in the form of a bevel gear differential and includes two side-shaft gears that are driven by differential gears encircling the differential cage.
- the multi-plate clutches are provided, which are filled with magneto-rheological fluid.
- magneto-rheological fluid By activating magnetic coils, which are arranged radially outside the multi-disc clutches, the viscosity of the magneto-rheological fluid changes, whereby a blocking effect between the differential carrier and the side-shaft gears is achieved.
- EP 446 863 B1 discloses a speed-sensing clutch for connecting a drive train in a motor vehicle having a plurality of drive trains. Such arrangements serve, in a normally driven only on the axis of the first drive train vehicle with insufficient traction zuzutouch also the axis of the second drive train. For this purpose, a so-called viscous coupling is used.
- the present invention has for its object to provide a lock assembly with a simple structure, which has a high power density, good controllability and short activation times.
- Such a locking arrangement can be designed in the form of a lock-up clutch or a locking differential.
- a first solution of the problem consists in a blocking coupling for coupling a first coupling part with a second coupling part rotatable relative thereto, comprising a gear arrangement for torque transmission between the first coupling part and the second coupling part, a chamber sealed to the outside, in which the gear arrangement is arranged is net and which is at least partially filled with a magnetorheological fluid, and a controllable magnetic coil which is adjacent to the chamber and can generate a magnetic flux through the chamber, wherein the viscosity of the magnetorheological fluid is changed.
- This lock-up clutch is that it is simple and has a high power density.
- the magnetic coil is electrically driven, so that the strength of the magnetic field can be set as desired by appropriate selection of the current or the voltage. This results in a high coupling accuracy and short activation times, so that it is possible to react quickly to changing driving conditions.
- the configuration of magnetic coil, chamber and gear arrangement is coordinated so that upon excitation of the magnetic coil as uniform a magnetic field in the region of the chamber is generated, so that a uniform viscosity of the liquid can be adjusted.
- the magnetic field is generated, in particular in the region of the rolling toothing interventions of the toothing arrangement.
- the gear arrangement is designed in the manner of a planetary gear.
- the gear arrangement preferably comprises a non-rotatably connected to the first coupling member ring gear, rotatably connected to the second coupling member sun gear and a plurality of the ring gear on the one hand and the sun gear meshing planetary gears, wherein between the ring gear and the sun filled with magnetorheological fluid chamber is formed.
- the gaps or gear teeth between the gears are covered by the chamber.
- the magnetic coil is arranged according to a preferred embodiment such that a torusfömiges magnetic field is generated which extends through at least some of the Verzah ⁇ Vietnameseseingriffe the gear arrangement.
- the magnet coil can be arranged axially adjacent to the toothing arrangement.
- the blocking coupling thus formed has a small radial size.
- the magnetic coil can also be arranged radially outside of the toothing arrangement. This is particularly favorable when the axial space of the lock-up clutch is limited.
- at least the ring gear, the planet gears and the sun gear are made of ferromagnetic material.
- the gears between the ring gear and the planet gears and between the planet gears and the sun gear may be straight or helical gears.
- an axial force component is generated, which leads to greater friction losses.
- an active blocking moment is superimposed on the basic blocking moment caused by friction, which arises due to the work of deformation of the magnetorheological fluid.
- the deformation work is composed of crushing, pumping and shearing work.
- the teeth between the ring gear and the planet gears are each axially shorter than the teeth between the Planetenrä ⁇ countries and the sun designed. In this way, a particularly homogeneous magnetic field results.
- a chamber volume reducing filler can be provided, in which the planet gears are rotatably supported. So only a small amount of magnetorheological fluid is required.
- the planet gears are preferably rotatably supported in a cage.
- the cage has at least one disc which is arranged on the side facing away from the magnetic coil of the planetary gears.
- the cage may also comprise two discs, wherein the planet gears are arranged axially between them and rotatably mounted on pins.
- the magnetic coil is an ⁇ arranged disc of ferromagnetic material, so that it is attracted to this when activating the magnetic coil.
- the Pla ⁇ netenver are held in the cage so that they are limited in the circumferential direction movable.
- the cage for example, in the circumferential direction extending Langlö ⁇ cher, in which the planetary gears are mounted.
- the cage further comprises axial openings which are aligned with the toothing engagements between the planetary gears and the ring gear and the sun gear.
- switched off electromagnet - magnetorheological fluid from the areas of the intermeshing engagements pass through the openings of the cage in the reservoir.
- the activated state ie when the electromagnet is switched on, due to the increased viscosity of the magnetorheological fluid, deformation work is performed between the toothing interventions. Due to the additional shear forces, the cage is rotated in the circumferential direction, so that the openings no longer align with the toothing engagements.
- the chamber is thus encapsulated on the front side, so that the work of deformation is superimposed on additional pumping and shearing work.
