WO2002095261A2 - Kupplungs- und schaltstellglieder - Google Patents
Kupplungs- und schaltstellglieder Download PDFInfo
- Publication number
- WO2002095261A2 WO2002095261A2 PCT/DE2002/001817 DE0201817W WO02095261A2 WO 2002095261 A2 WO2002095261 A2 WO 2002095261A2 DE 0201817 W DE0201817 W DE 0201817W WO 02095261 A2 WO02095261 A2 WO 02095261A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- electric motor
- teeth
- rotation
- pinion
- actuator according
- Prior art date
Links
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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
Definitions
- the present invention relates to clutch and shift actuators, and more particularly to electric motor actuators for controlling a clutch or a gear shift mechanism of an automatic transmission system of a motor vehicle.
- Electric motor actuators used to control the clutches and gear shift mechanisms of automatic transmission systems typically use a worm and worm gear drive mechanism to reduce high gear ratios, such as disclosed in GB2325036, GB2313885 and GB2309761, the contents of which are incorporated by reference and the content of which is expressly cited in the disclosure of the present application to convert the high speed, relatively low torque electric motor drive to a relatively high, low speed torque required to actuate a clutch or gear shift mechanism.
- the drive ratios of such mechanisms are usually of the order of 50: 1 to 60: 1.
- the worm wheel drives used so far have the disadvantage that they are relatively large and cause serious difficulties with regard to the installation restrictions that exist in automatic transmission systems for motor vehicles.
- the present invention uses a high gear ratio concentric design drive to overcome the drawbacks of the worm drive previously used.
- an electric motor actuator for controlling a clutch or gear selection mechanism includes one
- Motor vehicle an electric motor, an output shaft of the electric motor and a drive mechanism comprising; a double pinion eccentrically attached to the output shaft of the electric motor for rotation relative thereto, the double pinion having a first and a second set of teeth, the number of teeth in one set being greater than the number of teeth in the other set, the first set of teeth engages the teeth of a first fixed inner gear, the second set of teeth engages the teeth of an inner gear which is secured for rotation with an output member which in turn is secured for rotation coaxial with the output shaft of the electric motor, the number of Teeth on the fixed inner gear and on the inner gear on the output member are equal to the number of teeth on the first and second set of teeth on the double pinion plus 2 ⁇ k teeth, where " ⁇ " is the eccentricity of the rotation of the double pinion and "k "is a constant that is inversely proportional to the division of the Z ithout is.
- M the number of teeth in the first set of teeth of the double pinion
- N the number of teeth in the second set of teeth of the double pinion
- n 2 ⁇ k
- M, N and n must therefore be chosen to provide the required drive ratio, which is usually from 50: 1 to 60: 1.
- the drive used in the present invention is particularly advantageous for use with switching drums such as those disclosed in GB2308874 and GB2311829, the disclosures of which are incorporated by reference and the contents of which are expressly cited in the disclosure of the present application. wherein the electric motor and the drive mechanism can be mounted coaxially within the shift drum.
- the drive mechanism described above can be used as an alternative with linear actuators, for example
- Ball and spindle actuators or rack and pinion mechanisms are examples of Ball and spindle actuators or rack and pinion mechanisms.
- Another advantage of the present invention is that the actuators can be self-locking with a minimal increase in the internal friction of the drive mechanism.
- Figure 1 schematically shows a drive mechanism used in the clutch or shift actuators according to the present invention
- Figure 2 shows a side section of a shift drum actuator according to the present invention
- Figure 3 shows a side section of a ball and spindle actuator in accordance with the present invention
- Figure 4 shows a side section of a rack and pinion actuator according to the present invention.
- Figure 5 shows a side section of an alternative double shift drum actuator according to the present invention.
- a double pinion 10 is attached to the output shaft 12 of an electric motor 14.
- the double pinion 10 is rotatably mounted on the shaft 12 eccentrically to the latter, the axis of rotation of the pinion 10 being offset from the axis of rotation of the shaft by the eccentricity ⁇ .
