WO2010009935A1

WO2010009935A1 - Free-wheeling unit and adjusting unit, and crank mechanism comprising said free-wheeling unit and adjusting unit

Info

Publication number: WO2010009935A1
Application number: PCT/EP2009/056960
Authority: WO
Inventors: Norbert Radinger; Tomas Smetana; Philip Wurzberger
Original assignee: Schaeffler Kg
Priority date: 2008-07-21
Filing date: 2009-06-05
Publication date: 2010-01-28

Abstract

The invention relates to a free-wheeling unit (1) comprising at least one free-wheeling star wheel (3), a free-wheeling ring (2) and clamping bodies (4) between the free-wheeling star wheel and the free-wheeling ring (2), and a cage (5) in which the clamping bodies (4) are guided. The free-wheeling unit is characterized in that the clamping bodies (4) can be impinged by a change-over mechanism to change the free-wheeling unit (1).

Description

Name of the invention

Freewheel unit and adjustment unit and crank mechanism with the freewheel unit and adjustment unit

description

Field of the invention

The invention relates to a freewheel unit and an adjusting unit for the freewheel unit and a crank mechanism with the freewheel unit and adjusting unit.

Background of the invention

Such freewheel units are suitable for various applications, in particular for applications of automotive technology, which provide one-way blocking or reversible freewheels. They are preferably used in transmissions but also in hybrid drives.

DE 102 43 535 A1 shows a drive unit comprising a crank mechanism and a hybrid drive, in which several freewheels of the type are installed. The drive unit is formed by an internal combustion engine, an electric machine and a transmission. The crank gear has a driving shaft, which is usually the transmission input shaft. Furthermore, the transmission has a driven shaft (also referred to as the output shaft), which is usually a transmission output shaft. The two shafts are aligned parallel to each other and rotatably mounted in a transmission housing. In addition, the shafts are geared together. The geared connection is characterized by at least one eccentric drive on the drive shaft and at least one freewheel unit on the driven shaft and a connecting rod-like connection between the eccentric drive and the freewheel unit made. The contemplated embodiment of the eccentric drive has a plurality of juxtaposed on the drive shaft eccentric units, of which one is connected to a freewheel device. Therefore, the freewheel device has a plurality of freewheel units arranged side by side on the driven shaft.

The rotatably mounted output shaft is externally provided with a polygonal profile. On this polygon profile sit the freewheel units. The respective free-running units have clamping bodies, which are designed as rollers, for example. The polygonal profile is formed on an inner ring which sits on the output shaft. The clamp bodies sit between the inner ring and an outer ring. A relative rotation between inner and outer ring in a direction of rotation can be blocked with the clamping bodies. In the other direction of rotation is achieved in one-way freewheels no blocking effect. The clamping bodies are acted upon by spring elements in the reverse direction and are guided in a cage.

The drive shaft is driven by the internal combustion engine and / or by an electric machine. The electric machine can be designed as a motor and / or generator. Alternatively, the engine designed as a prime mover can also serve as a starter for the internal combustion engine. The electric machine is arranged, for example, coaxially with the transmission input shaft. The connection of the electric machine to the transmission input shaft is realized via couplings. The clutches can be designed as generic freewheels, which possibly also enable a temporary decoupling of the electric machine from the internal combustion engine. In other words, in certain operating conditions, the internal combustion engine can be shut down even while driving the motor vehicle. The electric machine is then a hybrid drive.

In the transmission described in DE 102 43 535 A1 exists between the electric machine and both the transmission input shaft and the Output shaft a geared connection. Both gear connections are each provided with at least one freewheel. In the case that the electric machine works as a generator, engages the geared connection between the driven shaft and the rotor. The corresponding freewheel in the geared connection between the rotor and the output shaft is locked. In the case, the rotor is driven electric machine at a speed which is at least equal to or greater than the rotational speed of the internal combustion engine. Another freewheel is in geared connection to the transmission input shaft and secures the free running separation of the connection between the rotor and the transmission input shaft, ie in this case no direct drive between the transmission input shaft and the rotor is connected.

When the electric machine is operated as a drive motor or starter, the freewheel interrupts the geared connection to the output shaft. The freewheels also lock when the electric machine and internal combustion engine are driving at the same time and in overrun mode, for example when the electric machine and the internal combustion engine act as a brake.

