CN1867477A - Superimposed steering system - Google Patents
Superimposed steering system Download PDFInfo
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- CN1867477A CN1867477A CN 200480029091 CN200480029091A CN1867477A CN 1867477 A CN1867477 A CN 1867477A CN 200480029091 CN200480029091 CN 200480029091 CN 200480029091 A CN200480029091 A CN 200480029091A CN 1867477 A CN1867477 A CN 1867477A
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- 230000008054 signal transmission Effects 0.000 claims description 2
- 239000010959 steel Substances 0.000 claims description 2
- 229920003023 plastic Polymers 0.000 claims 1
- 239000004033 plastic Substances 0.000 claims 1
- 238000010276 construction Methods 0.000 abstract description 2
- 241001343274 Dichrostachys spicata Species 0.000 description 6
- 238000010586 diagram Methods 0.000 description 3
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- 238000004519 manufacturing process Methods 0.000 description 3
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- 241000192783 Hakea sericea Species 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
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- 230000035807 sensation Effects 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
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Abstract
The invention relates to a superimposed steering system for a vehicle, in particular a servo-assisted or power steering system for a motor vehicle. Said system comprises a differential drive (4), which is configured as a shaft drive (11) and has a first input shaft (2) and a second input shaft (3), for superimposing the rotational angles that occur in the first and second input shafts (2,3) on an output shaft (5) of the differential drive (4). The output shaft (5) acts on an input shaft (6) of a steering gear (7). The first input shaft (2) interacts with a steering handle (9) by means of a steering shaft (8) and the second input shaft (3) interacts with a servo motor (10). The aim of the invention is to provide a superimposed steering system that can apply an additional steering angle, without play, to the output shaft (5) and that has a simple, cost-effective, space-saving construction, whilst being easy to install. To achieve this, the first input shaft (2) is directly connected in a detachable manner to a radially flexible flex-spline (13) of the shaft drive (11), said first input shaft (2) passing through an eccentric drive core (12) of the shaft drive (11), which extends into the radially flexible flex spline (13).
Description
Technical field
The present invention relates to a kind of superposition steering system that is used for vehicle as described in the preamble, the superposition steering system ( berlagerungslenkung) of or servo steering system servo especially for automobile by claim 1.
Background technology
Superposition steering system is known and its characteristics are, can passed through other corner of an actr stack by the vehicle driver on the deflection angle of selecting on the steering handwheel in case of necessity.Should control by an electron steering and/or control apparatus by additional corner, and be used to improve riding stability or other purpose of vehicle.
In order to produce additional angle or other corner, by DE 101 29 450 A1 and a kind of planetary gear mechanism of the known use of DE 101 60313 A1 as the stack transmission device, wherein, one disconnects vertically with one first transmission input shaft bonded assembly steering shaft and rotatably is connected by the classification satellite gear (Stufenplaneten) that moves to the sun wheel of spindle unit that rotates.These classification satellite gears are bearing on the planetary wheel carrier.Planetary wheel carrier can move around steering shaft and sun wheel thereof by a spiral gear mechanism or Worm and worm-wheel gearing again, and wherein rotatablely moving of planetary wheel carrier carried out on one second transmission input shaft of stack transmission device by means of screw element or worm screw.
This stack transmission device has a large amount of gears mesh.Produce the gear transmission gap thus, this can cause undesirable steering gap.In addition, the described stack transmission device that has servomotor more complicated and costliness technically.
DE 102 20 123 A1 disclose a kind of superposition steering system, wherein the integrated actuating device of a servo-electric in a steering stem shaft that steering handwheel and deflector are coupled together.The actuating device of this servo-electric have one with first section bonded assembly shell of steering stem shaft and one second section bonded assembly axle drive shaft with steering stem shaft.First section of steering stem shaft is connected with steering handwheel, and second section be connected with deflector, and be perhaps opposite.By the actuating device of servo-electric, axle drive shaft can rotate with respect to the shell of servo-electric actuating device, to produce an additional corner.Though can be to the additional angle of stack that rotatablely moves between steering handwheel and the deflector by this superposition steering system, but the opposing torque of servo-electric actuating device is bearing on the steering stem shaft, this may cause chaufeur turn to the sensation or travel and feel uncomfortable.
