CN101247971A - Eccentricity gear step - Google Patents
Eccentricity gear step Download PDFInfo
- Publication number
- CN101247971A CN101247971A CNA200680031036XA CN200680031036A CN101247971A CN 101247971 A CN101247971 A CN 101247971A CN A200680031036X A CNA200680031036X A CN A200680031036XA CN 200680031036 A CN200680031036 A CN 200680031036A CN 101247971 A CN101247971 A CN 101247971A
- Authority
- CN
- China
- Prior art keywords
- gear stage
- actuator
- rolling
- housing
- driven
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
- F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
- F16H13/08—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion with balls or with rollers acting in a similar manner
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
- B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
- B60N2/2252—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms in which the central axis of the gearing lies inside the periphery of an orbital gear, e.g. one gear without sun gear
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Aviation & Aerospace Engineering (AREA)
- Transportation (AREA)
- Retarders (AREA)
- Gear Transmission (AREA)
Abstract
A gear step (1) for an actuator in a motor vehicle, in particular for a vehicle seat, comprises a housing (3) provided with a drive (11) which mounted thereon in such a way that it is rotatable around an axis (A), driven output (21) rotatable about a second axis (B) differring from the axes (A). The drive (11) is used for receiving the driven output (21) by means of at least one rolling body (31) separated from the axes (A, B) at a parallel offset with respect to an eccentricity (E) and drives said driven output by rotating the thus obtained rolling eccentricity, wherein the driven output (21) carries out a tumbling rolling movement on the housing (3) by means of a friction oscillating gear (33, 35).
Description
The present invention relates to have the gear stage of feature of the preamble of claim 1.
DE19709852C2 discloses such gear stage, and wherein, the worm screw that is positioned on the motor spindle is used as actuator, and with driven mouth on worm gear engagement.This gear stage is the integrated form parts of actuator, and wherein worm gear drives the mechanism that is used to regulate seat then.By the suitable lead of screw thread on the worm and wheel, gear stage decelerates to high motor speed the low input speed of mechanism.
The objective of the invention is to improve the gear stage of the above-mentioned type.According to the present invention, this purpose realizes by the gear stage with claim 1 feature.Advantageous embodiments has formed the theme of dependent claims.
With respect to known gear stage, transmitting ratio is increased, because actuator is supporting driven mouth by at least one rolling element that forms discretely, and eccentric throw of parallel axes ground skew, and when the rolling element that so forms rotates driven mouth by the slip gear swinging gear, thereby make it carry out rolling movement on housing, when especially swinging rolling movement, actuator drives this driven mouth.Simultaneously, efficient has also improved significantly, thereby allows actuator, and such as the also raising similarly of combined efficiency of the actuator that preferably uses gear stage of the present invention in it, this has produced weight and reducing by the occupied comprehensive space of necessary member.Driven mouth can be considered by actuator " support ", because driven mouth also can partly be supported on the housing.
The rolling movement of driven mouth is substantially the rotational motion of the hunting motion with stack, though especially under the less situation of eccentric throw, the swing rolling movement can be compensated such as the play between driven mouth and the outgoing side mechanism to be driven (load-carrying mechanism) etc., perhaps compensates by the suitable elasticity between these parts.Under the bigger situation of eccentric throw, further member also can be connected to the outgoing side of stressed driven mouth, this further member has formed the actual driven mouth of gear stage, and carry out the rotational motion of hunting motion with respect to stressed driven mouth, but then carry out pure rotational motion with respect to actuator with stack.
To a certain degree rolling off-centre helps comprehensive transmitting ratio between actuator and the driven mouth.By preferably on one of them of two members, being formed for being preferably the groove of ball-shaped rolling element, and this is become:, all to obtain improvement on actuator and the driven mouth with respect to the simple rolling of rolling element such as setting different theoretical running radius of tires by the use of sloped sidewall.
The slip gear swinging gear is very helpful to comprehensive transmitting ratio, and this slip gear swinging gear produces slight swing relative motion between driven mouth and housing under the less situation of eccentric throw.Preferably betide driven mouth around the point of the rolling between the guide in body and the housing, as the instantaneous of the swing rolling movement of driven mouth and use.When actuator rotated, the application force that produces of the wedge by actuator, rolling element and driven mouth preferably was applied to driven mouth at the rolling drive torque of naming a person for a particular job.In case actuator has been finished it and driven rotation, freely swinging of actuator makes this application force dissipate once more, and the protection member.