- This embodiment thus causes a more favorable ratio between the maximum achievable torque and the drag torque in the non-activated state.
- a support disk is fixedly connected to the first coupling part, which delimits the chamber in the direction of the magnet coil and against which the planetary gears can be axially supported. Sealing means are provided between the support disk and a cylindrical section of the sun gear. These prevent magnetorheological fluid from being squeezed out of the chamber as the gears roll.
- the support disk is preferably paramagnetic, so that - viewed in longitudinal section - a circular magnetic field is generated around the magnetic coil.
- the filled with magnetorheological fluid chamber is connected to a preferred embodiment with a reservoir.
- a reservoir This preferably has a variable volume so that volume changes resulting from temperature changes in the magnetorheological fluid can be compensated.
- the reservoir is limited by a piston, which is acted upon by spring means.
- the piston and the spring means are preferably arranged in a tubular portion of the second coupling part and axially supported against a cover. Eben ⁇ so the reservoir can also be arranged in the first coupling part.
- the chamber may contain, in addition to the magnetorheological fluid to a small extent, a gas volume whose compressibility produces the volume compensation.
- a housing is provided, in which the Ver ⁇ toothing arrangement and the Magnetspuie are arranged.
- the housing is preferably cup-shaped and has an outer wall portion and a coaxial inner wall portion.
- the first coupling part can be rotatably mounted in the outer wall section and the second coupling part rotatably mounted on the inner wall section.
- the first coupling part connecting means for non-rotatable connection with a longitudinal drive shaft of a motor vehicle, and the second coupling part An ⁇ connecting means for non-rotatable connection with an axle differential.
- the second connecting means are preferably designed in the form of a longitudinal toothing, in which an axle journal can engage for torque transmission.
- the locking clutch according to the invention is versatile. After a first use, the lock-up clutch is arranged in the drive train of a motor vehicle, which has a permanently driven first axle and a second axle which can be engaged as required, wherein the lock-up clutch serves for coupling or uncoupling the second axle.
- the blocking clutch is controlled as required via a driving dynamics controller. In this case, the torque to be transmitted by the corresponding strength of the magnetic field, i. be set as desired by appropriate choice of the current or the voltage. This results in a high coupling accuracy and short activation times, so that it is possible to react quickly to changing driving conditions.
- the lock-up clutch is arranged in the drive train of a motor vehicle with a permanently driven first axle and a second axle which can be engaged as required.
- the lock-up clutch is connected upstream of a further speed-sensing additional clutch and serves for switching on or off this speed-sensing further clutch.
- the zu ⁇ switchable second axis is coupled, wherein a maximum torque capacity is available, while the second axis is decoupled in the off state of Antriebs ⁇ strand.
- This application has the advantage that it is possible to dispense with an elaborate control of the further clutch and that the drive train ESP is disconnected by the decoupling of the speed-sensing further clutch. becomes compatible.
- ESP-compatible in this context means that interventions in the driving dynamics of the motor vehicle can be done easily by means of a driving dynamics controller.
- the speed-sensing further clutch is usually designed in the form of a viscous coupling.
- a second solution of the above object is a limited slip differential for use in the drive train of a motor vehicle, comprising an input part which can be driven in rotation; a first output part and a second output part, which are respectively drive-connected to the input part via differential gears; an outwardly sealed chamber in which the differential gears are disposed and which is at least partially filled with a magnetorheological fluid; and a controllable solenoid disposed adjacent to the chamber and capable of generating a magnetic flux across the chamber, wherein the viscosity of the magnetorheological fluid is varied.
- the advantage of this limited slip differential is its simple structure and high power density.
- the magnetic coil is electrically driven, so that the strength of the magnetic field can be adjusted by a suitable choice of the current intensity or the voltage. This results in a high switching accuracy and short activation times, so that it can be quickly responded to changing driving conditions.
- the configuration of magnetic coil, chamber and differential gears is coordinated so that upon excitation of the solenoid as gleich ⁇ a uniform magnetic field is generated in the chamber, so that a uniform viscosity of the liquid can be adjusted. In this case, the magnetic field is generated in particular in the region of the rolling toothing interventions of the differential wheels.
- the limited slip differential is designed in the form of a planetary differential and comprises a ring gear, a sun gear, a plurality of differentiated wheels, which mesh with the ring gear on the one hand and the sun gear on the other hand. and a web arrangement for supporting the differential wheels, where between the ring gear and the sun gear filled with magnetorheological fluid chamber is formed.
- a limited slip differential in the form of a bevel gear differential or a Kronenraddifferentials. The gaps or toothing play between the differential wheels and the toothed wheels thus located in the toothed engagement are included in the chamber.
- the limited slip differential can be connected as desired in the drive train of a motor vehicle.
- the ring gear can serve as a torque input, so that the sun gear and the web arrangement serve as torque outputs.