It is conceivable that these freewheels are switchable with respect to the lockable or non-lockable relative rotational direction of the outer ring against the inner ring. By using such switchable freewheel units can be changed in the transmission, the direction of rotation of the output shaft and, for example, a reverse gear can be realized. Such switchable freewheels are switchable in three positions. In a neutral position, the relative rotation between the inner and outer ring is possible. In a first blocking position, the two rings are locked by means of the clamping body and formed on at least one of the rings ramps or otherwise designed blocking surfaces in a first rotational direction against each other against relative movement. In a second locking position, the rings are blocked in the opposite direction of rotation in the same way. A freewheel device has an outer ring and a freewheel star, clamping body, a cage and damping elements arranged concentrically to the outer ring. There are also applications in which the outer ring is a freewheel star. The freewheel star can be formed on the input or output shaft directly or on a separate part, for example as an inner or outer star.

DE 10 2005 048 611A1 describes such a freewheel device of the type in more detail. This freewheel star is designed as the polygon profile. This polygonal profile has a plurality of pairs of flanks of opposing blocking surfaces. Between the outer ring and the freewheel star several roles are arranged as a clamping body. Each roller is arranged between a pair of the aforementioned flanks (blocking surfaces). The freewheel device also has a spring per clamping body as a clamping element. The clamping body is pressed by means of the spring in a gap between the freewheel star and the outer ring. In this position, the clamping body are held as clamping elements in contact with the outer ring and freewheel star.

The clamp bodies are held in a cage. The cage has side windows and bars. The cage has on one side a radially extending side window with radially outwardly of the side plate axially angled webs. A through hole of the side window is provided with an inner profile which corresponds to the polygonal profile, so that the side window is arranged rotationally fixed on the freewheel star. The webs are arranged on the outside of the running surface of the outer ring and center the outer ring. Each web is circumferentially arranged in each case between two of the clamping body.

The side window with webs is provided with holes for storage of switching mechanisms of an adjustment. Each switching mechanism is formed by a profiled bar, a double leg spring and a washer per circumferential gap between the clamping bodies. The profile bar is mounted in the disc and the disc is rotatably disposed in the side window. The double leg spring is in a receptacle of the profile bar on orderly. When switching the disk is rotated about its axes of rotation and thus offset the profiled rod with the spring in a pivoting movement. In the process, a limb of the double limb spring, which is prestressed in one direction against a clamping body, releases from the clamp body. The other leg biases in the opposite direction against that clamping body which is opposite to the circumferential gap. A clamping body is thus freed by the pivoting movement of its clamping contact to the outer ring and the locking surface on the freewheel star and the other clamping body is biased in the opposite direction in the gap between the outer ring and locking surface, so that the reverse direction is switched. In addition, the switching mechanism can be switched to the neutral position in which none of the legs of the double leg spring is in contact with the clamping bodies.

Since several freewheels are arranged axially next to each other, the rods can reach axially through all freewheels and thus all freewheel units are switched simultaneously.

Another side window, whose inner profile of a through hole also corresponds to the polygonal profile, closes the cage down to the other side, so that the rollers (clamping bodies) are held axially between the discs.

An adjustment unit is described in DE 10 2005 0 48 611 A1. The adjustment unit is provided for adjusting or switching over a plurality of axially arranged one behind the other freewheel units of a crank mechanism. The freewheel units are seated on the output shaft of the crank gear and are bordered by connecting rod connecting rods similar connecting elements between the input and output shaft.

However, such an adjustment can also be used for a single reversible freewheel or for several in a freewheel device axially behind one another arranged freewheels. Object of the invention

The object of the invention is to provide a simple, inexpensive to produce freewheel unit that works safely even at high switching frequencies.

The requirements for a freewheel unit and its adjustment unit are robustness and low costs for their production. In addition, to switch over the freewheels, the power flow between the output shaft and the differential must be disconnected. Only then can the freewheels be switched over. There are three operating states: forward, reverse and neutral. The clutch switches to zero at a differential speed. Regardless of the actual function, the clutch is also used as an overload clutch.

A further object of the invention is therefore to provide an adjusting unit for the freewheel unit according to the invention, with which any switching mechanism or coupling mechanism can be actuated. This adjustment unit should be robust and inexpensive to produce.

Description of the invention

The object is solved according to the subject of claim 1.