Favourable geometric proportion has been guaranteed clear and definite and computable relative motion.La Jin two rolling elements are used to prevent to drive any idle travel that rotates when beginning against each other, and gear stage becomes self-locking.Gear stage of the present invention preferably combines with the motor of electric rectification and self-locking mechanism with eccentric planet train of gears.
In a preferred embodiment, at least one driver element in housing, actuator and the driven mouth, and preferably all driver elemenies are made of plastic-metal composite material.The metal that is contained in it is partly guaranteed high load-carrying ability, and plastic areas then allows complicated geometric configuration, the manufacturing that cost benefit is calculated, lower weight to reach very good damping force characteristics in non-load uptake zone.The metal part is preferably made by the about constant high duty metal thin slice of material thickness is carried out machinework, and it has avoided expensive reprocessing.
Explain the present invention in more detail below with reference to being expressed in two exemplary embodiments in the accompanying drawing, among the figure:
Fig. 1 showed the line I-I in Fig. 2 and passed the axial cross section of first exemplary embodiment,
Fig. 2 showed the line II-II in Fig. 1 and passed the radial section of first exemplary embodiment,
Fig. 3 showed corresponding with Fig. 1 and passed the cross section of first Application Example of the present invention,
Fig. 4 showed corresponding with Fig. 1 and passed the cross section of second Application Example of the present invention,
Fig. 5 showed along the line V-V among Fig. 6 and passed the axial cross section of exemplary embodiment,
Fig. 6 has showed along the line VI-VI among Fig. 5 and has passed the radial section of exemplary embodiment.
In first exemplary embodiment, gear stage 1 has the housing 3 that is approximately cylinder ground symmetry, and this housing 3 has center first axle A.The housing axle collar 5 radially and with first axle A is formed at the inside of housing 3 with one heart.Housing 3 has the case lid 7 that is positioned at radially outer, and case lid 7 is formed by enclosure body 9 discretely, and when to gear stage 1 assembling the time and securely be connected on the enclosure body 9.Actuator 11 is supported on the housing 3 similarly and with first axle A with one heart.Actuator 11 has hollow cylinder driving tube 13, and itself and first axle A are inserted in the housing axle collar 5 with one heart; The driving flange of giving prominence to radially outwardly in the end 15; And being formed at the axle drive shaft carrier ring 17 that drives on the flange 15, axle drive shaft carrier ring 17 is concentric with first axle A, and overlaps with the housing axle collar 5.Rub less and the cylindrical bearing 19 of support drive part 11 in radial direction (with respect to first axle A) specially, such as the spheroid bearing or be preferably needle bearing, be arranged between the outside of the inside of axle drive shaft carrier ring 17 and the housing axle collar 5.
In its outside, promptly in the outside of driven output shaft carrier ring 27, driven mouth 21 has that periphery distributes and is radially outstanding around body 33, should form with one heart around body 33 and the second axis B, and should engage with the interior periphery guide 35 of housing 3 with tongue-groove ways of connecting around body 33.The channel-like guide 35 that forms with one heart as annular ditch groove and with first axle A is partly by enclosure body 9 and partly be formed at by case lid 7 on the common sides that housing 3 radially inwardly faces.
The sidewall of guide 35 tilts slightly with respect to the plane vertical with first axle A, thereby makes the bottom that can't fully penetrate guide 35 around body 33, and only farthest can be through the some W that rolls.Around body 33 is driven mouth 21, with guide 35 be that housing 3 has formed slip gear mechanism, after this be called the slip gear swinging gear.Radially with the some W opposed side edges of rolling on, between body 33 and guide 35, or the distance between driven mouth 21 and the housing 3 is 2xE, it is greater than a distance of putting the W place in rolling.Similarly, actuator 11 is 2xE with the distance of driven mouth 21 at the some place of the most close rolling point W, and it is greater than the respective distances on the opposed side edges radially.Therefore, similarly periphery direction curved wedge face is present between driven mouth 21 and the housing 3 simultaneously, and also is present between driven mouth 21 and the actuator 11.Contact point between housing 3, actuator 11 and the driven mouth 21 generally is positioned at same plane, and this plane is perpendicular to axis A and B.