More known superposition steering systems, they have a harmonic wave or pulsation transmission device (Well-oder Pulsatorgetriebe) conduct stack transmission device.But the servomotor of this harmonic drive mechanism is to support its torque on Steering gear.In addition, this harmonic drive mechanism needs a fixing shell, so that torque on the steering handwheel and corner are delivered on the transmission output shaft of stack transmission device.
Summary of the invention
The purpose of this invention is to provide a kind of zero-lash, in comfortable and superposition steering system that structurally simply be used for vehicle of when operation, its structure space demand minimum.
This purpose solves by a kind of superposition steering system with feature of claim 1.
This stack transmission device can constitute does not for this purpose as follows have shell, i.e. torque on steering handwheel and the first transmission input shaft and corner directly are delivered on the Rolling bearing of radial compliance of harmonic drive mechanism by removable being connected.Pass an accentric of harmonic drive mechanism, preferred oval-shaped transmission core at this first transmission input shaft, this transmission core is permanently connected in the Rolling bearing that protrudes into radial compliance and with the second transmission input shaft and servomotor rotation with being cam-shaped in the radial direction.
Preferred embodiment draw by dependent claims.
Harmonic drive mechanism has one first transmission input shaft, and its rotation is connected with steering handwheel with the steering shaft of vehicle regularly.The second transmission input shaft constitutes hollow shaft, and it is by driven by servomotor.The rotation of the second transmission input shaft is connected with the particularly oval-shaped transmission core of the accentric of harmonic drive mechanism regularly.This eccentric drive mandrel in the Rolling bearing that is embedded into the harmonic drive mechanism radial compliance (flex-spline), wherein one or more circumferential segment of the Rolling bearing of radial compliance lateral surface change continuously with a rotation regularly with the areal of support engagement of a substantially cylindrical of transmission output shaft bonded assembly carrier ring.Therefore steering shaft is divided into first a transmission input shaft that is permanently connected with the steering handwheel rotation and one and rotates the transmission output shaft that is permanently connected with carrier ring in the axial region of the carrier ring of harmonic drive mechanism.Transmission output shaft is captiveed joint with carrier ring and can be arranged on rotationally in the frame or shell of harmonic drive mechanism.Realized the rotation of transmission output shaft in this way, thus except the deflection angle of importing on the steering handwheel, importing a positive or negative deflection angle to steering shaft by chaufeur with respect to the first transmission input shaft.
For the assembling of simplifying harmonic drive mechanism and in order to change each parts apace, the first transmission input shaft detachably is connected with the accentric Rolling bearing.It is also advantageous in that each parts of harmonic drive mechanism can be made from a variety of materials, and can continue known manufacture method is used for these parts.In order to improve the operation comfort of steering swivel system, the torque of regulation servomotor steering swivel system or vehicle one with member vehicle stationary, that itself be not Steering gear on support.
In order to make assembling and possibility owing to safeguard that the dismounting that causes is simple, the Rolling bearing of radial compliance sealedly detachably is fixed on the first transmission input shaft by means of an attaching parts, the preferred shape of for example screw.Between the Rolling bearing of radial compliance and the first transmission input shaft, be provided with or clamp a conjoint disk (Kupplungsscheibe) that produces the fixing shape locking action of rotation.This conjoint disk is embedded in the Rolling bearing of the first transmission input shaft and radial compliance by locking element shape sealedly.Rotation regularly with an axle bonded assembly eccentric drive core of servomotor by being rotatably supported on the first transmission input shaft at the antifriction-bearing box on its axial end portion.The eccentric drive core is disposed radially between the Rolling bearing of the first transmission input shaft and radial compliance, and is designed to radially compact as far as possible for the structure space demand that reduces steering swivel system.
