• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:

    公开号:SE533945C2
    申请号:SE0801851
    申请日:2008-08-28
    公开日:2011-03-08
    发明作者:Achim Domhan；Juergen Hoersch；Wolfgang Runge；Arthur Rupp
    申请人:Zf Lenksysteme Gmbh；
    IPC主号:
    专利说明:

    533 945 The invention is the basis for the task of creating an overlay control, which is reliable and which can be mounted quickly and installed flvisibly and quickly in a vehicle.
    The task is solved with an overlay control ring with the frame marks for claim 1.
    By means of a cover for the harmonic drive gearbox and / or a cover for the servomotor of the overlay control, they are designed so that they can be fitted with a vehicle body, and that at least when selecting the direction of the second drive input shaft and the first drive input shaft, or the steering shaft in the axialoni council on the servomotor and the harmonic drive gear, take into account that these can, so to speak, take over a centering function separately and feed on components mounted on these shafts, in that the ratio between the smallest inner diameter of the second drive shaft and the outer diameter of the steering shaft is selected so that this is 1 to 2, ßre- preferably close to 1, an overlay control is created, which can be installed easily and quickly in a vehicle body and whose all components to its harmonio-drive gear, for example, can be mounted quickly and self-centering on the floating pre-assembled present first and second drive input shafts.
    Preferred statements are set out in the subclaims.
    The inventive superimposed control preferably has a relationship between the outer diameter of an electric stator to the servomotor in the axial rotor on the servomotor and the outer diameter of the gear output shaft in the axial region of the harmonic drive gear, which is at least 0.5 and 2 through the axial region of the servomotor. of this size ratio, advantageous package conditions are created.
    Mass inertia torque for servomotors adapted to the mass inertia torques for the rotating parts in the harmonic drive gear is obtained from the choice of the ratios between the inner diameter of a rotor to an electric servomotor and the outer diameter of the rotor, which is 0.3 to 0.9. If the rotor is mounted directly on the second drive input shaft designed as a pipe shaft, such adapted mass inertia moments are obtained at a ratio between the outer diameter of the rotor and the outer diameter of the second drive shaft from 1.1 to 3. An outside of the servomotor and harmonic drive shaft the gear unit which is designed with a contour without major protrusions ßs, and thus good package conditions, if the ratio between the active length of the rotor and the length of a diaphragm to a radially fl visible unwinding sleeve of the harmonic drive gear is suitably selected from 0, 5 to 1.5.
    The invention-like overlay control may preferably have a locking device.
    For this purpose, the second drive input shaft has a shoulder or is rotatably connected to an inner ring of the locking device, the inner ring carrying one or more preferably radially extending projections, which by interposing a noise-absorbing element with elastomeric risk properties engage one or fl your sockets on an outer ring that radially encloses the meaning. At its radial circumference, the outer ring preferably has pocket-like depressions with one or more projections, which serve as abutments for a locking element of the locking device. With the aid of the locking element, the second drive input shaft and thus the rotor of the servomotor can be fixedly locked to the body-fixed housing to the harmonic drive gearbox or to the servomotor IOm.
    In order to adapt the mass inertia moments of the rotating parts of the locking device to the mass inertia moments of the harmonic drive gear and those of the servomotor, it may be appropriate to select the ratio between the outer diameter of the rotor and preferably the largest outer diameter of the outer ring of the locking device from 0.5 to 1.5.
    It has surprisingly been found that when choosing the ratios between the largest outer diameter of the outer ring of the locking device and the smallest diameter of the inner ring from 1.1 to 3, these ratios for the moments of mass inertia are supported, especially if the outer ring and inner ring are dimensioned the ratio between the largest outer diurnal element on the inner ring and the largest outer diurnal element on the outer ring is 0.3 to 1.0.
    Particularly advantageous conditions for the mass inertia moments and particularly advantageous mounting conditions of locking device to servomotor are obtained if the ratio between the largest outer diameter of the outer ring and the outer diameter of the rotor is approximately 0.5 to 1.5. This also supports the choice of the ratio of the largest outer diameter of the outer ring to the outer diameter of the servomotor stator from 0.2 to 1.2.
    Advantageous installation and package conditions of the overlay control are obtained by equal or approximately equal outer dimensions or outer diameters on the cover of the hannonic drive gear and the servomotor. The diurnal diameter of the gear output shaft can be selected as large or approximately equal to the outer diameter of the stator of the servomotor. It may be appropriate to choose the ratio between 0.5 to 1.5. In an especially preferred embodiment of the overlay control for package reasons, the servomotor is approximately as long or exactly as long as the harmonic drive gear. It may also be appropriate to select the ratio between the length of the servomotor and the length of the harmonic drive gear between 0.5 and 1.5.