The outside of actuator 11, spheroid 31 have formed geometric configuration with groove 29, spheroid 31 is wedged between actuator 11 and the driven mouth 21 in this geometric configuration, because angle of contact is less than from the locking angle, therefore cliding friction does not take place in the contact point place of spheroid 31, and this also is known on such as wedging roller flywheel clutch.Because actuator 11 is static, the spheroid of observing from the periphery direction of first axle A 31 initially is positioned at rolling to be put on the identical angle of W, thus between actuator 11 and the groove 29 without any radial tension.On the other hand, spheroid 31 also moves when actuator 11 is driven, up to aforementioned wedge takes place.Because the cause of current geometric configuration and material, spheroid 31 are led over about 45 degree (angle of lead) of some W that roll.
In Fig. 2, actuator 11 anticlockwise directions are driven, thereby spheroid 31 is rolled on the outside of driven mouth 11, and promptly spheroid 31 clockwise rotates in Fig. 2.This causes the relative rolling movement of spheroid 31 in groove 29, and because wedge, this causes the appreciable directed force F in contact point place between spheroid 31 and the driven mouth 21.Owing to driven mouth 21 housing 3 in the some W place's breasting of rolling, the some W that promptly rolls has formed the wink point, and directed force F has produced the moment that acts on driven mouth 21 and center on the some W that rolls.This causes the swing rolling movement of driven mouth 21 on housing 3, and it is clockwise direction in Fig. 2.If the direction of rotation of actuator 11, after size was spheroid 31 angle of lead two-fold idle travels, the rotation direction of driven mouth 21 was also opposite similarly so.Suitable lubricant can be provided,, reduce simultaneously such as on the spheroid 31 or the wearing and tearing at the some W place of rolling so that have on the some position of high surfaces cell pressure the moment of increasing friction coefficient.
Gear stage 1 has the secondary design, and is presented as to have rolling accentric slip gear swinging gear.Because the rolling movement of spheroid 31 between actuator 11 and driven mouth 21, initially have with respect to the rolling off-centre of spheroid 31 and to be approximately 2: 1 theoretical transfer ratio.Providing radius than spheroid 31 little and produced extra transmission component towards the groove 29 of the theoretical running radius of tire of driven mouth 21, is 4: 1 in this case.Slip gear swinging gear level has produced the transmitting ratio component that approximates driven mouth 21 external diameters that eccentric throw is 2xE (housing 3 is at the diameter at some W place that rolls) greatly, is about 125: 1 in this case.Therefore generally speaking, the rotation of actuator 11 several magnitude of can slowing down.When eccentric throw E reduced, splitting effect was reduced, and transmitting ratio (perhaps reduction ratio) is increased.Can be not destroyed in order to make driver element can bear stress that contact force and driving torque produce, preferably use high-strength metal material to realize this purpose.Yet, use the highstrenghtpiston so that giving driven mouth 21 also is feasible with elastic surface, such as in order to weaken vibration and for obviously bigger mating surfaces is provided.
When stopping, in order to prevent to form non-circular surfaces, preferably produce a kind of equipment, rotating backward when no longer using with box lunch and with actuator 11, (such as fixing default value is 90 degree to a free pivot angle, determine) perhaps electronicly, so that make spheroid 31 its angle of lead of can rolling backward, and begin to set aside to most probable near near the some W that rolls, spheroid 31 no longer produces any directed force F at this.
In order to improve the contact of spheroid 31 when moving on the actuator 11, and then improve described wedge simultaneously, promptly in order to prevent " skidding " as much as possible at this some place, revise among the embodiment at one, actuator 11 preferably always has slight friction with spheroid 31, and can not stop rotation.This slight friction can be by applying such as the normal force of the spring between actuator 11 and the spheroid 31, perhaps by one of them magnetization in the member is applied.In order to reduce the idle travel of spheroid 31 in reversing sense, in revising embodiment, can provide two spheroids 31, it is retained on together or separates by spring.Therefore gear stage 1 also becomes self-locking.
In first example application, gear stage 1 of the present invention combines with motor 41, thereby forms driver element 43.In this case, by a plurality of permanent magnets are assembled on the actuator 11 as rotor magnetic patch 45, preferably be assembled on the driving tube 13, thereby make actuator 11 become rotor, and by a plurality of stator pack 47 are arranged in the housing 3, so that with rotor magnetic patch 45 mutual action contactlessly, gear stage 1 integrates mutually with motor 41.Control piece 49 provides the electric rectification of stator pack 47, and therefore the electric rectification of motor 41 is provided.For speed being controlled by feedback, ring-type magnetic patch 51 is assembled on the driven mouth 21, preferably be assembled on the driven delivery pipe 23, and interact, so that detect the position, angle of driven mouth 21 with Hall element 53 in the housing 3 that is connected to control piece 49.The electronic building brick of motor 41 is foreclosed, but gear stage 1 has formed a shell type unit.