Eccentric drive core preferred axes is in Rolling bearing that is embedded into radial compliance with major part and preferred hood-shaped carrier ring.Obtain the version of the axial and radially-compact of harmonic drive mechanism and steering swivel system thus.The eccentric drive core rolls in the Rolling bearing of radial compliance by the ball-bearing casing of a flexibility, and constantly makes the Rolling bearing distortion with changing.Can realize that at this according to the shape of cross section of transmission core, a columniform basically areal of support of one or more circumferential segment of the lateral surface of radial compliance Rolling bearing and carrier ring is chimeric.Carrier ring (circular-spline) radially surrounds Rolling bearing.Because the girth of the lateral surface of the Rolling bearing of radial compliance is than all length of the cylindrical bearing surface of carrier ring, so carrier ring also rotates the transmission output shaft that is permanently connected with carrier ring thus and rotates with this length difference, this transmission output shaft is connected with the input shaft of deflector again.With respect to therefore being applied on carrier ring and the transmission output shaft with high precision at the additional deflection angle of the deflection angle of importing on the steering handwheel along the plus or minus direction.
In order there to be the gap eccentric drive core is not set, one or more antifriction-bearing boxs of eccentric drive core vertically pretension on the first transmission input shaft.Axial pretightening is preferably undertaken by a cup spring, and this cup spring axially mounting is on outer shroud of antifriction-bearing box or interior ring and be bearing on the conjoint disk.In order to realize the preferred floating support of the first transmission input shaft, this first transmission input shaft is bearing on the axial end portion of transmission output shaft by a bearing.This bearing preferably constitutes needle bush.The removable sealedly rest pin of a preferred shape is embedded in this bearing on the axial end portion of the first transmission input shaft.Rest pin has a spanner width or a joint construction that is used for instrument that is different from circle, interior hexagonal for example, and be configured for simultaneously thus conjoint disk and radial compliance Rolling bearing shape sealedly detachably are fixed on attaching parts on the first transmission input shaft.
What conform with purpose can be that servomotor is provided with dividually with the shell of its shell and harmonic drive mechanism, and servo motor shaft is connected with the eccentric drive core by a preferred transmission device that slows down.This transmission device can constitute gear drive, for example spur gear transmission mechanism, Worm and worm-wheel gearing, spiral gear mechanism or bevel drive mechanism.Preferably on an axial end portion, constitute one at this eccentric drive core with a gear of this transmission device.This transmission device also can constitute and have all flexible gears (Zugmittelgetriebe) suitable and known drafting tool (Zugmitteln), drafting tool for example is odontoid belt, cone belt, chain or the like, and wherein the eccentric drive core can constitute one with belt pulley or sprocket wheel.
What conform with purpose can also be, servomotor constitutes hollow shaft motor, and wherein the rotor of servomotor is provided with rotationally around steering shaft.That can constitute one with the eccentric drive core at the hollow shaft of this servomotor and end at the transmission core in the Rolling bearing of radial compliance.
Servomotor is by control and/or control apparatus control, and wherein control and/or control apparatus are used to determine to turn to the sensor of torque, deflection angle and/or be connected with a sensor transmissions signal ground that is used for the corner of definite steering handwheel with one at input end.What can conform with purpose is that these sensors constitute the sensor of contactless work and the servo or servo steering system that steering swivel system constitutes parameter control.Preferably with servomotor, control and/or control apparatus, harmonic drive mechanism be used for determining that the corner of steering handwheel and the sensor groups of torque are contained in a shell.Each member can be separated from each other in this shell and the concealed ground setting.
The total of superposition steering system can be so that electricity between the parts of steering swivel system and/or signal transmission need the conductive mechanism of adding, as slider or wind spring etc.Can realize the raising of steering swivel system safety in operation thus.