    The invention will now be described in more detail with the aid of an exemplary embodiment and is reproduced with the aid of the accompanying drawing. In the drawing: Figure 1 shows a longitudinal section through an electric overlay control according to the invention, Figure 2 a cross section along the line II-III in Figure 1. In Figure 1, an overlay control 1 for a passenger car designed as an active steering is shown in a longitudinal section. It consists of a servomotor 9 designed as an electric tube shaft motor, which rests on a body-fixed component through a pivot bearing 26 on its housing 25. A guide shaft 7, which is rotatably connected to a knob 8, forms a first drive input shaft 2 for a superposition guide I associated superimposed gear 5. The superimposed gear 5 is designed as a harmonic drive gear 4 and its housing 24 is screwed together with the housing 25 of the servomotor 9.
    The harmonic drive gear 4 serves for superimposing a steering angle introduced on the first drive input shaft 2, with a rotational angle introduced from the servomotor 9 on a second drive input shaft 3, which is arranged coaxially around the first drive input shaft 2. Magnets for a rotor 11 are attached to the second drive input shaft 3.
    The ratio of the inner diameter drw; on the second drive input shaft 3 and the outer diameter dAwl on the first drive input shaft 2 or the control shaft 7 is selected close to the axial range A on the servomotor 9 and the harmonic drive gear 4, so that the two drive input shafts 2, 3 are centered, and that all rotating and non-rotating parts, in particular the harmonic drive gear 4, can be mounted to and on them in a floating device, and can then be statically and dynamically centered before the harmonic drive gear cover and the servomotor cover are finally screwed together.
    To break a sound path from the first to the second drive input shaft 3, the first drive input shaft 2 and the second drive input shaft 3 are mounted in roller bearings 27 in the housing 25 of the servomotor 9.
    The second drive input shaft 3 is formed in one piece with an eccentric drive core 28. Around the elliptical circumference of the eccentric drive core 28 an excitable ball bearing 29 is arranged. The eccentric drive core 28, with its axial extent, engages in a piece formed of elastic steel sheet, spherical, integrally formed with a diaphragm 12, and radially visible roll-off sleeve 13. The radially visible roll-out sleeve 13 engages under the action of the elliptical through the eccentric drive core 28 with an outer tooth on its diaphragm 12 into a per se known in an inner tooth on a rotationally fixed support ring 30 connected to a gear output shaft 6 to the superimposed gear 5. each other. The inner toothed support ring 30 has a larger number of teeth (for example two more teeth) is the radially flexible unrolling sleeve 13, whereby a rotation follows of the support ring 30 and thus the gear output shaft 6 relative to the first drive input shaft 2 with the difference of the number of teeth per rotation of the eccentric drive core 28. The first drive input shaft 2 and the radially visible unrolling sleeve 13 are rotatably connected. 10 15 20 25 30 533 945 In order to prevent the second drive input shaft 3 from rotating with the rotor 11 in the event of a fault or in the event of a failure of the servomotor 9, thus making it impossible to transmit a rotation angle of the first drive input shaft 2 and the steering wheel 8 through the radially fl visible unrolling sleeve 13 to the support ring 30 and the gear exit shaft 6, and that the vehicle can not be steered, is an electromechanical locking device 14, as shown in fi gur 1 and fi gur 2, provided for form-locking attachment of the other drive input shaft 3 on the body-fixed housing 24 of the harmonic drive gear 4.
    The locking device 14 is formed by an inner ring 15, which is fixed to the second drive shaft 3 by means of a toothed shaft connection, an outer ring 19, which surrounds the inner ring 15 radially, and a damping element 17 with elastomeric properties arranged therebetween. The ring 15 has, as shown in Fig. 2, three pin-shaped projections 16 'and three hump-shaped projections 16 arranged alternately with a 120 ° displacement relative to each other, which engage in a total of six outlets 18. The damping element 17 with elastomeric properties serves for oscillation disengagement and to create It has the possibility of rotating the inner ring 15 relative to the outer ring 19. It surrounds all tangential contact surfaces on the projections 16, 16 'against the outer ring 19. projections 21 are each provided, which serve as abutment 22 for an axially movably mounted locking element 23.