- the limited slip differential operates as a center differential with a fixed base ratio between two driven axles. By activating the solenoid, the differential is locked so that torque balancing between the outputs is prevented.
- the magnetic coil is arranged according to a preferred embodiment such that a toroidal magnetic field is generated which extends through at least some of the interlocking interventions of the planetary differential.
- the magnet coil is preferably arranged axially adjacent to the toothing arrangement.
- at least the ring gear, the differential gears and the sun gear are made of ferromagnetic material. This ensures that the magnetic circuit between one of the poles of the magnetic coil, the ring gear, the Planetenrä ⁇ and the sun gear to the second pole of the solenoid is closed.
- the differential lock according to the invention can also be designed in the form of an axle differential.
- the gears between the ring gear and the planet gears and between the planet gears and the sun gear may be straight or helical gears.
- an axial force component is generated, which leads to greater friction losses.
- the toothings between the ring gear and the planetary gears are each designed to be shorter axially than the toothings between the planetary gears and the sun gear. This creates a particularly homogeneous magnetic field.
- In the chamber may be provided a the chamber volume reducing filler in which the differential wheels are rotatably supported. Thus, only a small amount of the magnetorheological fluid is required.
- the web arrangement comprises at least one flange which is arranged on the side facing away from the magnetic coil of the differential wheels.
- a support disk is fixedly connected to the ring gear which delimits the chamber in the direction of the magnet coil.
- sealing means between the support disc and a cylindrical portion of the sun gear. These prevent magnetorheological fluid from being squeezed out of the chamber as the gears roll.
- the support disk and / or the web arrangement are preferably paramagnetic, so that - viewed in longitudinal section - a nik ⁇ shaped magnetic field is generated around the magnetic coil.
- the filled with magnetorheological fluid chamber is connected to a preferred embodiment with a reservoir.
- This preferably has a variable volume so that volume changes resulting from temperature changes in the magnetorheological fluid can be compensated.
- the reservoir is limited by a piston, which is acted upon by spring means.
- the piston and the spring means are preferably arranged in a tubular portion of the second output part and axially supported against a cover.
- the chamber may to a small extent contain a gas volume whose compressibility produces the volume compensation.
- the locking differential is rotatably mounted in a housing.
- the housing is preferably pot-shaped and has an annular space for receiving the magnetic coil.
- the first output part is rotatably mounted in a cylindrical bearing portion, while the second output part is mounted radially in the first output part coaxial with the axis of rotation.
- Figure 1 shows a first embodiment of a locking clutch according to the invention a) in longitudinal section; b) in cross-section according to section line l-l of Figure 1a);
- Figure 2 shows a second embodiment of a locking coupling according to the invention with connecting flange
- Figure 3 shows a third embodiment of a lock clutch according to the invention with a shortened toothing
- Figure 4 shows a fourth embodiment of a locking clutch according to the invention with optimized seal
- Figure 5 shows a fifth embodiment of a lock clutch according to the invention a) with a simple cage for the planet gears in longitudinal section; b) a cross section through the cage plane according to Figure 5 a);
- Figure 6 shows a sixth embodiment of a locking coupling according to the invention with double cage for the planetary gears
- Figure 7 shows a seventh embodiment of a lock clutch according to the invention with a compact hub a) in longitudinal section; b) in cross-section according to section line VII-VIl of Figure 7a);
- Figure 8 shows a seventh embodiment of a locking clutch according to the invention with a compact hub
- Figure 9 shows an eighth embodiment of a lock clutch according to the invention with two groups of planetary gears a) in longitudinal section; b) the principle of the planetary arrangement in cross section; c) in longitudinal section showing the magnetic field lines;
- Figure 10 shows a motor vehicle with inventive locking clutch in L Lucassan ⁇ drive train
- FIG. 11 shows a motor vehicle having a locking clutch according to the invention and a downstream viscous coupling in the drive train;
- Figure 12 is an inventive locking differential a) in longitudinal section; b) in cross-section.
- FIG. 1 shows a blocking coupling with a housing 2 and a first coupling part 3 rotatably mounted therefor and a second coupling part 4 rotatably coupled thereto.
- the first coupling part 3 has first connecting means 5 which are used to introduce a torque, for example from a longitudinal drive shaft of a motor vehicle. serve in the lockup clutch.
- the second coupling part 4 has second connecting means 6, which are designed in the form of a longitudinal toothing and for mosfe ⁇ most insertion of a connecting shaft, not shown here, for example, for driving an axle differential serve.
- the first coupling part 3 and the second coupling part 4 are each rotatably mounted in the housing 2 on a common axis of rotation.
- a rolling bearing 7 is provided between the first coupling part 3 and the housing 2. If necessary, the second coupling part 4 can be slidably mounted relative to the housing 2.
