WO2010025698A1 - Free-wheel arrangement for a transmission, particularly for a crank-cvt of a motor vehicle - Google Patents
Free-wheel arrangement for a transmission, particularly for a crank-cvt of a motor vehicle Download PDFInfo
- Publication number
- WO2010025698A1 WO2010025698A1 PCT/DE2009/001155 DE2009001155W WO2010025698A1 WO 2010025698 A1 WO2010025698 A1 WO 2010025698A1 DE 2009001155 W DE2009001155 W DE 2009001155W WO 2010025698 A1 WO2010025698 A1 WO 2010025698A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- inner ring
- cage
- outer ring
- clamping body
- freewheel
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
- F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
Definitions
- Freewheel arrangement for a transmission in particular for a crank CVT of a motor vehicle
- the present invention relates to a freewheel assembly for a transmission, in particular for a crank CVT of a motor vehicle.
- a continuously variable transmission which comprises a drive shaft and an output shaft, which are aligned parallel to each other in a rotatable gear housing mounted.
- the drive shaft and the output shaft are connected to each other via an eccentric of the drive shaft and arranged on the output shaft freewheel assembly and the eccentric the freewheel assembly connecting crank mechanism.
- the eccentric consists of a plurality of eccentric units, which are arranged axially next to one another on the drive shaft.
- the freewheel device consists of several freewheel units, which are arranged axially adjacent to each other on the output shaft.
- the drive shaft has a guide area offset eccentrically with respect to its axis of rotation, on the lateral surface of which an eccentric component is rotatably mounted.
- At least one connecting rod is rotatably arranged in the configuration of the continuously variable transmission as a crank CVT (Continuous Variable Transmission).
- CVT Continuous Variable Transmission
- the arranged on the output shaft freewheel units each have clamping bodies which are arranged between an inner ring formed by a portion of the output shaft and an outer ring, wherein the surfaces of the outer ring and the inner ring are coordinated with each other so that they form clamping gaps in which the clamping body in a Relativdredreichtung between inner ring and outer ring can block this rotation, so that the inner ring and the outer ring are twisted together.
- the clamping body In the other Relatiwerdusses between the outer ring and the inner ring no blocking effect is effected by the clamping body.
- the individual clamping body are acted upon in the reverse direction, which can be done by at least one spring element.
- the individual clamping bodies are positioned relative to each other via at least one cage in the circumferential direction.
- the clamping body of a freewheel unit are pressed with a force in the nip, which corresponds to 10 to 50 times the weight of the clamp body.
- This spring force presses the clamp body permanently against the outer ring and generates there friction losses during overtaking.
- the frictional force generated in this case is necessary because at the moment of overtaking it is the only force that pulls the clamping body into the clamping gaps.
- As a clamping body clamping rollers are preferably used.
- the outer ring undergoes, at the moment of gripping, a crank mechanism which is mentioned in the introduction, which is e.g. formed by connecting rods, pronounced acceleration.
- a crank mechanism which is mentioned in the introduction, which is e.g. formed by connecting rods, pronounced acceleration.
- the highest possible force must prevail, so that the slip time and thus the time delay until the pinch rollers grip correctly, as short as possible. It follows that depending on the acceleration of the outer ring when gripping a force must be applied, which corresponds to about 10 to 50 times the weight of the clamp body.
- the object of the present invention is to provide a freewheel assembly in which the slip time and thus the time delay to the correct or effective gripping of the clamping body in the clamping gaps between the outer ring and inner ring is as short as possible even with a relatively small exertion of force on the clamping body.
- a freewheel assembly in particular for use in conjunction with a crank-CVT, with an inner ring, an outer ring and an arranged between the outer ring and the inner ring annular cage in the clamp body are held (main freewheel), wherein the clamping body at a Relatiwerpitung of the outer ring with respect to the inner ring in the one direction in each case in a formed between the inner ring and the outer ring clamping gap movable and in a relative movement of the outer ring with respect to the inner ring in the other direction out of the nip out are movable.
- the clamping body movable in a relative movement between the outer ring and the inner ring in one direction into a formed between the cage and the outer ring further clamping gap and movable in a relative movement between the outer ring and the inner ring in the other direction the further clamping gap are movable out.
- the other clamping bodies of the forward freewheel are each biased by an energy storage in the direction of the further nip.
- the other clamp body have a smaller weight than the clamp body.
- the essential advantage of the present invention is that the actual freewheel, which is formed by the clamping body in the clamping gaps between the outer ring and the inner ring, a Vorschaltkelauf is connected upstream, which has the sole purpose of generating the acceleration force for the clamping body of the main freewheel ,
- This Vorschaltkelauf is formed by relatively small clamping body between the cage and the outer ring.