    The locking element 23 is held in an elastic guide 31 for oscillation disengagement from the housing 24. It has been found that particularly advantageous spatial conditions arise for the mounting of the overlay guide 1, if the ratio between the outer diameter dAS on the stator 10 to the servomotor 9 and the outer diaphragm outlet dnws in the axial region As on servomotor 9 is 0.5 to 2.
    In order to adjust the mass inertia moments for rotating parts in the servomotor 9, the harmonic drive gear 4 and the locking device 14, it is convenient to select the ratio between the inner diameter dm of the rotor 11 to the servomotor 9 and its outer diameters dAR between 0.3 and 0. , 9. In the exemplary embodiment shown in Figure 1, this is 0.6. Also for the same reason, it is suitable to choose the ratio between the outer diameter dm of the rotor 11 and the outer diameter dAwg of the second drive input shaft 3 from 1.1 to 3. In the embodiment shown in Figure 1, this ratio is 1.7.
    Favorable installation conditions in the overlay control 1 arise if the ratio between the active length LR on the rotor 11 and the length LM on the diaphragm 12 on the radially visible unwinding sleeve 13 of the harmonic drive gear 4 is 0.5 to 1.5. In the desiccation example shown in Figure 1, this ratio is 0.77. The mounting ear ratios for the overlay guide 1 and a good damping moment at power fl reversal of fate are preferably also achieved by selecting the ratio between the outer diurnal dm on the rotor 11 and the largest outer diurnal dM on the outer ring 19 to the locking device 14 between 0.5 and 1.5. In the exudation excerpt shown in Figure 1, this is 0.97. A selected size relationship between the largest outer diameter dM on the outer ring 19 of the locking device 14 and the smallest diameter du on the inner ring 15 from 1.1 to 3, further supports these desired properties of the overlay guide 1, as well as the relationship between the largest outer diameter dAA on the inner ring 15 and the largest outer diarnetem dM on the outer ring 19 in the range between 0.3 and 1.5.
    The two latter size disturbances are 1.8 and 1.34, respectively, in the drying example in Figure 1.
    In order to be able to easily slide the rotating parts of the servomotor 9 and the locking device 14 on the drive input shafts 2, 3, it is convenient to select the largest outer diameter dM of the outer ring 19 of the locking device 14 approximately equal to the outer diameter du; on the rotor 11. It is convenient to select the ratio between the largest outer diameter dM on the outer ring 19 and the outer diameter dAs on the stator 10 from 0.2 to 1.2. In the embodiment shown, it is 0.62.
    In addition, it is convenient to select the ratio between the largest outer diameter dAwg on the drive output shaft 6 and the outer diameter dAg on the stator 10 to the servomotor 9 fi from 0.5 to 1.5.
    In particular, the covers 24 and 25 of the harmonic drive gear 4 and the servomotor 9, respectively, are selected with an identical or approximately identical outer diameter dAw and dm ßr to obtain an outer contour on the overlay control 1 which is as fi in fi- as ledges as possible. The lengths LS, Lw on the covers 25 and 24 are also chosen to be the same or approximately the same.
    权利要求:
    Claims (14)
    [1]
    Overhead control for a vehicle, in particular for a servo or auxiliary power steering to a motor vehicle, having a first override gear (5), having a first drive shaft (2) and a second, coaxial drive input shaft (3), and designed as hannonic drive gear (4), for superimposing the angles of rotation of the two drive input shafts (2, 3) on a gear output shaft (6) to the superimposed gear (5), the first drive input shaft (2) being a control shaft (7), which is actively connected to a steering wheel (8), and the second drive input shaft (3) is actively connected to a servomotor (9), characterized in that a housing (24) for the harmonic drive gear (4) and / or a housing (25) to the servomotor (9) is arranged body body in the vehicle and that the ratio between the smallest inner diameter (d1w;) on the second drive shaft (3) and the largest outer diameter (dAwl) on the first drive shaft (2) over the length (LS) on the servomotor (9) and / or over the length (Lw) On the harmonic drive gear (4 ) is 1 to 2.
    [2]
    Overlay control according to claim 1, characterized! that the ratio between the outer diameter (ds) of a stator (10) in the axial region (AS) of the servomotor (9) and the outer diameter (dAwg) of the gear output shaft (6) over the length (Lw) of the harmonic drive gear (4) is 0 , 5 to 2.
    [3]
    Overlay control according to one of Claims 1 or 2, characterized in that the ratio between the inner diameter (dm) of a rotor (11) to the servomotor (9) and the outer diameter (dAR) of the rotor (11) is 0.3 to 0.9.