The freewheel unit according to the invention has at least one freewheel ring and at least one freewheel star, clamping body between the freewheel ring and the freewheel star and at least the directly switchable cage. The freewheel ring is either an inner ring, a shaft or an outer ring. The freewheel star is either integrated in an outer ring or is preferably an inner star. The freewheel star has a plurality of pairs of flanks of opposing blocking surfaces. Between the freewheel ring and the freewheel star at least one row circumferentially spaced from each other clamp body is arranged. The invention also applies to freewheel units in which at least two rows of clamping bodies are arranged. Clamping bodies are preferably rollers, but also balls or other suitable body.

Each clamping body is arranged between a pair of the aforementioned flanks (blocking surfaces). The freewheel device also has at least one clamping element per clamping body. The clamping body is pressed by means of the clamping element in a gap between the freewheel star and the outer ring, so that the clamping body are clamped in this position between freewheel ring and freewheel star. When switching the cage around the center axis of the freewheel device is pivoted against the clamped or in neutral position clamping body. The clamp bodies are either taken into the neutral position or moved against the opposite ramp (blocking surface) and thus clamped there again.

The clamp bodies are held circumferentially by means of the cage at a distance. The clamping elements are preferably supported on the cage. Alternatively, the clamping elements are supported on suitable structures of the freewheel star. The tensioning element is for example a spring of any suitable shape.

Preferably, the clamping element has a U-shaped base body. The distance between the legs of the U-profile is slightly narrower than the tangential or circumferential dimension of the web at the point at which the clamping element sits. Alternatively, the distance between the legs at at least one point between the legs is so narrowed that the body can be clamped onto the web and / or engages behind corresponding undercuts on the cage.

From the legs of the main body protrudes outward from the actual spring element, which, for example, by two spread apart spring Donate! is formed. The spring legs of a page are at least then biased against the respective clamping body when the clamping body is clamped on this same side in the blocking position between the freewheel star and the freewheel ring. If the cage is moved when switching the freewheel against the clamping body, the spring element is first compressed so far until the spring element terminates with the web or is biased between the clamping body and cage to block. Then the web meets the clamp body or on the block and moves the clamp body.

It may be disadvantageous under certain circumstances that the spring elements are compressed in a block. Therefore, at least one protruding in the direction of the respective clamping body stop are formed either on the main body of the clamping element or on the web. The base of the spring element, from which it leaves the base body, is set back in the direction away from the respective clamping body from the respective stop. The base is set back against the stop so far that the respective compressed at the level of the stop spring element between stop and base is not yet on block. The cage is preferably pivoted with the adjustment unit according to the invention described below.

The adjustment unit (the actuator) is alternatively single-sided or double-acting and therefore has at least one or two functions. On the one hand, a pivoting movement is generated, for example, the cage of the freewheel switched. On the other hand, an axial stroke is generated and, for example, a clutch is actuated via the end face of the adjusting unit. The biasing unit gives at least one mechanical impulse with which the clutch is disengaged.

Regardless, the adjustment unit has a cup-shaped housing. In or on the housing at least one backdrop is formed. A backdrop is formed at least from a first guideway. For example, the first guideway is continuous in the sheath of the sheet metal th housing introduced. Furthermore, the adjustment is provided with a sliding sleeve.

The sliding sleeve is axially, ie rectified with the central axis of the Ab- drive shaft, slidably mounted on a peripheral toothing of a base plate of the adjustment. The peripheral toothing is fixed to the base plate. Accordingly, the sliding sleeve is indeed axially displaceable in the direction of the central shaft of the adjusting but rotationally fixed in the circumferential direction to the base plate. On the sliding sleeve, a guide sleeve is mounted at least pivotably about the central axis of the adjustment. For example, a slide bearing serves to support the guide sleeve on the sliding sleeve. The base plate is, for example, sleeve-shaped, engages around the pin of a shaft and sits on this fixed or rotatable or displaceable.

At least one first guide pin projects radially out of the guide sleeve. The first guide pin is either formed integrally with the guide sleeve made of sheet metal or attached thereto. The first guide pin engages radially into the housing formed on the first guideway (backdrop). The first guide track is aligned at a first guide section substantially in the circumferential direction about the central axis of the output shaft, however, deflects obliquely at least at a second guide section, extending simultaneously in the axial direction and the circumferential direction. The second guide section then again adjoins a third guide section aligned in the circumferential direction.