- the Vorschaltkelauf can be smaller in its torque capacity many times, than the freewheel.
- the same rules mentioned above apply to the reverse freewheel with the 10 to 50 times the weight, but this is much smaller than that of the main freewheel corresponding to the smaller mass of the sprags of the forward freewheel. Therefore, the losses correspond to only a fraction of a known normal freewheel without Vorschaltkelauf.
- the energy storage in the form of a compression spring in the form of a compression spring, one side of which are supported on the clamping body of the Vorschaltfrevieres and the other side of the cage.
- the other side of the compression spring is structurally particularly advantageous arranged in a blind bore of the cage.
- the blind bore can be arranged in a projecting into the space between the outer ring and the cage portion of the cage. The cage and the portion can therefore be made in one piece.
- the cage can be cushioned by a further, damping energy storage relative to the inner ring.
- the further energy storage advantageously has the form of a further compression spring, one side of which is supported on the cage and the other side on the inner ring.
- one side of the further compression spring is supported in a blind bore of the inner ring and the other side of the further compression spring in a blind bore of the cage.
- the blind bore of the cage may be located in a portion of the cage that extends into the space between the cage and the inner ring. This portion of the cage may be formed integrally with the cage.
- the blind bore of the inner ring can be arranged in a portion of the inner ring, extending into the room - A - between the cage and the inner ring hineinerstreckt. This portion of the inner ring may be formed integrally with the inner ring.
- the clamping body of the main freewheel and / or the clamping body of the Vorschaltkelauf the form of pinch rollers.
- the ratio between the number of clamp bodies of the main freewheel and the number of clamp bodies of the freewheeling freewheel can, depending on the requirements, be chosen as desired.
- the dimensions of the clamping body of the main freewheel and the clamping body of the freewheel clutch be different.
- the clamping body of the main freewheel preferably have a larger diameter than the clamping body of the Vorschaltkelaufes.
- FIG. 2 is an enlarged sectional view of a portion of the freewheel assembly of FIG. 1.
- the present freewheel assembly 1 comprises in a conventional manner substantially an outer ring 2, a preferably formed as an inner star inner ring 3, a cage 4, which is annular and distributed over its circumference uniformly spaced from each other clamp body holds.
- these clamping bodies are designed as pinch rollers 5.
- the outer ring 2 may also comprise, in a manner known per se, a bore 6 which, in use of the present freewheel assembly in conjunction with a crank CVT, rotatably connects to one end of a connecting rod (not shown).
- the clamping bodies 5 arranged in clamping gaps 14 between the outer ring 2 and the inner ring 3 are held in an annular cage 4.
- the clamping bodies 5 together with the outer ring 2 and the inner ring 3 form a following Genden referred to as main freewheel freewheel, which corresponds to the normal freewheel known freewheel arrangements.
- additional clamping rollers 10 are arranged in additional clamping gaps 13 between the cage 4 and the outer ring 2, which, according to the present invention, form a further freewheel, which is referred to below as a preloading freewheel.
- the pinch rollers 10 of the indexing freewheel which are considerably smaller and therefore lighter than the clamping body 5 of the main freewheel, are each acted upon by a compression spring 11 and biased into the nip 13 inside.
- the compression spring 11 is preferably contained in a recess or blind bore 12 of the cage 4, such that its one side is supported on the bottom of the blind bore 12, whereas its other side is supported on the clamping roller 10.
- the blind bore 12 is preferably arranged in a portion 15 of the cage 4, which extends into the space between the outer ring and the cage 4 inside.
- a clamping body 10 clamping rollers are preferably also provided.
- the overrunning freewheel initially engages when overtaking, whereby the clamping bodies 10 acted upon by the compression spring 11 are pressed into the clamping gaps 13 with the small mass and abut permanently against the inner surface of the outer ring 2.
- the cage 4 follows in the blocking direction of the rotation of the outer ring 2 and subsequently the clamping body 5 of the main freewheel are introduced into the clamping gaps 14, so that the inner ring 3 follows the rotation of the outer ring 2.
- the pinch rollers 5 of the freewheel can during the overtaking the outer ring 2 with a small force, for. B. the simple weight or even have game.
- the overall efficiency can be significantly improved by the forward freewheeling arrangement of the invention, because the overhaul losses of the freewheel assembly of crank gears are the main losses of the transmission.
- the cage 4 with respect to the inner ring 3 in the circumferential direction such that a damping between the cage 4 and the inner ring 3 is effected.
- a compression spring 7 which is supported on the one hand on the cage 4 and on the other hand on the inner ring 3.
- the ends of the compression spring 7 in blind holes 8 and 9 of the cage 4 and the inner ring 3 are arranged.
- the blind bore 9 of the inner ring 3 is preferably located in a nem portion 16 of the inner ring 3, which extends in the space between the cage 4 and the inner ring 3 inside.