- the double pinion 10 defines a primary pinion 16 with N teeth and a secondary pinion 18 with M teeth.
- the primary pinion 16 engages an inner one
- An output element 22 is fastened for rotation coaxially to the output shaft 10 of the electric motor 14.
- the secondary pinion 18 meshes with an inner gear 24 on the output element 22, the inner ring gear 24 having M + n teeth.
- the drive ratio i for the previously described gear mechanism is:
- M, N and n are chosen so that a suitable transmission ratio is obtained, which is preferably of the order of 40: 1 to 60: 1, as indicated, for example, in Table 1 below.
- the transmission mechanism described above also has the advantage that friction in the transmission mechanism prevents loads applied to the output member from reversing the direction of rotation of the transmission, so that the transmission mechanism can be self-locking.
- This is particularly advantageous with clutch actuators, where the actuator, for example, must separate elements of the clutch while the clutch is disengaged against a spring load that forces the elements to engage.
- an eccentric is attached to the output shaft of the electric motor 14, the double pinion 12 being attached to the eccentric by means of a plain bearing.
- FIG. 2 shows a gear shift drum arrangement in which the drive mechanism described above is used.
- the electric motor 14 is mounted on a cylindrical housing 30, the motor 14 being fastened to an inner flange 32 which is arranged next to one end 34 of the housing 30.
- An outer flange 35 at the other end of the housing 30 is formed to be attached to a gear housing, for example.
- the fixed inner ring gear 20 is provided at the end 34 of the housing 30.
- An eccentric 36 is mounted on the output shaft 12 of the electric motor 14, the
- Double pinion 10 is rotatably mounted on the eccentric 36 by means of a roller bearing 38.
- the primary pinion 16 of the double pinion 10 engages in the inner ring gear 20, so that when the shaft 12 rotates, the double pinion 10 runs around the inner ring gear 20.
- a switching drum 40 is rotatably attached to the outer diameter of the cylindrical housing 30 by roller bearings 42.
- the end of the shift drum 40, which is removed from the flange 36 of the housing 30, is closed, the closed end of the shift drum 40 being rotatably attached to the output shaft 12 of the electric motor 14 by roller bearings 44.
- the inner ring gear 24 is provided on the shift drum 40 adjacent the closed end thereof, the inner ring gear 24 engaging the secondary pinion 18 of the double pinion 10.
- the drive ratio usually being on the order of 40: 1 to 60: 1.
- the linear actuator shown in Figure 3 can usually be used to control the movement of a piston of a hydraulic master cylinder of the type disclosed in GB2325036, GB2313885 and GB2309761, whereby a clutch slave cylinder has hydraulic pressure to control engagement and disengagement a clutch is supplied.
- linear actuators of this type can be used to control the engagement and disengagement of a clutch or to control the selection of a gear ratio via a suitable mechanical connection mechanism or cable drive.
- the double pinion 10 is rotatable on an eccentric 36, which in turn on the output shaft 12 of the
- Electric motor 14 is attached in a similar manner as described with reference to Figure 1.
- the pinion 10 is on the eccentric 36 by means of a slide bearing
- the motor 14 is attached to a concentric housing 50 which defines the 10 fixed inner ring gear 20 which in the primary pinion 16 of the
- Double pinion 10 engages.
- An annular output element 22 is rotatable by means of the
- Rolling bearings 52, 54 attached to the housing 50 and the output shaft 12 of the motor 14.
- the output element 50 defines the inner ring gear 24, which in the secondary
- End 56 of output member 22 remote from motor 14 defines the internally threaded portion of a ball screw actuator 58.
- An externally threaded portion 60 of ball screw actuator 58 is mounted coaxially with the inner member 56 in the threaded structure defined by the inner and outer members 56, 60, 0 where one Row of balls 62 is interposed.
- the outer part 60 of the ball screw actuator 58 has a plunger structure 64 which extends through an end wall 66 of the housing 50, the plunger structure 64 being axially movable to the housing 50 but being restricted in rotation with respect thereto.