In second example application, gear stage 1 of the present invention combines with mechanism 61, thereby forms the actuator 63 in the vehicle, in particular for the actuator of seat.This mechanism 61 is with the form of the back of seat angle demodulator that is used for seat and be described in DE 10144840A1, and its disclosure is incorporated into this clearly.Be presented as that the mechanism 61 of self-locking eccentric planet train of gears has first assembly parts 65 of inner gear form, and have second assembly parts 67 with inner gear ingear formed gear.First assembly parts 65 are connected on the backrest such as seat securely, and second assembly parts 67 then are connected on the seat part of seat.Two-piece type (or alternatively single type) actuator 69 and two mutual slack-free wedge-shaped segment 71 have defined eccentric structure, this actuator is supported between first assembly parts 65 and second assembly parts 67, and when rotating, this actuator makes the assembly parts 65 of winning make the swing rolling movement with respect to second assembly parts 67.
For gear stage 1 is combined with mechanism 61, housing 3 is assembled on first assembly parts 65 by its case lid 7, the outside main shaft 73 that is shaped then at one end with the in-profile engagement of driven delivery pipe 23, and mesh at the in-profile of the other end and actuator 69.At this, all be provided with play between the profile in every kind of situation, so that compensate the hunting motion of driven mouth 21.Hunting motion also can be installed especially by other, and flexible apparatus is compensated.
By first application examples and second application examples are combined, actuator 63 is finished by motor 41.
Unless below describe separately, second exemplary embodiment is identical with first exemplary embodiment, for this reason, it is 100 label that the identical or similar member of function has identical and prefix.The single or multiple features of first exemplary embodiment also can embody in conjunction with the feature of second exemplary embodiment, and vice versa.
In second exemplary embodiment, gear stage 101 has the housing 103 that is approximately cylinder ground symmetry, and this housing 103 has center first axle A.The housing axle collar 105 radially and with first axle A is formed at the inside of housing 103 with one heart.Housing 3 has the case lid 107 that is positioned at radially outer, and case lid 107 is formed by enclosure body 109 discretely, and when to gear stage 101 assembling the time and securely be connected on the enclosure body 109.Actuator 111 is supported on the housing 103 similarly and with first axle A with one heart.Actuator 111 has hollow cylinder driving tube 113, and itself and first axle A are inserted in the housing axle collar 105 with one heart; The driving flange of giving prominence to radially outwardly in the end 115; And being formed at the axle drive shaft carrier ring 117 that drives on the flange 115, axle drive shaft carrier ring 17 is concentric with first axle A, and overlaps with the housing axle collar 105.Rub less and the cylindrical bearing 119 of support drive part 111 in radial direction (with respect to first axle A) specially, such as the spheroid bearing or be preferably between the outside that needle bearing is arranged on the inside of axle drive shaft carrier ring 117 and the housing axle collar 105.
In its outside, promptly in the outside of driven output shaft carrier ring 127, driven mouth 121 has that periphery distributes and is radially outstanding around body 133, should form with one heart around body 133 and the second axis B, and should engage with the interior periphery guide 135 of housing 103 with tongue-groove ways of connecting around body 133.The channel-like guide 135 that forms with one heart as annular ditch groove and with first axle A is partly by enclosure body 109 and partly be formed at by case lid 107 on the common sides that housing 103 radially inwardly faces.
The sidewall of guide 135 tilts slightly with respect to the plane vertical with first axle A, thereby makes the bottom that can't fully penetrate guide 135 around body 133, and only farthest can be through the some W that rolls.Around body 133 is driven mouth 121, with guide 135 be that housing 103 has formed slip gear mechanism, after this be called the slip gear swinging gear.Radially with the some W opposed side edges of rolling on, between body 133 and guide 135, or the distance between driven mouth 121 and the housing 103 is 2xE, it is greater than a distance of putting the W place in rolling.Similarly, actuator 111 is 2xE with the distance of driven mouth 121 at the some place of the most close rolling point W, and it is greater than the respective distances on the opposed side edges radially.Therefore, similarly periphery direction curved wedge face is present between driven mouth 121 and the housing 103 simultaneously, and also is present between driven mouth 121 and the actuator 111.Contact point between housing 103, actuator 111 and the driven mouth 121 generally is positioned at same plane, and this plane is perpendicular to axis A and B.