- the blind bore 8 is located in a portion 17 of the cage 4, which extends the space between the cage 4 and the inner ring 3 inside.
- the force is only a fraction, for example one-tenth of the usual Anfederungskraft. Clamping angle differences between the main freewheel and the reverse freewheel can be compensated by the radial compliance of the cage 4 at the contact point of the clamping body of the freewheel clutch.
- clamping body 5 and the other clamping body 10 for better tolerance compensation in separate cages, which are arranged concentrically next to each other.
- the ratio between the number of clamping body 5 and the other clamping body 10 can be chosen arbitrarily.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011525400A JP5730202B2 (en) | 2008-09-04 | 2009-08-13 | Transmission device, in particular a freewheel device for a crank CVT of an automobile |
DE112009002173T DE112009002173A5 (en) | 2008-09-04 | 2009-08-13 | Freewheel arrangement for a transmission, in particular for a crank CVT of a motor vehicle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008045907.0 | 2008-09-04 | ||
DE102008045907 | 2008-09-04 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010025698A1 true WO2010025698A1 (en) | 2010-03-11 |
Family
ID=41404074
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2009/001155 WO2010025698A1 (en) | 2008-09-04 | 2009-08-13 | Free-wheel arrangement for a transmission, particularly for a crank-cvt of a motor vehicle |
Country Status (3)
Country | Link |
---|---|
JP (1) | JP5730202B2 (en) |
DE (2) | DE102009037480A1 (en) |
WO (1) | WO2010025698A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010052922A1 (en) | 2010-11-30 | 2012-05-31 | Schaeffler Technologies Gmbh & Co. Kg | Roller freewheel used for crank continuous variable transmission for drive train of motor vehicle, has pinch rollers that are rotationally fixed to cage and biased relative to clamping ramps in circumferential direction |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE382481C (en) * | 1922-06-08 | 1923-10-03 | Det Tekniske Forsoegsaktiesels | Device for locking a ball or roller bearing |
FR813779A (en) * | 1935-11-21 | 1937-06-08 | Improvements made to devices for driving two organs one by the other, in particular those of the freewheel type | |
DE1110477B (en) * | 1959-05-05 | 1961-07-06 | Stieber & Nebelmeier Fa | Overrunning clutch with clamping rollers in a cage |
FR2102631A5 (en) * | 1970-08-12 | 1972-04-07 | Alsthom Cgee | |
JPH04131527A (en) * | 1990-06-29 | 1992-05-06 | Ntn Corp | Torque limiter |
US5931271A (en) * | 1997-09-19 | 1999-08-03 | General Motors Corporation | Hybrid drive with one-way drive connections |
WO2008089004A1 (en) * | 2007-01-15 | 2008-07-24 | The Timken Company | Releaseable one-way clutch |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003027538A1 (en) | 2001-09-26 | 2003-04-03 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Transmission |
JP2003232386A (en) * | 2002-02-06 | 2003-08-22 | Koyo Seiko Co Ltd | One-way clutch and pulley device |
-
2009
- 2009-08-13 DE DE102009037480A patent/DE102009037480A1/en not_active Withdrawn
- 2009-08-13 WO PCT/DE2009/001155 patent/WO2010025698A1/en active Application Filing
- 2009-08-13 JP JP2011525400A patent/JP5730202B2/en not_active Expired - Fee Related
- 2009-08-13 DE DE112009002173T patent/DE112009002173A5/en not_active Withdrawn
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE382481C (en) * | 1922-06-08 | 1923-10-03 | Det Tekniske Forsoegsaktiesels | Device for locking a ball or roller bearing |
FR813779A (en) * | 1935-11-21 | 1937-06-08 | Improvements made to devices for driving two organs one by the other, in particular those of the freewheel type | |
DE1110477B (en) * | 1959-05-05 | 1961-07-06 | Stieber & Nebelmeier Fa | Overrunning clutch with clamping rollers in a cage |
FR2102631A5 (en) * | 1970-08-12 | 1972-04-07 | Alsthom Cgee | |
JPH04131527A (en) * | 1990-06-29 | 1992-05-06 | Ntn Corp | Torque limiter |
US5931271A (en) * | 1997-09-19 | 1999-08-03 | General Motors Corporation | Hybrid drive with one-way drive connections |
WO2008089004A1 (en) * | 2007-01-15 | 2008-07-24 | The Timken Company | Releaseable one-way clutch |
Also Published As
Publication number | Publication date |
---|---|
JP2012502228A (en) | 2012-01-26 |
DE112009002173A5 (en) | 2011-06-16 |
JP5730202B2 (en) | 2015-06-03 |
DE102009037480A1 (en) | 2010-03-11 |
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