- the plunger structure 64 which directly or indirectly
- a compensating spring 68 acts between the output element 22 and the
- the balance spring 68 thus works against the load exerted by the clutch spring.
- Compensating spring 68 is arranged to be compressed when the clutch is fully engaged and ball screw actuator 58 is at a limit of its movement away from the closed end of housing 50.
- the load exerted by the balancing spring 68 therefore supports the electric motor 5 when the ball screw actuator 58 is driven to release the clutch. In this way, a smaller electric motor 14 can be used than would be required without a compensation spring 68.
- Figure 4 shows a rack and pinion actuator, similar to the actuator shown in Figure 3, with output member 22 defining a pinion 70 which engages a rod 72 which extends transversely in housing 50.
- a shift drum 80 is attached coaxially to an electric motor 82, the shift drum 80 extending axially 5 from the motor flange 84, so that the gear mechanism 86 is arranged between the electric motor 82 and the shift drum 80.
- the switching drum 80 comprises a tubular element 90 with a guide track 92 which is formed in sheet metal and is adjacent to the outer circumference of the tubular element 90
- the other end 94 of the tubular member 90 has an enlarged diameter, with a radiused shoulder portion 96 being provided between the body 98 of the tubular member 90 and the enlarged diameter end 94.
- An inner ring gear 100 has an interference fit within the end 94 with the enlarged one
- a tubular housing element 102 is for screwing to the
- the tubular housing element 102 has one
- Diameter of the end 94 with the enlarged diameter of the tubular element 90 is.
- An outer flange structure 106 is provided at one end of the housing member 102 and is provided for screwing onto the motor flange 84.
- the other end 108 of the housing element 102 has a reduced diameter, an inner diameter smaller than the outer diameter of the enlarged end 94 of the tubular element 90 but larger than the outer diameter of the body portion 98 of the tubular element 90.
- the reduced diameter 108 of the housing member 102 defines a radiused shoulder 110.
- the tubular element 90 is assembled coaxially to the housing element 102, the end 94 with the larger diameter being arranged within the housing 102 and the body portion 98 and the guide track 92 extending from the end with the smaller diameter 108 of the housing element 102.
- the radiused shoulders 96 of the tubular member 90 and 108 of the housing member 102 define the inner and outer ball race rings of a ball bearing 112 which, for rotation, places the tubular member 90 radially and axially away from the end of the flange structure 106 of the housing member 102.
- An inner ring gear 114 has a press fit in the housing element 102, so that it is fixed axially and against rotation therewith.
- the adjacent outer diameter and radial surface of the inner ring gear 100 and the inner diameter and radial surface of the inner ring gear 114 form the inner and outer raceways 116, 118 for a further ball bearing 120, which radially and axially towards the end of the tubular element Arranged flange structure 106 of the housing element 102 out.
- a double pinion 122 is fixed for rotation on an eccentric 123, which is provided on the output shaft 124 of the electric motor 82, by means of a slide bearing 126.
- the pinions 128 and 130, which define the double pinion 122, are provided for engagement in the inner ring gear 100 and 114, respectively, when the housing element 102 is screwed to the motor flange 104 by means of the flange structure 106.
- the pinions 128 and 130 of the double pinion 122 have different numbers of teeth and the inner sprockets 100 and 114 each have a corresponding number of teeth, as discussed above, to provide the required gear ratio.
- the double pinion is rotatably mounted on the output shaft of the electric motor on an eccentric, the output shaft may alternatively be cranked.