The outside of actuator 111, spheroid 131 have formed geometric configuration with groove 129, leading over the spheroid 131 of the some W (leading angle of lead) that rolls wedges between actuator 111 and the driven mouth 121 in this geometric configuration, because angle of contact is less than from the locking angle, therefore on the contact point of spheroid 131 cliding friction does not take place, this also is known on such as wedging roller flywheel clutch.Therefore, with the some W Fu spheroid 131 not wedgings of rolling.When actuator 111 was driven, spheroid 31 rolled on the outside of driven mouth 111.This causes the relative rolling movement of spheroid 131 in groove 129, and because the wedge of leading spheroid, this causes the appreciable application force in contact point place between leading spheroid 131 and the driven mouth 121.Owing to driven mouth 121 housing 103 in the some W place's breasting of rolling, the some W that promptly rolls has formed the wink point, and application force has produced the moment that acts on driven mouth 121 and center on the some W that rolls.This causes the swing rolling movement of driven mouth 121 with respect to housing 103.If the direction of rotation of actuator 111, afterwards, the rotation direction of driven mouth 121 is also opposite similarly at minimum idle travel (up to another spheroid 131 wedgings) so.Suitable lubricant can be provided,, reduce simultaneously such as on the spheroid 131 or the wearing and tearing at the some W place of rolling so that have on the some position of high surfaces cell pressure the moment of increasing friction coefficient.If spheroid 131 is compressed by spring or fixing dividually, gear stage 101 becomes self-locking.
At least one driver element in housing 103, actuator 111 and the driven mouth 121, and be preferably all driver elemenies and constitute by plastic-metal composite material.Being contained in metal in it partly allows driver element to stand contact force and from the stress of drive torque and can be not destroyed.Preferably make, because deep-draw is pulled out, punching and punching press etc. provide necessary accuracy and surface quality, and do not needed extra reprocessing by high duty metal (being preferably steel) thin slice.Heat treatment is used to improve strength characteristics.The associated metal part preferably is molded in the highstrenghtpiston, and therefore interosculates.Plastic areas then allows complicated geometric configuration to reach the manufacturing that cost benefit is calculated in non-load breasting district, lower weight and very good damping force characteristics, reach the noise properties that improves, and be used for the curved surface (words if necessary) and the obvious bigger contact area of damped vibration.Unless indicate separately, the metal in the exemplary embodiment partly has at least approximately constant material thickness, and plastic areas then occupies the remaining space of corresponding transfer element.
In the exemplary embodiment, housing 103 has metal part 103m, and it passes through the housing axle collar of enclosure body 109 and extend to guide 135 from the housing axle collar 105, is used for breasting around body 133.The remainder of enclosure body 109 is formed by the plastic areas 103k of housing 103.The case lid 107 of giving housing 103 has metal part 107m, and it extends to guide 135 always, is used for breasting around body 133, and the remainder of case lid 107 then is plastic areas 107k.Corresponding plastic areas 103k and 107k weld mutually by super sonic, so that housing 103 and this case lid 107 are combined.
Actuator 111 has the first metal part 111m, and it extends to the side of axle drive shaft carrier ring 117 towards cylindrical bearing 119 from driving tube 113 via driving flange 115; The second metal part 111n, it is arranged on axle drive shaft carrier ring 117 on the side of spheroid 131; And be positioned at the plastic areas 111k of axle drive shaft carrier ring 117 remainders.
Similar with first exemplary embodiment, thus gear stage 101 can combine with motor and forms driver element, thus and/or combine the actuator that is formed for regulating such as the vehicle seat back gradient with mechanism.