- the housing 2 is substantially pot-shaped and has a zylinderförmi ⁇ gene outer wall portion 9 and a coaxial for this zylin ⁇ derförmigen inner wall portion 10 and a connecting these two bottom 12. Between the outer wall portion 9, the inner Wandungs- section 10 and the Bottom 12, an annular space 13 is formed, in which a Verzah ⁇ nungsan extract 14 and a magnetic coil 25 is arranged.
- the toothing arrangement 14 is designed in the form of a planetary gear mechanism and comprises a ring gear 15 which is connected in a rotationally fixed manner to the first coupling part 3, a ring gear 15 connected to the second coupling part 3.
- a sealed chamber 18 is formed between the ring gear 15 and the sun gear 16, which is delimited in the axial direction on the one hand by a flange 19 and on the other hand by a support disk 20 of the first coupling part 3.
- the support disk 20 carries a sealing ring 22 which seals the chamber to the outside.
- the chamber 18 is at least largely filled with a magnetorheological fluid which can be magnetized by a magnet coil 25 arranged in the housing 2.
- the operation of the lock-up clutch is as follows.
- the first coupling part 3, the planetary gear 14 and the second Kupplungs ⁇ part 4 rotate together at the same speed about the axis of rotation A. occur different speeds between the first coupling part 3 and the second coupling part 4, for example, due to itself Changing driving conditions between the front and the rear axle of the motor vehicle, there is a difference in rotational speed between the ring gear 15 and the sun gear 16.
- the planet gears 17 roll ge compared to the ring gear 15 and the sun gear 16, wherein the located in the chamber 18 Magnetorheological fluid is displaced by each successive abconsultedl ⁇ Zenden tooth flanks.
- a reservoir 24 is provided in order to compensate for the resulting increase in volume of the magnetorheological fluid.
- a reservoir 24 is provided in order to compensate for the resulting increase in volume of the magnetorheological fluid.
- This is located in a tubular section of the second coupling part 4, in which a piston 26 is seated in an axially displaceable manner.
- the piston 26 is acted upon axially by spring means 27 which, on the one hand, are axially supported relative to a cover 29 which is firmly seated in the pipe section.
- the magnetic coil 25 is turned on, so that the resulting magnetic field puts the magnetorheological fluid into a highly viscous or plastic state.
- the planetary gears 17 are prevented from freely shifting with respect to the ring gear 15 and the sun gear 16, respectively, so that torque is transmitted from the ring gear 15 to the sun gear 16.
- magnetizing the magnetorheological fluid increases its viscosity, so that a rolling motion between the planet gears 17 and the ring gear 15 and the sun gear 16 is decelerated.
- the drag torque can be varied. This is due to the displacement of the magnetorheological fluid, even when the solenoid is de activated. While the drag torque in the case of spur gears is relatively small, helical gears cause an axial force component, which results in greater frictional forces.
- the housing 2, the ring gear 15, the sun gear 16 and the planet gears 17 are made of ferromagnetic material.
- ferromagnetic material For this example, non-austenitic steels come into question.
- the support disk 20 arranged between the planet gears 17 and the magnet coil 25 is preferably made of a non-magnetic material, for which austenitic steels or aluminum are preferably used.
- the configuration of magnetic coils, chamber and planetary gear is coordinated so that upon excitation of the magnetic coil as uniform a magnetic field in the region of the chamber er ⁇ is witnessed, so that a uniform viscosity of the liquid can be adjusted.
- Figure 1 b shows a cross section through the lock-up clutch.
- the ring gear 15 the sun gear 16 and the meshing with two wheels planet gears 17 er ⁇ visible.
- eight planet gears distributed over the circumference are provided, the number of which can be varied depending on the torque to be transmitted.
- Figure 2 shows a second embodiment of the lock-up clutch, with respect to their Structure substantially similar to that of Figure 1.
- the first coupling part 3 2 has a pin 30 with a spline 32 for introducing a torque.
- a roller bearing I 2 is provided, which is arranged with a bearing outer ring in a cover part 35 and a bearing inner ring on a bearing portion 36 of the connecting flange 33.
- the advantage of this embodiment is that the rolling bearing I 2 has a small diameter and can therefore be produced cost-effectively.
- the smaller Wälzla ⁇ ger generates 7 2 only low drag torque.
- Figure 3 shows a third embodiment of the lock-up clutch, which corresponds in terms of their construction substantially to that of Figure 1.
- the present embodiment differs from that according to FIG. 1 in that the toothing of the ring gear 15 3 is axially shorter than the toothing of the planet wheels 17. In this way, a particularly strong magnetic field can be achieved when the magnet coil 25 is activated, because the density the magnetic flux is greater. In this way arises between the sun gear 16 and the ring gear 15 3, a particularly homogeneous magnetic field in the magnetorheological fluid, so that the viscosity over the radial extent is constant.