Harmonic drive mechanism preferably mainly is formed from steel, and the Rolling bearing of radial compliance and transmission core are made by this material at least.What also can conform with purpose is that the parts of harmonic drive mechanism are made by a kind of non-metallic material or non-ferrous metal material.A lateral surface of the Rolling bearing of radial compliance can shape sealed or force closure be engaged in the cylindrical bearing surface of carrier ring (circular-spline).What can conform with purpose is that for the sealed engagement of shape, the lateral surface of the Rolling bearing of radial compliance can be provided with an outer toothed portion, and the cylindrical bearing surface of carrier ring is provided with an internal tooth portion.The number of teeth of the lateral surface of the Rolling bearing of the ratio of number of teeth radial compliance of the carrier ring of internal tooth is many, and this Rolling bearing is with the internal tooth portion engagement of at least two of its outer toothed portion circumferential segment relative on diameter and carrier ring.By eccentric or the rotation of oval-shaped transmission core in the Rolling bearing of radial compliance, when revolution moving encloses, all teeth of the outer toothed portion of the Rolling bearing of radial compliance successively with the tooth engagement of the internal tooth portion of carrier ring, carrier ring and transmission output shaft rotate with number of teeth difference thus.A gear stage by harmonic drive mechanism can be realized about 1: 20 to 1: 600 step-down ratio, a plurality of gear stages of wherein can connecting successively.A plurality of teeth mesh simultaneously, feasible torque load with respect to comparable transmission device several times becomes possibility under the situation of high superposed like this, and the harmonic drive mechanism texture ratio is less and guaranteed failure-free, zero-lash torque and corner transmission between the transmission output shaft of the first transmission input shaft and steering shaft by harmonic drive mechanism.If the friction of the areal of support of the lateral surface of Rolling bearing and carrier ring is meshed sealedly, can in certain critical range, select transmitting ratio arbitrarily so.
Under the situation of hydraulic power-assist steering system, what conform with purpose is that the stack transmission device is arranged between a convertible valve and the deflector or between steering handwheel and convertible valve.Under the situation of electric boosting steering system, the stack transmission device preferably is arranged on one and turns between torque sensor and the deflector or between steering handwheel and deflector.
What also can conform with purpose is, harmonic drive mechanism be installed in the steering shaft or steering handwheel and deflector between transmission system in, make the steering handwheel rotation be connected with carrier ring regularly, and the transmission output shaft rotation of the Rolling bearing of radial compliance and stack transmission device is permanently connected.
Description of drawings
By means of an embodiment and with reference to accompanying drawing the present invention is described below.
Fig. 1 is by the view of the local vertical profile of superposition steering system of the present invention;
The longitudinal diagram of the harmonic drive mechanism of superposition steering system among Fig. 2 Fig. 1;
The longitudinal diagram of another superposition steering system of Fig. 3;
Partial view IV among Fig. 4 Fig. 3.
The specific embodiment
Fig. 1 shows the view of the local vertical profile of the superposition steering system that constitutes active front steering system 1 that is used for vehicle.Superposition steering system 1 as the superposition steering system of electricity comprise a servomotor 10, rotation regularly with a steering handwheel 9 bonded assembly steering shafts 8, a stack transmission device 4 and an input shaft 6 that is used for deflector 7 that constitutes harmonic drive mechanism 11, described servomotor is bearing on the member 17 with vehicle stationary, and this member is not the Steering gear of vehicle.Deflector 7 can be the part of electricity or hydraulic power-assist steering system.
Deflector 7 comprises in an illustrated embodiment that the miniature gears 37 of a helical teeth on the axial end portion that is arranged on input shaft 6 and one are that can support with moving axially and constitutes with miniature gears 37 ingear tooth bars 38.Tooth bar 38 is hingedly fixed by track rod lever and the wheel of vehicle that turns to that does not illustrate in known manner.
The servo motor shaft 32 of servomotor 10 is connected with harmonic drive mechanism 11 by a transmission device 29 that constitutes flexible gear 30.Servomotor 10 is prepared an additional deflection angle is provided on the harmonic drive mechanism 11, wherein in embodiment illustrated in figures 1 and 2, on the belt pulley 31 that odontoid belt 39 is delivered to harmonic drive mechanism 11 with the torque and the rotating speed of servomotor 10.Belt pulley 31 is parts of transmission device 29 and constitutes one with one second transmission input shaft 3 and off-centre, preferred oval-shaped transmission core 12.Transmission core 12 constitutes oval-shaped in itself and belt pulley 31 direct coupled axial region.
On its oval-shaped circumference, put the ball-bearing casing 40 of a flexibility.This transmission core 12 extends axially part with it and rabbets on that made by spring steel plate, jar Rolling bearing 13 shape, radial compliance (flex-spline) from belt pulley 31 is other.Transmission core 12 by respectively be arranged on its axial end portion 21,21 ' on the antifriction-bearing box that constitutes radial ball bearing 20,20 ' rotationally be arranged on the first transmission input shaft 2.The Rolling bearing 13 of radial compliance has a lateral surface 14, and it has an outer toothed portion 35 in the axial region of ball-bearing casing 40.Outer toothed portion 35 is being engaged to one in the internal tooth portion 36 on the cylindrical bearing surface 15 with the transmission output shaft 5 bonded assembly carrier rings 16 (circular-spline) of input shaft 6 and harmonic drive mechanism 11 with two circumferential segment 41 under the effect of the ellipse of Rolling bearing 13 expansion.Carrier ring 16 is fixed on the input shaft 6 or transmission output shaft 5 of deflector 7 with one heart with the longitudinal axis 42 of steering shaft 8.When 12 rotations of transmission core, oval-shaped expansion is carried out continuously along internal tooth portion 36 with changing.The number of teeth of the carrier ring 16 of internal tooth is greater than the number of teeth of the Rolling bearing 13 of radial compliance, and transmission core 12 revolutions moving enclose thus, and carrier ring 16 rotates with number of teeth difference.
In order to make and assemble harmonic drive mechanism 11 at an easy rate, structure like this on this harmonic drive mechanism function makes it can be configured to not have shell, and what however conform with purpose is, it is arranged in the shell 43 of deflector 7 (seeing Fig. 3,4).
For simpler assembling, for the part that provides for simple replacement of harmonic drive mechanism 11 and for also can be with the part of known manufacture method by different material manufacture harmonic drive mechanisms, the first transmission input shaft, 2 shapes sealedly detachably be connected with the Rolling bearing 13 of radial compliance.The transmission of torque of the Rolling bearing 13 from the first transmission input shaft 2 to radial compliance is born by a conjoint disk 19, and this conjoint disk extend in the Rolling bearing 13 and the first transmission input shaft 2 of radial compliance by means of locking piece.Conjoint disk 19 constitutes attaching parts 18 screw, that extend in the first transmission input shaft 2 by one and detachably is fixed on the end face that extend into the first transmission input shaft 2 in the carrier ring 16.
Shown in Fig. 1 to 4, cup spring 24 axially is clamped between the annular lip 44 of the Rolling bearing 13 of ring 23 and radial compliance in of antifriction-bearing box 20.Cup spring 24 makes antifriction-bearing box 20 axial pretightenings, and transmission core 12 seamless unoccupied places are placed on the first transmission input shaft 2.Cup spring 24 also can act on the outer shroud 22 of antifriction-bearing box 20.
Fig. 3 and 4 shows the longitudinal diagram of a superposition steering system 1, its servomotor 10 constitutes hollow shaft motor 33, the first transmission input shaft 2 needn't cantilever support in harmonic drive mechanism 11 by the present invention's structure, but the first transmission input shaft 2 can be bearing in the carrier ring 16 or first transmission output shaft 5 by a bearing 25.Bearing 25 constitutes needle bush 26 and radial bearing, and the rest pin 27 that one of them shape is removable sealedly extend in the needle bush 26 in the end of the first transmission input shaft 2.Rest pin 27 has an interior hexagonal, simultaneously is fixed on attaching parts 18 on the first transmission input shaft 2 as being used for Rolling bearing 13 with conjoint disk 19 and radial compliance thus.In the embodiment shown in all, a head of attaching parts 18 axially extend in the transmission output shaft 5, and the version of harmonic drive mechanism 11 is very compact thus.
Hollow shaft motor 33 is provided with the longitudinal axis of steering shaft 8 is concentric.The first transmission input shaft 2 that servomotor 10 is diverted axle 8 passes, and wherein the rotor 34 of servomotor 10 can be rotatably set on the servo motor shaft 32 around steering shaft 8.Servo motor shaft 32 is configured to one with transmission core 12, and by means of antifriction-bearing box 20,20 ' and needle bush 26 and another needle bush 45 between transmission input shaft 2 and servo motor shaft 32 in transmission output shaft 5 support.Another needle bush 45 and antifriction-bearing box 20,20 ' axially-spaced are apart from the ground setting.
The stator 46 of servomotor 10 is fixedly installed on the shell 43, and shell surrounds harmonic drive mechanism 11, servomotor 10 and control and/or control apparatus 47.Harmonic drive mechanism 11, servomotor 10 and control and/or control apparatus 47 spatially are separated from each other with concealed ground and are arranged in the shell 43.
Replace the lateral surface 14 of Rolling bearing 13 and the sealed engagement of shape of the internal tooth portion 36 of carrier ring 16, what can conform with purpose is, lateral surface 14 meshes with cylindrical bearing surface 15 frictions of carrier ring 16 sealedly, can select transmitting ratio arbitrarily thus, and its denominator is not an integer.Also meticulous tooth pitch, groove line or annular knurl can be set in addition.
Reference numerals list
1 superposition steering system, 26 needle bushes
2 first transmission power shafts, 27 fulcrum posts
3 second transmission power shafts, 28 grooves
4 stack transmission mechanisms, 29 transmission mechanisms
5 transmission output shafts, 30 flexible gears
6 input shafts, 31 belt pulleys
7 deflectors, 32 servo motor shafts
8 steering shafts, 33 hollow shaft motors
9 steering handwheels, 34 rotors
10 servomotors, 35 outer toothed portion
11 harmonic drive mechanisms, 36 internal tooth portions
The miniature gears of 12 eccentric drive cores, 37 helical teeth
Rolling bearing 38 tooth bars of 13 radial compliance
1412 lateral surface 39 odontoid belts
15 columniform areal of support 40 ball-bearing casings
16 supportings, 41 circumferential segment
17 with the member of vehicle stationary, 428 longitudinal axis
The shell of 18 attaching partss 4311
19 conjoint disks, 44 shape flanges
20,20 ' antifriction-bearing box, 45 needle bushes
21,21 ' 12 axial end portion 46 stators
22 outer shrouds, 47 control and/or control apparatuss
Ring 48 in 23
24 cup springs 49
25 bearings 50
The axial region of x 16
Claims (17)
1. superposition steering system that is used for vehicle, the superposition steering system of or servo steering system servo especially for automobile, described superposition steering system comprises that one has one first transmission input shaft (2) and one second transmission input shaft (3), constitute the stack transmission device (4) of harmonic drive mechanism (11), being used for will be at described two transmission input shaft (2,3) be added to of stack transmission device (4) of the corner that go up to produce affacts on the transmission output shaft (5) on the input shaft (6) of a deflector (7), wherein the first transmission input shaft (2) is connected with a steering handwheel (9) effect by a steering shaft (8), and the effect of the second transmission input shaft (3) and a servomotor (10) is connected, it is characterized in that: the first transmission input shaft (2) detachably is connected with the Rolling bearing (13) of a radial compliance of harmonic drive mechanism (11) and passes of harmonic drive mechanism (11) and extend into the interior eccentric drive core (12) of radial compliance Rolling bearing (13).
2. by the described superposition steering system of claim 1, it is characterized in that: described servomotor (10) is prepared a torque and corner are provided on the eccentric drive core (12) on the second transmission input shaft (3) of harmonic drive mechanism (11), and the Rolling bearing of described radial compliance (13) shape sealedly detachably is connected with the first transmission input shaft (2), and one or more circumferential segment of a lateral surface (14) of radial compliance Rolling bearing (13) change continuously with a rotation regularly with areal of support (15) engagement of the substantially cylindrical of transmission output shaft (5) bonded assembly carrier ring (16).
3. by claim 1 or 2 described superposition steering systems, it is characterized in that: the torque of described servomotor (10) superposition steering system (1) or vehicle one with member vehicle stationary, that be different from a Steering gear (17) on supported.
4. by one of claim 1 to 3 described superposition steering system, it is characterized in that: the Rolling bearing of described radial compliance (13) is fixed on the first transmission input shaft (2) by an attaching parts (18) and a conjoint disk (19).
14. by the described superposition steering system of claim 13, it is characterized in that: described transmission device (29) is a gear drive, for example is a spur gear transmission mechanism, a Worm and worm-wheel gearing, a spiral gear mechanism or a conical gear drive.
15. by the described superposition steering system of claim 14, it is characterized in that: described eccentric drive core (12) constitutes one with a gear of the second transmission input shaft (3) and transmission device (29).
16. by the described superposition steering system of claim 13, it is characterized in that: described transmission device (29) constitutes flexible gear (30).
17. by the described superposition steering system of claim 16, it is characterized in that: the described eccentric drive core (12) and the second transmission input shaft (3) constitute one with a belt pulley (31) of transmission device (29).
18. by one of claim 1 to 12 described superposition steering system, it is characterized in that: described eccentric drive core (12) constitutes one with a servo motor shaft (32) that constitutes the second transmission input shaft (3).
19. by the described superposition steering system of claim 18, it is characterized in that: described servomotor (10) constitutes hollow shaft motor (33), wherein a rotor (34) of servomotor (10) is set to and can rotates around steering shaft (8).
20. by one of claim 1 to 19 described superposition steering system, it is characterized in that: current supply and/or signal transmission to described servomotor (10) do not need a transport sector, as slider or wind spring.
21. by one of claim 1 to 20 described superposition steering system, it is characterized in that: described harmonic drive mechanism (11) is formed from steel basically.
22. by one of claim 1 to 20 described superposition steering system, it is characterized in that: described harmonic drive mechanism is made of plastics basically.
23. by the described superposition steering system of one of claim 1 to 22, it is characterized in that: described Rolling bearing (13) has an internal tooth portion (a 36) ingear outer toothed portion (35) with carrier ring (16).
24. by one of claim 1 to 23 described superposition steering system, it is characterized in that: described stack transmission device (4) is arranged in hydraulic power-assist steering system between a convertible valve and the deflector (7) or between steering handwheel (9) and convertible valve.
25. by the described superposition steering system of one of claim 1 to 23, it is characterized in that: described stack transmission device (4) is arranged between a steering torque sensor and the deflector (7) in electric boosting steering system or between steering handwheel (9) and deflector (7).
26. by one of claim 2 to 25 described superposition steering system, it is characterized in that: described harmonic drive mechanism (11) is installed between steering handwheel (9) and the deflector (7), makes carrier ring (16) rotation be connected with steering handwheel (9) regularly and the Rolling bearing (13) of radial compliance rotates and is connected with transmission output shaft (5) regularly.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP03028023.4 | 2003-12-06 | ||
| EP20030028023 EP1431161B1 (en) | 2002-12-19 | 2003-12-18 | Steering system for a vehicle |
| DE102004003582.2 | 2004-01-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1867477A true CN1867477A (en) | 2006-11-22 |
| CN100422024C CN100422024C (en) | 2008-10-01 |
Family
ID=37433857
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800290916A Expired - Fee Related CN100422024C (en) | 2003-12-06 | 2004-12-02 | Superimposed steering system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100422024C (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102224056A (en) * | 2009-04-09 | 2011-10-19 | 高田-彼得里公开股份有限公司 | Steering wheel for a motor vehicle having superimposed steering |
| CN104903177A (en) * | 2013-01-09 | 2015-09-09 | 蒂森克虏伯普利斯坦股份公司 | Angle superimposition apparatus for a vehicle steering device |
| CN107010097A (en) * | 2015-12-17 | 2017-08-04 | 株式会社捷太格特 | Transfer |
| CN109955896A (en) * | 2017-12-22 | 2019-07-02 | 美国Trw天合汽车集团 | Torque is superimposed transfer |
| CN110803214A (en) * | 2019-10-30 | 2020-02-18 | 中国第一汽车股份有限公司 | Steering column for automobile |
| CN113335368A (en) * | 2021-07-22 | 2021-09-03 | 中国第一汽车股份有限公司 | Intelligent automobile man-machine cooperation steering input device |
| CN113883185A (en) * | 2021-08-29 | 2022-01-04 | 北京工业大学 | Miniature clutch device based on servo control |
| CN114502448A (en) * | 2019-10-13 | 2022-05-13 | 感知公司 | Method and system arrangement for steering a vehicle and vehicle having such a system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| KR100458378B1 (en) * | 1996-05-17 | 2005-04-06 | 혼다 기켄 고교 가부시키가이샤 | Electric Power Steering Device |
| DE29715257U1 (en) * | 1997-08-26 | 1997-12-04 | Atlas Copco Electric Tools GmbH, 71364 Winnenden | Driving device |
| JPH11115779A (en) * | 1997-10-16 | 1999-04-27 | Harmonic Drive Syst Ind Co Ltd | Power assisting device for motor-driven power steering |
| EP1013534B1 (en) * | 1998-12-08 | 2002-09-18 | Ford-Werke Aktiengesellschaft | Electrical power steering especially for motor vehicles |
| DE10214655A1 (en) * | 2002-04-03 | 2003-10-30 | Zf Lenksysteme Gmbh | Power-assisted steering device for a motor vehicle has overlaid gearing with feeder gear elements, steering gears and worm gear pairs. |
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2004
- 2004-12-02 CN CNB2004800290916A patent/CN100422024C/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102224056A (en) * | 2009-04-09 | 2011-10-19 | 高田-彼得里公开股份有限公司 | Steering wheel for a motor vehicle having superimposed steering |
| US8631896B2 (en) | 2009-04-09 | 2014-01-21 | Takata-Petri Ag | Steering wheel for a motor vehicle having superimposed steering |
| CN104903177A (en) * | 2013-01-09 | 2015-09-09 | 蒂森克虏伯普利斯坦股份公司 | Angle superimposition apparatus for a vehicle steering device |
| CN104903177B (en) * | 2013-01-09 | 2017-03-08 | 蒂森克虏伯普利斯坦股份公司 | Equipment is superimposed for the angle of vehicle steering device |
| CN107010097A (en) * | 2015-12-17 | 2017-08-04 | 株式会社捷太格特 | Transfer |
| CN109955896A (en) * | 2017-12-22 | 2019-07-02 | 美国Trw天合汽车集团 | Torque is superimposed transfer |
| CN109955896B (en) * | 2017-12-22 | 2022-07-29 | Zf主动安全与电子美国有限责任公司 | Torque superposition steering device |
| CN114502448A (en) * | 2019-10-13 | 2022-05-13 | 感知公司 | Method and system arrangement for steering a vehicle and vehicle having such a system |
| CN110803214A (en) * | 2019-10-30 | 2020-02-18 | 中国第一汽车股份有限公司 | Steering column for automobile |
| CN113335368A (en) * | 2021-07-22 | 2021-09-03 | 中国第一汽车股份有限公司 | Intelligent automobile man-machine cooperation steering input device |
| CN113335368B (en) * | 2021-07-22 | 2022-06-10 | 中国第一汽车股份有限公司 | Intelligent automobile man-machine cooperation steering input device |
| CN113883185A (en) * | 2021-08-29 | 2022-01-04 | 北京工业大学 | Miniature clutch device based on servo control |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100422024C (en) | 2008-10-01 |
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| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: ROBERT BOSCH AUTOMOTIVE STEERING GMBH Free format text: FORMER NAME: ZF FRIEDRICHSHAFEN AG |
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| CP01 | Change in the name or title of a patent holder |
Address after: Germany, Germany Patentee after: ROBERT BOSCH AUTOMOTIVE STEERING GmbH Address before: Germany, Germany Patentee before: ZF LENKSYSTEME GmbH |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20081001 |