Label list
1,101 gear stage
3,103 housings
5, the 105 housing axle collars
7,107 case lid
9,109 enclosure body
11,111 actuators
13,113 driving tubes
15,115 drive flange
17,117 axle drive shaft carrier rings
19,119 cylindrical bearings
21,121 driven mouths
23,123 driven delivery pipes
25,125 driven output panels
27,127 driven output shaft carrier rings
29,129 (V-arrangement) groove
31,131 spheroids, rolling element
33,133 around body
35,135 guides
41 motors
43 driver elements
45 motor magnetic patch
47 stator pack
49 control pieces
51 ring-type magnetic patch
53 Hall elements
61 mechanisms
63 actuators
65 first assembly parts
67 second assembly parts
69 actuators
71 wedge-shaped segment
73 main shafts
The plastic areas of 103k housing
The metal part of 103m housing
The plastic areas of 107k case lid
The metal part of 107m case lid
The plastic areas of 111k actuator
The first metal part of 111m actuator
The second metal part of 111n actuator
The plastic areas of the driven mouth of 121k
The first metal part of the driven mouth of 121m
The second metal part of the driven mouth of 121n
The A first axle
B second axis
The E eccentric throw
The F application force
W rolling point
Claims (29)
1. gear stage (1 that is used for vehicle in particular for the actuator (63) of seat, 101), it comprises: housing (3,103), be installed in described housing (3,103) thus go up and to make it can center on the actuator (11 of first axle (A) rotation, 111), and can be around the driven mouth (21 of second axis (B) rotation that is different from described first axle (A), 121), it is characterized in that: described actuator (11,111) by at least one rolling element that forms discretely (31,131) support described driven mouth (21,121), and described axis (A, B) depart from abreast with eccentric throw (E), and the rolling off-centre of working as so formation is by slip gear swinging gear (33,35,133,135) and at described housing (3,103) go up rotation and carry out the described driven mouth (21 that rolling movement is especially swung rolling movement, 121) time, described actuator (11,111) drive described driven mouth (21,121).
2. gear stage as claimed in claim 1, it is characterized in that, when described actuator (11,111) rotated, described rolling element (31,131) was gone up at described actuator (11,111) simultaneously and is rolled, and also went up at described driven mouth (21,121) and roll.
3. gear stage as claimed in claim 2, it is characterized in that, on the one hand, described rolling element (31,131) partly rolls in the ring-type periphery groove (29,129) in described driven mouth (21,121) or in the described actuator (11,111), and on the other hand, described rolling element (31,131) rolls the outside or inner of corresponding another member.
4. gear stage as claimed in claim 3 is characterized in that, described rolling element (31,131) is presented as spheroid, and is formed with sidewall on the described groove (29,129), described sidewall slope in the vertical plane of described axis (A, B).
5. as any one the described gear stage among the claim 2-4, it is characterized in that, when described actuator (11,111) rotates, described rolling element (31,131) is wedged between described actuator (11,111) and the described driven mouth (21,121), and has produced application force (F).
6. the described gear stage of any one claim as described above is characterized in that, described rolling accentric rotates the reduction ratio that produces greater than 2: 1.
7. the described gear stage of any one claim as described above is characterized in that described eccentric throw (E) is less than or equal to 0.5 millimeter.
8. the described gear stage of any one claim as described above, it is characterized in that, ring-type periphery guide (35,135) and periphery ring have formed described slip gear swinging gear around body (33,133) between described housing (3,103) and described driven mouth (21,121), describedly be formed at especially on the described driven mouth (21,121), and described guide (35,135) is formed on the described housing (3,103) especially around body (33,133).
9. the described gear stage of any one claim as described above, it is characterized in that, described driven mouth (21,121) is located breasting at rolling point (W) and described housing (3,103), and described rolling point (W) has formed the instantaneous of the described swing rolling movement that is used for described driven mouth (21,121).
10. as claim 5 or 9 described gear stage, it is characterized in that, when described actuator (11,111) rotates, described rolling element (31,131) is led over described rolling point (W) in described rotation direction, thereby the application force (F) that described rolling point (W) is located applies moment on described driven mouth (21,121).
11. gear stage as claimed in claim 10, it is characterized in that, in case finish its rotation, the freedom that described actuator (11,111) becomes in opposite rotation direction is so that bring described rolling element (31,131) into most probable ground near near the described rolling point (W).
12. the described gear stage of any one claim is characterized in that as described above, described actuator (11,111) is supported on the described housing (3,103) by cylindrical bearing (19,119).
13. the described gear stage of any one claim as described above, it is characterized in that the contact point between described housing (3,103), described actuator (11,111) and the described driven mouth (21,121) generally is positioned at the plane perpendicular to described axis (A, B).
14. the described gear stage of any one claim is characterized in that as described above, the described hunting motion of described driven mouth (21,121) is compensated by play or other device.