    [4]
    Overlay control according to one of Claims 1 to 3, characterized in that the ratio between the outer diameter (dm) of the rotor (11) and the outer diameter (dAW2) of the second drive input shaft (3) is 1.1 to 3.
    [5]
    Overlay control according to one of Claims 1 to 4, characterized in! in that the ratio between the active length (LR) of the rotor (1 l) and the length of a diaphragm (12) on a radially flexible unwinding sleeve (13) to the harmonic drive gear (4) is 0.5 to 1.5. 533 945 8
    [6]
    Overlay guide according to one of Claims 1 to 5, characterized in that the overlay guide (1) has a locking device (14), the second drive input shaft (3) having a shoulder or an inner ring (15) to which it is rotatably connected, and the inner ring (15) carries one or more radial and / or axial projections (16, 16 ') which, by inserting a noise attenuating element (17) with elastomeric properties, engage in one or two of their sockets (18), and the outer ring (19) has at its radial and / or axial circumference k-like depressions (20) with one or fl protrusions, which serve as abutments (22), a locking element (23), with which the outer ring (19) is form-loosely releasably attached to the body-fixed housing (24, 25) to the harmonic drive gear (4) or the servomotor (9).
    [7]
    Overlay control according to claim 6, characterized in that the ratio between the outer diameter (dm) of the rotor (11) and the largest outer diameter (dM) of the outer ring (19) of the locking device (14) is 0.5 to 1.5.
    [8]
    Overlay control according to claim 6 or 7, characterized in that the ratio between the largest outer diurnal element (dAA) on the outer ring (19) to the locking device (14) and the smallest diameter (du) on the inner ring (15) is 1.1 to 3.
    [9]
    Overlay control according to one of Claims 6 or 8, characterized in that the ratio between the largest outer diameter (dAI) of the inner ring (15) and the largest outer diameter (dAA) of the outer ring (19) is 0.3 to 1.
    [10]
    Overlay control according to one of Claims 6 to 9, characterized in that the ratio between the largest outer diameter (dAA) of the outer ring (19) of the locking device (14) and the outer diameter (dAR) of the rotor (11) is 1.
    [11]
    Overlay control according to one of Claims 6 to 10, characterized in that the ratio between the largest outer diameter (dan) of the outer ring (19) and the outer diameter (dAs) of the stator (10) to the servomotor (9) is between 0.2 and 1, 2.
    [12]
    Overlay control according to one of Claims 1 to 11, characterized in that the ratio between the outer diameter (dAG) of the housing (25) of the servomotor (9) and the outer diameter (dAw) of the housing (26) of the harmonic drive gear (4) is 0.5 to 1.5. 533 945
    [13]
    Overlay control according to one of Claims 1 to 12, characterized in: in that the ratio between the largest outer diameter (d ^ w_ ~,) on the gear output shaft (6) and the outer diameter (dAs) on the stator (10) to the servomotor (9) is 0.5 to 1.5.
    [14]
    Overlay control according to one of Claims 1 to 13, characterized in that the ratio between the length (LS) of the servomotor (9) and the length (LW) of the harmonic drive gear (4) is 0.5 to 1.5.
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    同族专利:
    公开号 | 公开日
    DE102007000937A1|2009-03-05|
    DE102007000937B4|2022-03-03|
    SE0801851L|2009-03-05|
    KR20090024628A|2009-03-09|
    FR2920391A1|2009-03-06|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE10159800A1|2001-05-23|2002-12-12|Continental Teves Ag & Co Ohg|Overlay transmission for overlay steering can overlay rotary motion input from driver by means of rotary transmission with at least two stages|
    JP3758649B2|2002-07-30|2006-03-22|トヨタ自動車株式会社|Vehicle steering device|
    US6938724B2|2003-03-18|2005-09-06|Toyoda Koki Kabushiki Kaisha|Motor vehicle steering device|
    DE102005022409A1|2005-05-14|2006-11-30|Zf Lenksysteme Gmbh|Superposition gear|
    EP1934082B1|2005-10-06|2012-03-21|ThyssenKrupp Presta Aktiengesellschaft|Superimposed steering system comprising a mechanical return level|CN113085999A|2021-04-30|2021-07-09|浙江吉利控股集团有限公司|Vehicle control method and device and vehicle|
    法律状态:
    2014-04-01| NUG| Patent has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    DE102007000937.4A|DE102007000937B4|2007-09-04|2007-09-04|overlay steering|
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