- Figure 4 shows a fourth embodiment of the lock-up clutch, with respect to their Structure substantially similar to that of Figure 1.
- the embodiment of Figure 4 is characterized, ' that the support plate 2O 4 , which is fixedly connected to the first coupling part 3 4 and the chamber 18 in the direction of the magnetic coil 25 4 axially limited, radially inward reaches up to an outer cylindrical portion of the sun gear 16 ,
- the pump pressure generated by the rolling movement of the gears of the magnetorheological fluid does not act directly on the sealing ring 22, but presses against the support disk 2O 4th
- the annular gap between the cylindrical section of the sun gear 16 and the support disk 20 4 is displaced radially outward such that the sealing surface lies outside the alignment of the toothing between the sun gear 16 and the planet gears 17. It would also be ensured that the pressure generated by the magnetorheological fluid in the toothed area does not act directly on the sealing ring 22.
- FIG. 5 shows a fifth embodiment of the lock-up clutch, which corresponds in terms of their construction substantially to that of Figure 1.
- the special feature of this embodiment is that the Plane ⁇ tenmann 17 5 are held by a disc-shaped cage 37 in the circumferential direction to each other.
- the planetary gears 17 are each held rotatably mounted on the cage 37 bolts 38.
- the cage 37 has in the area between two planet gears 17 circumferentially distributed openings for the passage of gnetorheologischen fluid in the reservoir 24.
- the advantage of this ists ⁇ is that the tolerances between the ring gear 15, the planetary gears 17 and the sun gear 16th can be kept rough, which has a positive effect on the manufac turing costs.
- the coarse tolerances reduce the drag torque in the non-activated state of the magnet coil 25, so that the friction losses are minimized.
- the disc-shaped cage 37 consists of ferromagnetic material and is located on the side facing away from the magnetic coil 25 of the planet gears 17. In this way, the cage 37 acts as an armature disc and is When activating the magnetic field together with the planetary gears 17 in the direction Magnet ⁇ coil 25 attracted. This results in additional friction and reduction of the axial gap dimensions of the planetary gear set in the chamber 18, thus increasing the barrier effect created by plastication of the magnetorheological fluid. By this measure, the power density of the lock-up clutch is particularly large.
- FIG. 5b shows, in particular, the cage from FIG. 5a), to the description of which reference is made.
- the planet gears 17 are held in the cage 37 5 so that they are limited in the circumferential direction movable.
- Hier ⁇ for the cage 37 5 extending in the circumferential direction slots 28, in which the planet gears 17 are attached.
- the bolts 38 engage in the oblong holes 28, spring elements 50 being provided between the bolts 28 and the wall bounding the oblong holes in the circumferential direction. These allow a limited relative rotation of the cage 37 5 to the planetary gears 17.
- the cage 37 5 further comprises axia ⁇ le openings 31, 31 ' , which are aligned with the teeth meshing between the Planetenrä ⁇ the 17 and the ring gear 15 and the sun gear 16.
- magnetorheological fluid can pass from the regions of the meshing interventions through the apertures 31, 31 'of the cage into the reservoir.
- the activated state ie when the electromagnet is switched on, deformation work is performed between the toothed engagements due to the increased viscosity of the magnetorheological fluid.
- FIG. 6 A further embodiment is shown in FIG. 6, which substantially corresponds to that of FIG. 5, to the description of which reference is made.
- a cage 37 6 is provided, which comprises two discs 39, 40 coupled to one another, between which the planet wheels 17 are rotatably held.
- openings 17 are provided in the circumferential direction between the planetary gears, which serve for the passage of electromagnetic fluid into the reservoir 24.
- the disc 40 remote from the magnet coil 25 consists of magnetic material, while the disc 39 adjacent to the magnet coil 39 is nonmagnetic. In this way, the disk 40 can act as an armature disk, so that the planetary gears 17 are pulled in the direction of the magnetic coil 25 when generating a magnetic field, which has the advantages described in the description of FIG. 5.
- Figure 7 shows a seventh embodiment of the lock-up clutch, which corresponds in terms of their construction substantially to that of Figure 1.
- the second coupling part 4 7 is designed in one piece with the sun gear 16 7 and has a substantially tubular construction.
- An inner shoulder 41 serves as a contact surface for the lid 29.
- the present embodiment has the advantage that the second Kupp ⁇ ment part 4 7 can be made easier, so that manufacturing costs can be saved.
- the second coupling part 4 7 , the planet gears 17, the ring gear 15 7 and the bottom 12 of the housing 2 are made of ferromagnetic material.
- the flange portion 19 7 of the first coupling part 3 7 and the outer wall portion 9 7 of the housing 2 are not magnetic.
- the flange portion 19 7 is fixedly connected to the ring gear 15 7 , for which any connection means, such as welding, a screw or a spline with axial securing means come into question.