15. the described gear stage of any one claim is characterized in that as described above, and two rolling elements (31,131) are provided, a leading described rolling point (W) in described two rolling elements (31,131), and another then follows described rolling point (W).
16. gear stage as claimed in claim 15 is characterized in that, described rolling element (131) tensioning against each other.
17. the described gear stage of any one claim is characterized in that as described above, described gear stage (1,101) combines with the motor (41) of electric rectification, and is integrated into common driver unit (43) especially.
18. gear stage as claimed in claim 17 is characterized in that, stator pack 47 in described housing (3,103) breasting, and described actuator (11,111) then breasting rotor magnetic patch (45).
19., it is characterized in that generator (51,53) is used to detect the position, angle of described driven mouth (21,121) as claim 17 or 18 described gear stage.
20. the described gear stage of any one claim is characterized in that as described above, described gear stage (1,101) combines with mechanism (61), combines with the mechanism with self-locking eccentric planet train of gears (61) especially.
21. gear stage as claimed in claim 20 is characterized in that, described driven mouth (21,121) drives the actuator (69) of described mechanism (61) by main shaft (73).
22. the described gear stage of any one claim is characterized in that as described above, the lubricant that bears high surface cell pressure allows the little great friction coefficient of abrasion loss.
23. the described gear stage of any one claim as described above, it is characterized in that, at least one driver element in described housing (103), described actuator (111) and the described driven mouth (121) is made of at least one metal part (103m, 107m, 111m, 111n, 121m, 121n) and at least one plastic areas (103k, 107k, 111k, 121k) especially plastic-metal composite material.
24. gear stage as claimed in claim 23 is characterized in that, described metal part (103m, 111m, 111n, 121m, 121n) has at least approximately constant material thickness.
25., it is characterized in that described metal part (103m, 111m, 111n, 121m, 121n) is made of high duty metal thin slice especially steel thin slice as claim 23 or 24 described gear stage.
26., it is characterized in that described metal part (103m, 111m, 111n, 121m, 121n) is made and formed as any one described gear stage among the claim 23-25 under the situation without any reprocessing.
27., it is characterized in that described associated metal partly is molded into plastics especially in the highstrenghtpiston, and therefore interosculates as any one described gear stage among the claim 23-26.
28. one kind has motor (41) and as the driver element (43) of any one described gear stage (1,101) among the claim 1-27.
29. actuator (63) that has as any one described gear stage (1,101) among the claim 1-27.
30. one kind has by motor driven and has the seat of adjustable backrest and/or seat, it is characterized in that having at least one actuator as claimed in claim 29 (63).
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE200510039733 DE102005039733A1 (en) | 2005-08-23 | 2005-08-23 | Gearing stage for servo drive of vehicle seat, has drive to support another drive under parallel misalignment of axes by body and drive latter drive during rotation of eccentrics, where driven driver executes movement by tire and guide |
| DE102005039733.6 | 2005-08-23 | ||
| DE102006005906.9 | 2006-02-09 | ||
| DE102006005906A DE102006005906A1 (en) | 2005-08-23 | 2006-02-09 | gear stage |
| PCT/EP2006/008102 WO2007022909A2 (en) | 2005-08-23 | 2006-08-17 | Eccentricity gear step |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101247971A true CN101247971A (en) | 2008-08-20 |
| CN101247971B CN101247971B (en) | 2010-09-08 |
Family
ID=37715339
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200680031036XA Expired - Fee Related CN101247971B (en) | 2005-08-23 | 2006-08-17 | Eccentricity gear step |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN101247971B (en) |
| DE (1) | DE102005039733A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102498012A (en) * | 2009-09-10 | 2012-06-13 | 凯波有限责任两合公司 | Fitting For A Vehicle Seat |
| CN103517825A (en) * | 2011-05-06 | 2014-01-15 | 约翰逊控股公司 | Planetary gear arrangement for a seat adjustment mechanism and method for operating such a planetary gear arrangement |