- the output member of the drive mechanism can define the male screw part of the ball screw and not the female screw part.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Gear-Shifting Mechanisms (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10292233T DE10292233D2 (de) | 2001-05-23 | 2002-05-21 | Kupplungs- und Schaltstellglieder |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0112534A GB2375805A (en) | 2001-05-23 | 2001-05-23 | Electric motor actuator having an eccentric double pinion gear |
GB0112534.3 | 2001-05-23 | ||
GB0114079.7 | 2001-06-09 | ||
GB0114079A GB2376275A (en) | 2001-06-09 | 2001-06-09 | Clutch and gear actuator |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2002095261A2 true WO2002095261A2 (de) | 2002-11-28 |
WO2002095261A3 WO2002095261A3 (de) | 2003-02-06 |
Family
ID=26246109
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2002/001817 WO2002095261A2 (de) | 2001-05-23 | 2002-05-21 | Kupplungs- und schaltstellglieder |
Country Status (4)
Country | Link |
---|---|
DE (2) | DE10222339A1 (de) |
FR (1) | FR2825130B1 (de) |
IT (1) | ITMI20021110A1 (de) |
WO (1) | WO2002095261A2 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004045432A1 (de) * | 2004-09-18 | 2006-04-13 | Zf Friedrichshafen Ag | Stelleinrichtung für ein Stell- oder Schaltelement |
DE202008013633U1 (de) | 2008-10-19 | 2010-03-18 | Asturia Automotive Systems Ag | Differential-Exzentergetriebe |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2309761A (en) | 1996-01-31 | 1997-08-06 | Luk Getriebe Systeme Gmbh | An electrically-operated actuator for a motor vehicle friction clutch |
GB2313885A (en) | 1996-06-05 | 1997-12-10 | Luk Getriebe Systeme Gmbh | Powered actuator with variable spring bias |
GB2325036A (en) | 1994-02-23 | 1998-11-11 | Luk Getriebe Systeme Gmbh | An electric clutch actuating system |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1365883A (en) * | 1971-08-25 | 1974-09-04 | Maxseal Ltd | Valve actuating mechanisms |
US4014224A (en) * | 1973-10-12 | 1977-03-29 | Pitts Drive, Inc. | Speed differential planetary gear train |
DE2617951C3 (de) * | 1976-04-24 | 1979-02-08 | Kurt G. 6710 Frankenthal Fickelscher | Planetengetriebe |
DE2559577A1 (de) * | 1975-11-14 | 1977-05-26 | Kurt G Fickelscher | Getriebe |
DE3131612A1 (de) * | 1981-08-10 | 1983-02-24 | Zahnräderfabrik Renk AG, 8900 Augsburg | Getriebe zur positionierung von sonnenenergie-kollektoren |
FR2736594B1 (fr) | 1995-07-12 | 1999-12-10 | Luk Getriebe Systeme Gmbh | Dispositif d'actionnement notamment pour vehicules |
DE19713423C5 (de) | 1996-04-03 | 2015-11-26 | Schaeffler Technologies AG & Co. KG | Vorrichtung und Verfahren zur Betätigung eines Getriebes |
-
2002
- 2002-05-21 FR FR0206157A patent/FR2825130B1/fr not_active Expired - Fee Related
- 2002-05-21 DE DE10222339A patent/DE10222339A1/de not_active Withdrawn
- 2002-05-21 DE DE10292233T patent/DE10292233D2/de not_active Expired - Fee Related
- 2002-05-21 WO PCT/DE2002/001817 patent/WO2002095261A2/de not_active Application Discontinuation
- 2002-05-22 IT IT2002MI001110A patent/ITMI20021110A1/it unknown
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2325036A (en) | 1994-02-23 | 1998-11-11 | Luk Getriebe Systeme Gmbh | An electric clutch actuating system |
GB2309761A (en) | 1996-01-31 | 1997-08-06 | Luk Getriebe Systeme Gmbh | An electrically-operated actuator for a motor vehicle friction clutch |
GB2313885A (en) | 1996-06-05 | 1997-12-10 | Luk Getriebe Systeme Gmbh | Powered actuator with variable spring bias |
Also Published As
Publication number | Publication date |
---|---|
WO2002095261A3 (de) | 2003-02-06 |
DE10222339A1 (de) | 2002-11-28 |
FR2825130B1 (fr) | 2008-05-02 |
DE10292233D2 (de) | 2004-05-27 |
ITMI20021110A1 (it) | 2003-11-24 |
FR2825130A1 (fr) | 2002-11-29 |
ITMI20021110A0 (it) | 2002-05-22 |
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