- the ring gear 15 7 has a cylindrical portion 42 which extends up to the bottom 12 of the housing 2 to close the magnetic circuit.
- the bottom 12 can be firmly connected to the outer wall portion 9 7 of the housing 2 in beechi ⁇ ge manner.
- a ringver ⁇ bond or a welded joint in question In Fig. 7c) the magnetic flux is through a similar lock-up clutch, as shown in Figure 7a), can be seen.
- the description of the lockup clutch according to FIG. 7a) is hereby incorporated by reference.
- the magnetic field is conducted through the outer wall portion 9 ⁇ of the housing 2, which in the present case is ferromagnetic.
- This embodiment offers the advantage that a larger radial annular space is available for the magnetic coil 25, which can thus also be larger.
- FIG. 8 shows a further alternative embodiment, wherein the second coupling part 4 8 according to the embodiment according to FIG. 7 is constructed.
- the blocking clutch according to FIG. 8 has a ferromagnetic housing 2 8 .
- the circular magnetic flux is in this case axially beyond the bottom 12, an axially zoom reaching to the bottom 12 of cylindrical certain sections of the sun gear 16 8, planet gears 17, the ring gear 15 8 and the zylin ⁇ derförmigen wall section 9 8 of the housing 2 made.
- the first coupling part 3 8 together with the flange 19 8 and the support disk 20 8 are made of non-magnetic material.
- Figure 9 shows a further embodiment of the lock-up clutch, which corresponds in terms of their operation to the preceding locking clutches.
- the solenoid 25g is disposed radially outside of the gear assembly 14g and held in a support member 43.
- the carrier element is mounted in an annular space 13 9 between the housing 2 and the ring gear 15 9 on the inside of the housing 2.
- the gearing arrangement is the manner of a Planetenge- drive 14 is designed and comprises a ring gear 15 9, a sun gear 16 9 as well as two groups of axially adjacently disposed planetary gears 17 9 17 9 ', which with the ring gear 15 g on the one hand and with the sun gear 16 9 on the other hand comb.
- the planet wheels - as shown in particular in Figure 9b) - 2Q
- the number of planet gears 17g, 17g 1 is arbitrary and depends on the height of the torque to be transmitted.
- the ring gear 15 g is firmly connected to the first coupling part 3 g and rotatably supported in the housing 2 on the one hand and on the output shaft 44 on the other hand by means of rolling bearings 7, 45.
- the ring gear 15 9 is designed such that a closed chamber 18 9 is formed, in which the sun gear 16 g is rotatably arranged.
- the chamber 18 g is partially filled with magnetorheological fluid, wherein between a cranked shoulder of the ring gear 15 g and a hub 46 of the second coupling part 4 g a sealing ring 22 is provided which prevents the escape of the magnetorheological fluid from the chamber 18g.
- a gas volume is contained in the chamber 18g, the compressibility of which produces the volume compensation.
- the two groups of planetary gears 17g, 17g ' are arranged axially spaced from each other, wherein insulating means 47 are provided in each case between two planet wheels lying in a cutting plane.
- the insulating means 47 hold the planetary gears 17g, 17g 1 in position and cause a - viewed in cross section - circular magnetic flux around the magnetic coil 25 g around which of the support member 43 via a first ferromagnetic portion 48 of the ring gear 15 9 , the first group of Planet gears 17g, the sun gear 16 9 , the second group of planet gears 17 g ⁇ a second ferromagnetic portion 48 'of the ring gear 15 9 back to Shin ⁇ element 43 extends.
- the magnetic flux is represented by the annular lines in Figure 9c).
- FIG. 10 shows a four-wheel drive motor vehicle 80 whose motor 81 is connected to the driven front wheels 85 via a manual transmission 82 and a transfer case (angle drive) with front axle differential 83 and front drive shafts 84.
- a longitudinal shaft 86 the drive to the rear axle of the Ver ⁇ divergent gear (angle drive) is branched off with front differential 83.
- a locking clutch 1 according to the invention is interposed, the torque via the rear differential gear 88 and the drive shafts 89 on the Rear wheels 90 can transmit.
- the lock-up clutch serves for coupling or uncoupling the rear axle driven by the differential gear.
- the lock-up clutch 1 is controlled as needed via a vehicle dynamics controller.
- the torque to be transmitted can be set as desired by the corresponding strength of the magnetic field, ie by appropriate selection of the current or voltage.
- FIG. 11 shows a motor vehicle 80 similar to that shown in FIG. 10, to the description of which reference is made.
- the inventive blocking clutch 1 in the present case is followed by a viscous coupling 87, for example, as shown in DE 198 10 940 A1.
- the viscous coupling serves to be ⁇ hintician drive the rear wheels 90 via the rear differential gear 88 and the drive shafts 89.
- a difference in rotational speed between the front and the rear axle of the viscous coupling is automatically transferred to a state in which the torque between the Axes transfers.