| CN107031462A (en) * | 2015-09-22 | 2017-08-11 | 福特全球技术公司 | Ball bearing application for seat angle adjustor disk mechanism |
| CN115320459A (en) * | 2022-07-21 | 2022-11-11 | 恺博座椅机械部件有限公司 | High-strength continuous eccentric angle adjuster for seat |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007056392A1 (en) | 2007-10-23 | 2009-04-30 | Keiper Gmbh & Co. Kg | gear stage |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR601616A (en) * | 1924-11-04 | 1926-03-05 | Roller or ball speed reducer or multiplier system | |
| DD256904A1 (en) * | 1987-01-02 | 1988-05-25 | Zeiss Jena Veb Carl | CYCLE TRANSMISSION FOR TRANSMITTING A TURNING MOVEMENT |
| DE19709852C2 (en) * | 1997-03-11 | 2003-08-21 | Keiper Gmbh & Co Kg | Gear unit for adjusting seats, in particular motor vehicle seats |
| DE10144840B4 (en) * | 2001-09-06 | 2006-11-09 | Keiper Gmbh & Co.Kg | Fitting for a vehicle seat |
| DE10232247B3 (en) * | 2002-07-17 | 2004-03-04 | Bühler Motor GmbH | Eccentric gear used as a rolling eccentric gear comprises a sun wheel, a planet wheel rolling on the inner side of an external geared wheel, and an internal geared wheel |
-
2005
- 2005-08-23 DE DE200510039733 patent/DE102005039733A1/en not_active Ceased
-
2006
- 2006-08-17 CN CN200680031036XA patent/CN101247971B/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102498012A (en) * | 2009-09-10 | 2012-06-13 | 凯波有限责任两合公司 | Fitting For A Vehicle Seat |
| CN103517825A (en) * | 2011-05-06 | 2014-01-15 | 约翰逊控股公司 | Planetary gear arrangement for a seat adjustment mechanism and method for operating such a planetary gear arrangement |
| CN107031462A (en) * | 2015-09-22 | 2017-08-11 | 福特全球技术公司 | Ball bearing application for seat angle adjustor disk mechanism |
| CN107031462B (en) * | 2015-09-22 | 2021-03-23 | 福特全球技术公司 | Ball bearing application for disc mechanism of seat angle adjuster |
| CN115320459A (en) * | 2022-07-21 | 2022-11-11 | 恺博座椅机械部件有限公司 | High-strength continuous eccentric angle adjuster for seat |
| CN115320459B (en) * | 2022-07-21 | 2024-03-22 | 恺博座椅机械部件有限公司 | High-strength continuous type seat eccentric angle adjuster |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101247971B (en) | 2010-09-08 |
| DE102005039733A1 (en) | 2007-03-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4799199B2 (en) | In-wheel motor drive device | |
| CN101247971B (en) | Eccentricity gear step | |
| CN102889339B (en) | Large-size horizontal cycloidal reducer | |
| WO2010001698A1 (en) | Cycloid reduction gear, in-wheel motor drive device, and motor drive device for vehicle | |
| JP4995820B2 (en) | Gear transmission unit for vehicles | |
| US20150038285A1 (en) | Continuously variable transmission | |
| CN103718434B (en) | Driver element for the close wheel of automobile | |
| CN100342154C (en) | Eccentric planetary drive transmission | |
| JP2009506267A5 (en) | ||
| JP2013231448A (en) | One-way clutch and power generating device | |
| CN101835656A (en) | Gear stage | |
| JP5903834B2 (en) | Friction roller speed reducer and electric vehicle drive device | |
| CN109139846A (en) | Planetary spindle drive, actuator and separation system | |
| CN109532462A (en) | Bi-motor couples planet Traction Drive bearing type reduction electric hub | |
| KR20110031356A (en) | Acceleration and deceleration device | |
| JP2016161117A (en) | Cycloid speed reducer and motor drive device with cycloid speed reducer | |
| KR20230115998A (en) | Planar dense ball bearing, its manufacturing method and gearbox | |
| JP2010071462A (en) | In-wheel motor driving device | |
| EP1707528B1 (en) | Elevator hoisting machine | |
| JP2008168821A (en) | In-wheel motor drive unit | |
| JP5255370B2 (en) | In-wheel motor drive device | |
| US20180320769A1 (en) | Bearing arrangement for a stepped planetary gear, and epicyclic gearing equipped therewith for a motor vehicle drive unit | |
| KR20180087355A (en) | Continuously Variable Planetary Gear Transmission | |
| JP2008168822A (en) | In-wheel motor drive unit | |
| US11852224B2 (en) | Gear unit for an electric drive system of a motor vehicle and electric drive system with such a gear unit |
Legal Events
| 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 | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100908 Termination date: 20170817 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |