WO2018019790A1 - Liaison inter-arbres transmettant le couple et procédé de fabrication - Google Patents

Liaison inter-arbres transmettant le couple et procédé de fabrication Download PDF

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Publication number
WO2018019790A1
WO2018019790A1 PCT/EP2017/068686 EP2017068686W WO2018019790A1 WO 2018019790 A1 WO2018019790 A1 WO 2018019790A1 EP 2017068686 W EP2017068686 W EP 2017068686W WO 2018019790 A1 WO2018019790 A1 WO 2018019790A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
drive shaft
torque transmitting
adjusting device
output shaft
Prior art date
Application number
PCT/EP2017/068686
Other languages
German (de)
English (en)
Inventor
Eckhard Kirchner
Original Assignee
Valeo Siemens Eautomotive Germany Gmbh
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 Valeo Siemens Eautomotive Germany Gmbh filed Critical Valeo Siemens Eautomotive Germany Gmbh
Priority to CN201780045028.9A priority Critical patent/CN109790871A/zh
Publication of WO2018019790A1 publication Critical patent/WO2018019790A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
    • F16C3/12—Crankshafts assembled of several parts, e.g. by welding by crimping releasably connected
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/18—Eccentric-shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0222—Lateral adjustment
    • F16H2057/0224—Lateral adjustment using eccentric bushes

Definitions

  • the invention relates to a torque transmitting Wellenver ⁇ bond and a manufacturing method for such a torque transmitting shaft connection.
  • the invention also relates to a drive train for a motor vehicle and a
  • the invention relates to a production device with a suitable program for implementing the manufacturing method according to the invention.
  • a belt tensioning device for an electric motor is known, the motor shaft is received in a recess in the motor flange.
  • the motor flange has in the region of the recess on an axial stub, which is eccentric with respect to the motor shaft.
  • the stub of the motor flange is rotatably received in a recess of an angle arm. By a rotation of the motor flange in the recess in the angle arm, the position of the motor shaft is adjustable.
  • the belt tensioning device according to DE 40 33 894 AI is also suitable for alignment of a gear which engages in a driven gear.
  • the torque-transmitting shaft connection consists of a drive shaft, via which the torque to be transmitted is delivered, and an output shaft.
  • the drive shaft and the Ab ⁇ drive shaft are each mounted rotatably mounted about its axis of rotation in a housing and are otherwise stationary with respect to the housing.
  • the transfer of torque from the actuator shaft to the output shaft is effected by a geeig ⁇ designated clutch, such as a toothing of the shafts, pulleys, belt, a shaft-hub connection, or a chain.
  • the housing, in which the drive shaft is received, is releasably connected to a first adjusting device, which serves to set an angular position of the housing about the axis of rotation of the drive axle.
  • the housing, in which the output shaft is received is detachably connected to a two ⁇ th adjusting device, which serves to set an angular position of the housing about the axis of rotation of the output shaft se.
  • Both adjustment devices are formed in wesentli ⁇ Chen ring or disc-shaped.
  • the first and second adjusting devices are connected to one another in a torsionally rigid manner. Each of the adjusting devices is configured to adjust the radial positioning of the drive shaft and the output shaft relative to each other by selecting the respective angular position.
  • Radial direction here is a direction perpendicular to one of the axes of rotation of Drive shaft or the output shaft to understand.
  • the radi ⁇ ale distance between the drive shaft and the output shaft can thus be set by choosing the relative angular position between the first and second adjusting device.
  • the housing with the drive shaft is torsionally ⁇ fixed to the housing with the output shaft rotationally rigidly verbun ⁇ .
  • a radial relative movement for adjusting the radial distance between the drive shaft and the output shaft is thereby selectively divided into two individual radial movements of the two shafts.
  • the maximum radial performed Be ⁇ movement by rotating the housing is consequently reduced.
  • the first and / or second adjusting device on an axially inner and an axially outer portion.
  • Under an axially outer section is in the first and second Adjusting device to understand each of the section which faces along the respective axis of rotation of the other adjusting device.
  • the axially inner section of the first and / or second adjusting device the portion facing away from the other adjusting device and facing the associated housing.
  • the axially innenlie ⁇ ing portion of the first adjusting device has a center point through which the axis of rotation of the drive shaft ⁇ runs.
  • the axially outer portion of the first adjusting device has a center which is radially offset from the center of the axially inner portion.
  • the outer From ⁇ section of the second adjusting device on a center point which is offset radially to the center of the axially inner portion.
  • the axis of rotation of the drive shaft or Ab ⁇ drive shaft is radially adjustable by rotation relative to each of ⁇ the shaft.
  • the position of the respective axis of rotation is variable along a 180 ° rotation so that by twice Exzent ⁇ riztician. This ensures an increased accuracy in the setting of the radi ⁇ alen distance between the drive shaft and the Abtriebswel- le while at the same ⁇ lasting achievable angular accuracy when rotating the housing.
  • particularly low-wear and low-noise torque-transmitting shaft connections can be produced when the drive shaft and the output shaft are coupled to one another via toothings.
  • the eccentricity of at least one adjusting device is 100 ym to 500 ym. Eccentricities of this size can play as examples produced by non-circular grinding reliable high pre ⁇ cision cost. Upon rotation ei ⁇ nes housing with an inventive adjustment thus a maximum gradient of 2.78 to 0.56 degrees per ym ym per degree is obtained for the movement of the respective axis of rotation. Thus, the adjustment devices offer a high
  • At least one of the housing is substantially circular or cylindrical in shape and has a
  • Diameter of 150 to 400 mm Diameter of 150 to 400 mm.
  • at least egg ⁇ nes of the housing and / or one of the adjusting devices are provided on an outer side with a scale that allows reading the angular position of the housing and / or the adjustment.
  • the higher the diameter of the housing the more clearly the scale is readable and, for example, bezüg ⁇ Lich a stationary reference line adjustable.
  • complex measuring instruments and tools can be dispensed with during assembly of the torque-transmitting shaft connection according to the invention.
  • the production of the torque-transmitting shaft connection according to the invention is accelerated.
  • the torque-transmitting shaft connection may preferably be present between the drive shaft and the output shaft in the radial direction, a transition fit.
  • the interference fit between the drive shaft and the output shaft as a fit type js5 to jslO, particularly preferably of the type js5 to js7, All forms ⁇ .
  • the torque transmission is ensured by an interlocking toothing of the drive shaft and the Ab ⁇ drive shaft in the torque transmission ⁇ ing shaft connection according to the invention.
  • the toothing is produced by hobbing, Wälzdorfen, scraping and / or grinding.
  • Such production methods offer a high degree of manufacturing precision ⁇ with which the exact relative positioning ra ⁇ Diale described above the output shaft and the output shaft can be further exploited for noise prevention in a relatively simple and economical manner.
  • a particularly high production quality can be achieved, which offers maximum noise reduction.
  • the torque-transmitting shaft connection according to the invention accelerates and can be carried out inexpensively without sacrificing quality.
  • the torque-transmitting shaft connection according to the invention can also have adjustment devices which have an eccentricity which corresponds to 0.2 times and 0.8 times, preferably 0.5 times, a desired radial desired distance between the drive shaft and the output shaft , Thereby, the radial distance set between the input shaft and the output shaft is substantially free ⁇ a divisible.
  • the exact production of the radial distance between the shafts is thus divisible to both Einsteilvorraumen, so that the achievable precision of two Ein-adjusting devices is used in a selectable degree. Consequently, the torque-transmitting shaft connection according to the invention offers increased design flexibility.
  • an end face of at least one of the adjusting devices can be provided with a curable coating.
  • the thus axially outer curable coating allows the Einsteilvortechnischen after an axial Caribbeaneben in mutual contact rotatably connected to each other.
  • the aushärt ⁇ bare coating is formed as a curable resin.
  • the curable coating can be formed as a UV-curable ⁇ material.
  • Curing by means of UV irradiation allows a non-contact fixation, so that unintentional contact of the housing and / or the adjusting devices, and thus a departure from the achieved positioning, are avoided. A complex handling of touch-sensitive component arrangements is thus avoided and the torque-transmitting inventive
  • the first and / or second Einstellvorrich- a with respect to the respective axis of rotation have an inclined end face. Between the plane of the front side and the corresponding axis of rotation is an angle that deviates from a 90 ° angle.
  • the inclined end face he ⁇ laubt it, a chen compensate between the drive shaft and the output drive shaft ⁇ present axial inclination or Achsschränkung.
  • the end faces of both adjusting devices are inclined so that there is a high potential for correction of existing axial inclinations or axial limitations.
  • the first and second adjusting device can be formed in one piece.
  • the drive shaft is designed as an electric motor shaft and / or the drive shaft from ⁇ as the input shaft of a transmission.
  • Electric motors are operated in many applications, for example in an electric traction motor in a motor vehicle, in a high speed range, so that a corresponding transmission is required.
  • the rotating ⁇ torque-transmitting shaft connection according to the invention offers a high degree of noise reduction for such appli ⁇ compounds and by the pre- alignment zie durability.
  • the underlying task is also solved by a manufacturing method, with which, inter alia, one of the torque-transmitting shaft connections described above can be produced. Consequently, the features of the manufacturing ⁇ method on the torque transmitting Wellenverbin ⁇ tion and vice versa transferable.
  • the procedural ⁇ ren according to the invention serves to produce a torque-transmitting shaft connection comprising a drive shaft and an output shaft.
  • the drive shaft serves to transmit the
  • the drive shaft ⁇ and the output shaft are formed for this purpose in a suitable form.
  • the drive shaft and the output shaft can be positioned by the method according to the invention in a desired position, which includes a desired angle and a radial nominal distance. The nominal angle is based on a stationary reference line.
  • the drive shaft and the output shaft are stationary both each rotatably mounted in a housing positioned ⁇ taken in and with respect to the axial or radial direction of the respective housing.
  • the housing with the drive shaft and the drive shaft ⁇ are provided in a starting position.
  • In ei ⁇ nem process step is a Einstellwinkelsumme determined on the basis of the radial desired distance between the Antriebswel ⁇ le and the output shaft.
  • determining the Einstellwinkelsumme also the eccentricities of a first and a second adjustment device are taken into account.
  • the first adjusting device is associated with the housing with the drive shaft and the second adjusting device is associated with the housing with the output shaft.
  • the determination of the Einstellwinkelsumme utilizing a geo ⁇ metric relationship between the said measurements.
  • the determination of the setting angle sum takes place by means of a mathematical conversion of the geometric relationship.
  • the geometric relationship is a triangular shape resulting from the eccentricities and the radial nominal distance. One of the triangle sides forms the radial nominal distance, which is inclined by the nominal angle.
  • a division behaves ⁇ nis is chosen for the desired radial distance.
  • Based on the selected TEI is transmitted division ratio of the radial distance to the target setting ⁇ sum of angles in a further process step.
  • the transfer takes place under Chamfering ⁇ wetting of the geometric relationship between the eccentricities of the shafts and the desired radial distance.
  • the Studentstra ⁇ gen can be done as the determination of Einstellwinkelsumme also with- means of a computational implementation of the geometric context. Thereby, a first pitch angle is determined, and for the housing with the output shaft, a second setting angle of the housing with the at ⁇ drive shaft.
  • Be ⁇ a fixed reference line the housing at the corresponding setting angle to be rotated and thus achieves the desired Positionin ⁇ tion for at ⁇ drive shaft and the output shaft. Further, between the adjusting devices a non-rotatable connection, for example by screws, made and thus fixed the achieved positioning.
  • the method according to the invention requires a minimum of process steps and is therefore quick and easy to carry out. At the same time it offers a high degree of accuracy in the positioning of the drive shaft and the Abtriebswel ⁇ le. Due to the selectability of the division ratio of the radi ⁇ alen setpoint distance, the claimed method on different constructions and applications can be adapted.
  • the inventive method also allows sepa ⁇ rate readjustment if necessary. In this way, the rejection rate is reduced in quality control and production IMP EXP ⁇ together more efficiently.
  • the method steps may be performed by a manufacturing ⁇ plant, for example from a manufacturing robot is controlled by an appropriate program, both manual and automated.
  • the division ratio is selected such that the first and second setting angles are the same. This results in a maximum relative Wegig ⁇ ness is achieved in the adjustment of the radial distance between the drive shaft and the output shaft for each of the setting angle. Consequently, the technical advantages ⁇ parts of the torque-transmitting shaft connection according to the invention achieved to a particularly high degree by two equal adjustment angle.
  • the first and / or second adjustment device may be coated with a curable coating.
  • the curable coating is preferably on an end face of the Adjustment arranged, which faces the respective other adjusting device.
  • the curable coating makes it possible to fix the achieved desired positioning of the at ⁇ drive shaft and the output shaft without an additional tool contact. Unintentional deviations from the set positioning are thus avoided.
  • the curable coating is formed as a UV-curable coating. A curing accelerated by UV irradiation allows contactless mutual rotationally fixed fixing of the adjusting devices.
  • the underlying task is also solved by a drive train for a motor vehicle having a drive shaft ⁇ and an output shaft.
  • the drive shaft and the output shaft according to the invention are interconnected by torque over ⁇ bearing shaft connection according to one of the embodiments described above.
  • a motor vehicle that having an electric traction motor, which is adapted to-least temporarily to the motor vehicle at the required ⁇ drive power to provide at least in part made available.
  • a vehicle may be, for example, a hybrid vehicle or an electric vehicle ⁇ .
  • the electric driving ⁇ engine is equipped according to the invention with a drive train according to the above sketched representation.
  • a motor vehicle with an electric traction motor in particular takes the scored by the inventive torque transmitting camshaft ⁇ bond noise reduction due to the at least temporarily missing combustion engine noise produced advantageously. It is thus the ride comfort of a motor vehicle with electric traction motor increased.
  • the task is also solved by a program that is stored on a control unit of a manufacturing facility, such as a manufacturing robot, and executable.
  • the program is designed to control the mechanical processes of the production device via control signals and to implement at least one of the above outlined manufacturing ⁇ method.
  • the program thus allows the production of a torque-transmitting shaft connection according to the invention.
  • the object underlying Stel ⁇ lung is achieved by a production device, such as a manufacturing robot, which has at least a partially automated implementation ⁇ example of the production method according to the invention is formed.
  • Theiquesseinrich ⁇ tung has for this purpose a control unit on which the dung OF INVENTION ⁇ proper program is stored in an executable form.
  • the production of the torque-transmitting shaft connection according to the invention is generally automated and thus economic ⁇ Lich feasible with very high precision and speed.
  • FIG. 1 shows a side view of an embodiment of the torque-transmitting shaft connection according to the invention
  • the torque transmitting shaft connection 10 comprises a drive shaft 12, which cooperates with the output shaft 14 for torque transmission. The torque transmission between the drive shaft 12 and the output shaft
  • the drive shaft 12 is rotatably supported about its axis of rotation 13 in a housing 22. Due to the bearing, not shown, the drive shaft 12 with respect to its housing 22 in the radial direction 16, 17 and axial direction 19, 20 immovable.
  • the output shaft 14 is rotatably mounted in a separate housing 24 about its axis of rotation 15.
  • the housings 22, 24 are, as seen along the axial direction 18, 19, coupled to their end faces in each case with Einsteilvorraumen 32, 34.
  • the Einsteilvortechnischen 32, 34 are interconnected at their axially outer end surfaces 26, 28 to each other about the respective axes of rotation 13, 15 rotatably connected to each other.
  • the first and second adjusting devices 32, 34 are each essentially disk-shaped or cylindrical-shaped.
  • the Einsteilvoriquesen 32, 34 each have an axially inner portion 36 which is rotatably connected to the respective housing 22, 24.
  • the axially inward ⁇ ing direction is shown in FIG. 1 for each housing 22, 24 through an arrow with the reference numeral 18 shown.
  • the center of the radially inner sections 36 lies on the respective axis of rotation 13, 15 of the drive shaft 12 and the output shaft 14.
  • the axially inner portions 36 are thus substantially coaxial with adjacent housing 22, 24 are arranged. At the axially inner portions 36 each adjacent to a radially outer portion 37.
  • the axially outer portions 37 of the adjusting devices 32, 34 each have a center point which au ⁇ ßerrenz the axis of rotation 13, 15 of the associated housing 22, is 24th
  • the axially outer sections 37 abut one another directly on their end faces 26, 28.
  • the centers of the axially outer sections 37 form a ge ⁇ common center axis 25, which are parallel between the axes of rotation 13, 15 of the drive shaft 12 and the output shaft 14.
  • the center points of the axially outer sections 37 are facing the axis of rotation 13, 15 of the associated Antriebsl. Output shaft 12, 14 an eccentricity 42, 44, which in FIG. 1 are shown as radial distances.
  • the housings 22, 24 have housing diameter 27 which are considerably larger than the eccentricities 42, 44.
  • the Einstellvorrichtun- gen 32, 34 further have at their end faces 26, 28 a curable coating 39, through which a rotating ⁇ fixed connection between the adjusting devices 32, 34 is ensured.
  • 2 shows a top view and a sectional view of an adjusting device 32, 34 which can be used in a torque-transmitting shaft connection 10 according to the invention.
  • the adjusting device 32, 34 is essentially a round Disc and in the sectional view cylindrical.
  • the Axialrich ⁇ lines and the radial directions are indicated in FIG 2 analogous to FIG 1 with the arrows 16, 17, 18, 19.
  • the Einsteilvor ⁇ direction 32, 34 has an axially inner portion 36 adjacent to an axially outer portion 37.
  • the axially inner portion 36 has a diameter which corresponds to a housing diameter 27 of a housing 22, not shown in detail.
  • the center 33 of the axially inner portion 36 is located on the axis of rotation 13, 15, around which the associated drive shaft 12 or output shaft ⁇ 14 is rotatably mounted.
  • the axially outer Ab ⁇ section 37 has a center 35 which is offset eccentrically to the center 33 of the axially inner Ab ⁇ section 36.
  • the resulting eccentricity 42, 44 is shown in FIG 2 as a radial distance.
  • the ex ⁇ zentrizmaschineen have a size of 100 .mu.m to 500 .mu.m.
  • a rotation 21 of the adjusting device 32, 34 about the center 33 of the axially inner portion 36 of ⁇ center point 35 of the axially outer portion 37 is movable in a circular path 23 with a radius corresponding to the eccentricity 42, 44.
  • the rotation 21 takes place at an angle of a desired angle 54 of a desired position 50 and a respective adjustment angle 61, 62.
  • the target angle 43 is based on a stationary reference line 58 and is of the desired position 50 of the drive shaft 32 and the Abtriebswel ⁇ le 34th dependent, which can be achieved by the adjusting devices 32, 34.
  • the setting angle of 61, 52 result from the choice of a parameter in the assembly of navmomentübertra ⁇ constricting wave communication therewith 10.
  • the position of the central axis 25, which passes through the center 35 of the axially outer portion 36 is spatially variable.
  • a further adjustment device 32, 34 which rests on the end face 26, 28 is Thus, a radial distance between the drive shaft 12 and the output shaft 14 adjustable.
  • the end face 26, 26 is provided with a coating of a curable material 39.
  • a rotationally fixed connection between the setting devices 32, 34 can be produced by hardening the curable material.
  • the adjusting device 32, 34 consists essentially of a metallic material and is produced by non-circular grinding.
  • FIG. 3 schematically shows the determination of setting angles 61, 62, which is carried out in one embodiment of the method 100 according to the invention.
  • the method 100 starts from a desired position 50, which is to be assumed by the drive shaft 12 and the output shaft 14.
  • the drive shaft 12 and its axis of rotation 13 form the origin of a coordinate system that includes a horizontal x-axis 51 and a vertical y-axis 53 for describing the relative position of the output shaft 14 and its axis of rotation.
  • the desired position 50 comprises a target angle 54 and a ra ⁇ Dialen desired distance 52.
  • For determining the setting angle of 61, 62, 44 of the respective adjusting devices 32 is out of the radia ⁇ len desired distance 52 and the eccentricities 42, 34 formed a triangle 60th
  • the radial target distance is 52 ge ⁇ divided into a selectable dividing ratio 66th
  • the division ratio 66 is represented by the position of a division point 59 at the radial nominal distance 52.
  • the division point 59 divides the radial nominal distance 52 into a first and a second partial section 56, 57.
  • the first partial section 56 corresponds to a radial position of the drive shaft 12, which is to be adjusted by the first adjusting device 32.
  • the second section 56 corresponds to a radial position of the output shaft 14, which is to be adjusted by the second adjusting device 34.
  • a connection line from the triangular point 55 for dividing point 59 divides the Einstellwin ⁇ kelsumme 64 in two setting angles 61, 62.
  • the first A ⁇ adjustment angle 61 defining a rotation of the first housing 22 with the drive shaft 12 and the second setting angle of rotation of the second housing 24.
  • the pitch angle 61, 52 thus define the relative position of the drive shaft 12 to the output shaft 14.
  • the rotations of the housing 22 , 24 are further defined by the nominal angle 54 with respect to the fixed reference line 58.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

L'invention concerne une liaison inter-arbres (10) transmettant le couple entre un arbre d'entrée (12) et un arbre de sortie (14) respectivement logés de façon rotative dans un carter (22, 24). Le carter (22) de l'arbre d'entrée (12) est relié à un premier dispositif de réglage (32) et le carter (24) de l'arbre de sortie (14) est relié à un deuxième dispositif de réglage (34). Selon l'invention, les dispositifs de réglage (32, 34) sont respectivement conçus pour le positionnement réglable de façon radialement excentrique de l'arbre d'entrée (12) et de l'arbre de sortie (14). Par ailleurs, le premier et le deuxième dispositif de réglage (32, 34) sont fixés directement l'un à l'autre. L'invention concerne également un procédé (100) de fabrication de la liaison inter-arbres (10) transmettant le couple.
PCT/EP2017/068686 2016-07-25 2017-07-24 Liaison inter-arbres transmettant le couple et procédé de fabrication WO2018019790A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201780045028.9A CN109790871A (zh) 2016-07-25 2017-07-24 传递扭矩的轴连接装置和制造流程

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016213562.7 2016-07-25
DE102016213562.7A DE102016213562B4 (de) 2016-07-25 2016-07-25 Drehmomentübertragende Wellenverbindung und Herstellungsverfahren, sowie Antriebsstrang, Kraftfahrzeug, Programm und Fertigungseinrichtung

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Publication Number Publication Date
WO2018019790A1 true WO2018019790A1 (fr) 2018-02-01

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DE (1) DE102016213562B4 (fr)
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DE1224100B (de) * 1961-12-29 1966-09-01 Richard Schmidt Kupplung zur drehwinkelgetreuen Drehmomentuebertragung zwischen exzentrisch gegeneinander versetzten Wellen
DE4033894A1 (de) 1990-10-25 1992-04-30 Alon Tavori Riemenspanneinrichtung fuer insb. einen elektromotor
DE69301050T2 (de) * 1992-04-02 1996-05-15 Devilbiss Air Power Co Exzentrische Kurbelwelle für einen Luftverdichter mit Verdrängerkolben
WO2000057073A1 (fr) * 1999-03-24 2000-09-28 Fev Motorentechnik Gmbh Element d'accouplement pour la liaison de deux arbres a axe parallele places coaxialement l'un derriere l'autre et avec un ecart transversal l'un par rapport a l'autre

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110925321A (zh) * 2019-12-27 2020-03-27 长安大学 一种偏心距可调的偏心联轴器
CN110925321B (zh) * 2019-12-27 2023-07-14 长安大学 一种偏心距可调的偏心联轴器

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