- the lock-up clutch 1 is closed, so that a torque is transmitted to the rear axle.
- the viscous coupling 87 in case of need by means of Sperrkupp ⁇ ment 1 disconnected from the drive train.
- the lock-up clutch 1 acts as a disconnect clutch when engaging in the driving dynamics of the motor vehicle, for example when an anti-lock braking system or an electronic stability program is engaged.
- FIG. 12 shows a locking differential according to the invention with a housing 52 and an input part 53 rotatably arranged therefor, as well as a first output part 54 and a second output part 61 connected thereto, wherein the two output parts 54, 61 have an equalizing effect.
- the locking differential is designed in the form of a planetary differential and comprises a non-rotatably connected to the input part 53 ring gear 65, a fixed to the first output part 54 fixed sun gear 66 and several with the ring gear 65th 2
- the planetary gears 67 are rotatably supported on a web assembly 58 which is fixedly connected to the second output part 61.
- the input part 53 has first connection means 55 for introducing a torque into the locking differential, for example from an output shaft of a transmission.
- the first output part 54 has second connection means 56, which are designed in the form of a L Lucassver ⁇ toothing and for non-rotatable insertion of a connecting shaft, not shown here, for example, for driving a first axis, are used.
- the second output part 61 likewise has a longitudinal toothing for connecting a connection shaft, not shown here, which drives, for example, a second axis.
- the input part 53 and the two output parts 54, 61 are each rotatably mounted in the housing 52 on a common axis of rotation. For this purpose, a rolling bearing 57 is provided between the input part 53 and the housing 52.
- the first output part 54 is slidably mounted relative to the housing 52.
- the second output part 61 is rotatably mounted coaxially within the first output part 54 by means of a Nadella ⁇ gers 60.
- the housing 52 has a substantially pot-shaped design and has a cylindrical cylindrical wall section 59 and a flange-shaped bottom 62.
- An annular space 63 is formed between the wall section 59 and a cranked projection on the bottom 62, in which a magnet coil 75 is arranged.
- the planetary differential 64 is arranged, wherein between the ring gear 65 and the sun gear 76 and web arrangement 58, a sealed chamber 68 is formed. This is limited in the axial direction on the one hand by the input part 53 and on the other hand by a einitzende in the ring gear 65 support plate 70.
- the support plate 70 carries a sealing ring 72, which seals the annular gap to the sun gear 66.
- a further sealing ring 71 is provided, which seals the chamber 68 to the outside.
- the chamber 68 is at least largely filled with a magnetorheological fluid, which can be magnetized by the magnetic coil 75 arranged in the housing 52.
- the operation of the locking differential corresponds to that of a conventional differential gear.
- the input part 53 and the two output parts 54, 61 rotate together at the same rotational speed about the rotational axis A. If different rotational speeds occur between the first output part 54 and the second output part 61, for example due to changing driving conditions between the front and The rear axle of the motor vehicle, there is ei ⁇ ner speed difference between the sun gear 66 and the web assembly 58.
- a reservoir 74 is provided to compensate for the resulting increase in volume of the magnetorheological fluid. This is located in a tubular section of the second output part 61, in which a piston 76 is seated in an axially displaceable manner. The piston 76 is acted upon axially by spring means 77, which in turn are axially supported relative to a firmly seated in the pipe section lid 79.
- the magnetic coil 75 is turned on, so that the resulting magnetic field puts the magnetorheological fluid in a highly viscous or a plastic state.
- the planet gears 67 are prevented from rolling freely relative to the ring gear 65 and the sun gear 66, respectively, so that torque is transmitted from the ring gear 65 to the sun gear 66 and the bridge assembly 58.
- the strength of the magnetic field generated and thus the viscosity of the magnetorheological fluid can be adjusted precisely so that the blocking effect of the locking differential can be precisely metered.
- the ring gear 65, the sun gear 66 and the planet gears 67 and the bottom 62 of the housing 52 made of ferromagnetic material.
- Non-austenitic steels are suitable for this purpose.
- the support disk 70 arranged between the web arrangement 58 and the magnet coil 75 is preferably made of a non-magnetic material, for which austenitic steels or aluminum are preferably used. to be eligible.
- the configuration of magnet coils, chamber and planetary gear is coordinated so that upon excitation of the magnetic coil a lichg lichst uniform magnetic field in the region of the chamber is generated, so that a uniform viscosity of the liquid can be adjusted.
- FIG. 12b shows a cross section through the locking differential.
- the ring gear 65 the sun gear 66, the two wheels meshing with planetary gears 67 and the web assembly 58 which is integrally connected to the second output member 61 can be seen.
- eight planet gears are regularly distributed over the circumference, the number of which can be varied depending on the torque to be transmitted.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112004002908T DE112004002908B4 (de) | 2004-09-25 | 2004-09-25 | Sperranordnung mit Verstellung durch magnetorheologisches Fluid |
PCT/EP2004/010787 WO2006032295A1 (de) | 2004-09-25 | 2004-09-25 | Sperranordnung mit verstellung durch magnetorheologisches fluid |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2004/010787 WO2006032295A1 (de) | 2004-09-25 | 2004-09-25 | Sperranordnung mit verstellung durch magnetorheologisches fluid |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006032295A1 true WO2006032295A1 (de) | 2006-03-30 |
Family
ID=34958876
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/010787 WO2006032295A1 (de) | 2004-09-25 | 2004-09-25 | Sperranordnung mit verstellung durch magnetorheologisches fluid |
Country Status (2)
Country | Link |
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DE (1) | DE112004002908B4 (de) |
WO (1) | WO2006032295A1 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005021945B3 (de) * | 2005-05-12 | 2007-02-01 | Gkn Driveline International Gmbh | Hydrostatische Sperrkupplung |
DE102005052386B3 (de) * | 2005-10-31 | 2007-07-12 | Gkn Driveline International Gmbh | Hydrostatische Sperrkupplung in Planetenbauweise |
WO2008071241A1 (de) * | 2006-08-14 | 2008-06-19 | Magna Powertrain Ag & Co Kg | Bauteil mit haltefunktion, aufhaltesystem und verfahren zu deren betrieb |
DE102008059979A1 (de) * | 2008-12-02 | 2010-06-10 | Magna Powertrain Ag & Co Kg | Sperrbare Differentialgetriebeeinheit |
US8292774B2 (en) | 2009-11-11 | 2012-10-23 | Honda Motor Company, Ltd. | Differential lock assembly including coupler |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102019215116B3 (de) * | 2019-10-01 | 2020-10-15 | MAGNA Metalforming GmbH | Festkörperbremse |
DE102019135760A1 (de) | 2019-12-18 | 2021-06-24 | Inventus Engineering Gmbh | Magnetorheologische Bremseinrichtung |
DE102022115766A1 (de) | 2022-06-24 | 2024-01-04 | Signata GmbH | Anordnung mit einem schaltbaren Planetengetriebe |
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DE3815225C2 (de) | 1988-05-05 | 1990-07-26 | Uni-Cardan Ag, 5200 Siegburg, De | |
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DE3815225C2 (de) | 1988-05-05 | 1990-07-26 | Uni-Cardan Ag, 5200 Siegburg, De | |
EP0446863B1 (de) | 1990-03-12 | 1996-06-05 | Fuji Photo Film Co., Ltd. | Farbphotographisches Silberhalogenidmaterial |
DE19810940A1 (de) | 1998-03-13 | 1999-09-30 | Gkn Viscodrive Gmbh | Kupplungsvorrichtung zur Übertragung von Drehmoment |
DE19847405C1 (de) | 1998-10-14 | 2000-07-20 | Gkn Viscodrive Gmbh | Schaltkupplung |
EP1154172A2 (de) * | 2000-05-12 | 2001-11-14 | Auburn Gear, Inc. | Schlupfbegrenztes Differential mit einer magnetorheologischen Flüssigkeitsbremse |
US6585616B1 (en) | 2000-11-06 | 2003-07-01 | Honda Giken Kogyo Kabushiki Kaisha | Magneto-rheological variable limited slip differential |
WO2004070224A1 (de) * | 2003-02-03 | 2004-08-19 | Gkn Driveline International Gmbh | Aktuator, insbesondere für eine reibungskupplung mit verstellung durch magneto-rheologisches fluid |
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DE102005021945B3 (de) * | 2005-05-12 | 2007-02-01 | Gkn Driveline International Gmbh | Hydrostatische Sperrkupplung |
DE102005052386B3 (de) * | 2005-10-31 | 2007-07-12 | Gkn Driveline International Gmbh | Hydrostatische Sperrkupplung in Planetenbauweise |
WO2008071241A1 (de) * | 2006-08-14 | 2008-06-19 | Magna Powertrain Ag & Co Kg | Bauteil mit haltefunktion, aufhaltesystem und verfahren zu deren betrieb |
JP2010500224A (ja) * | 2006-08-14 | 2010-01-07 | マグナ パワートレイン アクツィエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | 保持機能を有するコンポーネントアセンブリ及び開放保持システム並びにそれらの動作方法 |
DE102008059979A1 (de) * | 2008-12-02 | 2010-06-10 | Magna Powertrain Ag & Co Kg | Sperrbare Differentialgetriebeeinheit |
US8292774B2 (en) | 2009-11-11 | 2012-10-23 | Honda Motor Company, Ltd. | Differential lock assembly including coupler |
Also Published As
Publication number | Publication date |
---|---|
DE112004002908B4 (de) | 2010-06-02 |
DE112004002908A5 (de) | 2007-08-30 |
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