The housing is axially fixed by means of at least one rolling bearing but rotatably supported radially about the central axis of the adjusting unit on the base plate. In addition, the housing can be driven to pivot at least about the central axis with a suitable geared engagement device. The attack device is, for example, an outer toothing for the toothed engagement with a drive toothing. Alternatively, the engagement device may also be a seat for a belt, a chain or any other driving element. The housing is pot-shaped and formed from sheet metal. The bottom of the pot is perforated. Through the bottom of the pot grip the base plate and a pin of the output shaft. The lateral surface of the pot is stepped with respect to the diameter. On a hollow cylindrical portion with a small diameter of the bearing seat is formed for the outer ring of the rolling bearing, with which the pot is mounted on the base plate.

In a hollow cylindrical section with a larger diameter, the first guideway is introduced. The larger diameter section is followed by an edge of the pot, so that the case resembles a hat with brim. At the edge of the brim outside the outer toothing is formed.

Inside the hollow cylindrical portion with the larger diameter, the peripheral teeth, the sliding sleeve and the guide sleeve are arranged. The sliding sleeve sits concentrically on the peripheral teeth and the guide sleeve concentrically on the sliding sleeve. The first guide pin is at least partially radially into the first guide track.

At least one guide element, which engages in a second guideway of an adjustable machine part, is fastened to the sliding sleeve. The second guide track is independent of the first guide track on the machine part and therefore not formed on the housing. The machine part is pivotally actuated by means of the guide element about the central axis of the output shaft. For this purpose, the guide element engages radially in the second guideway of the machine part. The second guide track on the machine part runs at a first guide track section substantially axially rectified with the central axis of the adjustment unit, but deflects at a second guide track section in the axial direction and obliquely in the circumferential direction. In the second guideway section, a third guideway section then connects, which again runs rectified axially with the central axis. In the adjustment further a locking device is arranged. The locking device has at least one spring-loaded locking element, which is biased in a radial direction against the sliding sleeve. For this purpose, the locking element is supported in the other radial direction on the base plate. The sliding sleeve has per locking at least one first detent recess in which the locking element is locked at least in an initial position of the sliding sleeve. In this position, the sliding sleeve is held by the bias of at least one spring on the locking element and can be moved accordingly only against the resistance of the spring from this position. In the initial position, the sliding sleeve sits on the peripheral teeth in a position from which the sliding sleeve must be moved axially to pivot the machine parts on the peripheral teeth. The initial position corresponds, for example, to the operating state forward drive into the crank gear.

For adjusting the machine part, that is to say, for example, for pivoting the machine part about a center axis common to the adjusting unit, the housing is driven via the engagement device and pivots about the central axis in a first circumferential direction. The first guide track moves relative to the guide sleeve in the circumferential direction about the central axis. In this case, the first guide pin passes through the first guide track without being axially loaded because it moves in the first guide section aligned only in the circumferential direction.

As soon as the second guide section of the first guide track obliquely deflecting from the circumferential direction in the axial direction strikes the first guide pin, an axial force is exerted on the first guide pin, via which the guide sleeve is carried along axially, ie in the same direction as the center axis. About the guide sleeve, the sliding sleeve is moved from the initial position and moved axially on the peripheral teeth. In this case, the latching element springs in and out of the first latching recess and releases the sliding sleeve. The maximum axial travel around the guide sleeve can be shifted is determined by the proportion of the axial deflection of the circumferential direction of the inclined second guide portion. After the first guide pin has passed through the second guide section, the guide track moves with the third guide section relative to the first guide pin. Since the third guide section is again aligned in the circumferential direction, the axial adjustment is movement of the guide sleeve and thus the sliding sleeve is completed and this, although the housing is still pivotable over the entire length of the third guide portion in the first circumferential direction.

The spring-biased locking element is also suitable in cooperation with one or more ramps on the sliding sleeve to generate targeted adjustment forces. In this case, the sliding sleeve must be moved against the spring force of the respective ramp on or descending locking element. The adjusting force increases or decreases depending on the increase in the ramp.

With the sliding sleeve, the guide element moves in the axial direction. The guide element is for example a second guide pin which engages in the second guide track on the machine parts. The second guide pin passes through the second guide track without exerting an adjusting force on the guide track until the second guide pin strikes from an axially extending first guide track section of the guide track to the second guide track section of the second guide track which is obliquely deflected in the circumferential direction. When the second guide pin passes through the obliquely extending second guide track section, a force directed in the circumferential direction or in the tangential direction is exerted on the machine element, so that the machine element is pivoted about the central axis. The machine element can be pivoted maximally by the amount by which the obliquely extending second guide track section is deflected overall in the circumferential direction.

In this position, the sliding sleeve z. B. by the bias of the spring on the locking element and by locking the locking element in one held axially to the first detent recess second detent recess in a second operating state until the housing is driven via the engagement device in a direction opposite to the first circumferential direction second circumferential direction and pivoted about the central axis at least until the first guide pin back to the second guide section the first guideway meets in the housing and the sliding sleeve is thereby moved back to the starting position. The second operating state is in the crank gear, for example, the reverse drive.

It is still provided a third position of the sliding sleeve, which corresponds to a neutral position and which is therefore carried out on the way between the starting position and switched position on the sliding sleeve.

As mentioned earlier, the adjustment unit is double-acting. It has already been mentioned that to switch the freewheels the power flow between the output shaft and the differential must be separated. Only then can the freewheels be switched over. For this purpose, the housing has circumferentially on the non-perforated part of the bottom a ramp contour, which is formed from at least one but preferably from three axially rising from the ground and falling again ramps. At the bottom are on an imaginary circular circumferential path, which extends over the ramps, at least one but preferably three Axialverstellelemente. The Axialverstellelemente are actuated by axial stroke. The axial stroke is applied to the Axialverstellelemente over the ramp contour as described below.

When the housing for adjusting the machine part is driven by the engagement device and thereby pivots, the ramp contour moves relative to the Axialverstellelement along the Axialverstellelement. The axial adjustment element rises on a ramp and thus alters its position axially, that is, it generates a stroke with which, for example, a clutch can be disconnected. This clutch is, for example, a multi-plate clutch between the output shaft of the crank gear and a differential. These Movement is independent of the movement of the guide pin in the first guide track, since the axial stroke is generated exclusively by the axially increasing ramp contour of the axially immovably mounted housing. However, the beginning of this movement is oriented so that the stroke, that is, the separation of the clutch, as long as and only carried out when the first guide pin passes through the first guide portion. In this operating state, the sliding sleeve is not yet operated axially and thus the freewheel not yet switched.

When the first guide pin enters the second guide section, the disengagement of the clutch must be completed, then the pivoting of the machine element begins. Therefore, the ramp contour does not increase axially, but remains constant over a circumferential arc portion corresponding to the pivoting path of the first guide pin in the second guide portion, and moves with respect to the now not axial- stroke movable Axialverstellelement.

When the pivoting of the machine part is completed, i. when the first guide pin has left the second guide portion, the pivoting of the machine part is completed and the clutch must be engaged again. The first guide pin enters the third guide section of the first guide track. The housing is further rotated in the first circumferential direction without the adjustment movement influencing the position of the machine part. With the course of the third guide portion corresponds to a sloping towards the bottom ramp contour on which the Axialverstellelement moves back around the stroke back axially and thus the clutch is engaged again.

In the freewheel unit, various elements are integrated to prevent the consequences of sudden switching. In the example described above, switching at high speeds releases much kinetic energy. In addition, it is also effective to dampen when the clamp body slip due to unfavorable kinematic conditions. In the case where a cage described above is arranged in the freewheel, an embodiment of the invention provides that a damping element is arranged and supported separately from the cage. Irrespective of this, an embodiment of the invention provides that the damping element is formed at least temporarily by at least one damping element acted upon by the clamping body, which is arranged in a limited and relatively movable manner between the clamping bodies and a contact surface of the freewheel star, preferably the inner star. In this case, at least one damping element is provided either axially or radially between the respective clamping body and a contact surface of the freewheel star or the shaft. With an embodiment, it is provided that the damping element is resilient.

Regardless, it is provided with an embodiment of the invention that the clamping body are arranged in a separate cage to the cage, and wherein the damping cage with at least damping element is engaged, wherein the damping element between the damping cage and the surrounding structure is resiliently clamped.

The damping cage and the damping element are positively engaged, alternatively frictionally engaged or via a mixed form of positive and frictional engagement with each other. The damping element is positively and / or frictionally engaged in one direction with the damping cage and is elastically biased directly or indirectly supported on the contact surface in the direction axially of the damping element pioneering direction. The damping element is supported directly or indirectly on the surrounding structure, for example on a radially at least axially connected to the freewheel star radial disc section from. Direct to the surrounding construction means, for example, that there is frictional engagement between the damping element and the surrounding construction. Indirectly means that between the damping element and surrounding structure, for example, discs and / or spring elements are arranged, with which the damping element is in the form and / or frictional connection and but at least pass on part of the energy to the surrounding construction. The disc section can also be used separately formed the freewheel star and be held at least axially thereto. Alternatively, the damping element is supported on a shaft shoulder or on the damping element of an adjacent freewheel unit. If the damping element is supported on an adjacent freewheeling element, it is possible that the damping element with the adjacent freewheeling element, preferably also with a damping element form and or frictionally engaged.

A further embodiment of the invention provides that the damping element has elastically yielding ramps which are supported on the surrounding structure separately from the damping cage. The ramps all rise in the same direction with an increase preferably over the circumferential direction and thereby in a circumferentially directed locking direction of the freewheel. The ramps may increase in the radial direction over a circumferential line or preferably in the axial direction.

In reversible freewheel devices, the two directions ramps are formed so that when switching from one locking direction to the other or from the neutral position is selectively damped in any reverse direction of the impact of the clamping body.

Advantages of the invention:

- robust construction - simple construction

- cost-effective production

- Increasing the life of the freewheel

- noise reduction Description of the drawings

Figure 1 - Figure 1 shows a freewheel device 34 on an output shaft 14 of a crank mechanism otherwise not shown. The freewheel device 34 is formed from a plurality of freewheel units 1. The picture shows a total of six pieces of the freewheel units 1. The respective freewheel star 3 of each freewheel unit 1 is formed directly on the output shaft 14. The respective freewheel ring 2 is in each case an outer ring 15. The individual clamping bodies 4 of the freewheel units 1 are guided in a common cage 5. The cage 5 of the freewheel device 34 is coupled to the adjustment unit 35. The adjusting unit 35 connects axially to an unspecified coupling 36.

2, 3, 4 and 5 - Figure 2 shows the adjustment unit 35 in a longitudinal section along the central axis 37 of the output shaft 14. Figure 3 shows an overall view of the adjustment unit 35 and its connection to the cage 5. Figure 4 also shows an overall view the adjusting unit 35, but from the other side.

The adjusting unit 35 has a cup-shaped housing 38. In or on the housing 38 at least one gate is formed. The backdrop is formed at least from a first guide track 39.

FIG. 2 - The adjusting unit 35 is provided with a sliding sleeve 40. The sliding sleeve 40 is axially, ie rectified with the central axis 37 of the output shaft 14, slidably mounted on a peripheral teeth 41 of a base plate 42 of the adjustment. The peripheral teeth 41 is fixed to the base plate 42. On the sliding sleeve 40 is seated a guide sleeve 43. The guide sleeve 43 is at least pivotally mounted around the central axis 37 of the adjusting unit 35. To the central axis 37 circumferentially pivotable mounting of the guide sleeve 43 on the sliding sleeve 40 is a sliding bearing 45. The base plate 42 is, for example, sleeve-shaped, surrounds the pin 52 of the output shaft 14 and sits on this fixed or rotatable or displaceable. From the guide sleeve 43 is radially a first guide pin 44 protrudes. The first guide pin 44 is formed integrally with the guide sleeve 43 made of sheet metal and engages radially in the formed on the housing 38 first guide track 39 (backdrop).

The housing 38 is axially fixed by means of at least one rolling bearing 49 but mounted radially on the base plate 42 so as to be rotatable about the central axis 37 of the adjusting unit 35. In addition, the housing 38 can be driven in a pivotable manner at least about the center axis 37 with a suitable geared engagement device. The engagement device is an outer toothing 50 for the toothed engagement of a drive, not shown.

Figures 3, 4 and 5 - The first guide track 39 is aligned at a first guide portion 46 substantially in the circumferential direction about the central axis 37 of the output shaft 14, but deflects at least at a second guide portion 47 obliquely, in the axial direction and circumferential direction simultaneously, from. The second guide section 47 is then followed by a third guide section 48 aligned again in the circumferential direction.

Figure 5 - The housing is shown in Figure 5 as a single part and pot-shaped. The bottom 51 of the pot is perforated. Through the bottom 51 of the pot, the base plate 42 and the pin 52 of the output shaft 14 pass through. The shell of the pot is stepped with respect to the diameter. On a hollow cylindrical section 53 with a small diameter of the bearing seat is formed for the outer ring 55 of the rolling bearing 49, with which the pot is mounted on the base plate 42 (Figure 2).

In a hollow cylindrical portion 54 of larger diameter, the first guide track 39 is introduced. The section with the larger diameter is followed by an edge 56 of the pot. At the edge 56, the outer teeth 50 is formed on the outside. Figures 2 and 3 - inside the hollow cylindrical portion 54 with the larger diameter, the peripheral teeth 41, the sliding sleeve 40 and the guide sleeve 43 are arranged. Three guide elements 57 are attached to the sliding sleeve 40 on the circumference, of which only one is visible in the illustrations. The respective guide element can be formed only from a radially directed pin, projection or other or is, as can be seen in particular from Figure 2, formed by a radially directed pin and a radial bearing in the form of a needle bearing. The cage 5 is actuated pivotably about the central axis 37 of the output shaft 14 by means of the guide element 57. For this purpose, the guide element 57 engages radially into the second guide track 58. The guideways 58 are formed on axial extensions 59 of the cage 5.

FIG. 6 - The cage 5 according to the invention is shown in FIG. 6 as an individual part without prestressing elements and has in each case one of the guideways 58 on three axial extensions 59 distributed uniformly in the circumferential direction. The second guideway 58 extends at a short first guideway portion 60 substantially axially rectified with the central axis of the adjustment, but deflects at a second guideway portion 61 in the axial direction and in the circumferential direction obliquely. The second guideway section 61 is then followed by a third guideway section 62, which again runs rectified axially with the central axis 37.

FIG. 2 - A locking device 63 is furthermore arranged in the adjusting unit 35. The locking device 63 has at least one spring-loaded locking element 64 in the form of a ball, which is biased in a radial direction against the sliding sleeve 40. The sliding sleeve 40 has per locking element 64 at least one latching recess 65 in which the locking element 64 is latched at least in an initial position of the sliding sleeve 40.

Figure 5 - The housing 38 has at the bottom 51 circumferentially a ramp contour 65, the at least one, but preferably from three axially out the floor 51 uplifting and sloping ramps 66 is formed.

Figures 4 and 1 - At the bottom 51 are on an imaginary circular peripheral line extending over the ramps 66, at least one, but preferably three Axialverstellelemente 67 in the form of rollers. The operative connection between the adjusting unit 35 and the coupling 36 is shown in FIG. The Axialverstellelemente 67 run in one direction on the ramp contour 65 from. In the other axial direction are the Axialverstellelemente against the clutch 36 at. Relative movements of the adjusting unit 35 and the Axialverstellelemente 67 relative to the clutch 36 in the circumferential direction are possible by a thrust bearing 68 with low friction.

Figure 6 - The cage 5 is provided with all rows of cage pockets 24 all freewheeling units 1 of the freewheel device 34, which are separated from each other in the circumferential direction by the webs 10. As an alternative to the one-piece variant of the cage 5, it is conceivable that this is formed of a plurality of mutually coupled items.

Figure 7 - Figure 7 shows a section of a freewheel device 1, which is designed as a reversible roller freewheel. The freewheel unit 1 according to the invention has a freewheel ring 2, which is designed as an outer ring 15, a freewheel star 3, which is an inner star, clamping body 4 between the freewheel ring 2 and the freewheel star 3, a cage 5 and a damping cage 11. The freewheel star 3 is formed in this case directly on a shaft 7, for example on an output shaft 14.

The freewheel star 3 has a plurality of pairs of flanks of opposing blocking surfaces 8. Between the freewheel ring 2 and the freewheel star 3, a series of peripherally spaced apart clamping body 4 is arranged. The clamping body 4 are formed as rollers. Each clamping body 4 is arranged between a pair of the aforementioned flanks (blocking surfaces 8). The freewheel device 1 also has at least one clamping element 9 per clamping body 4. The respective clamping element 9 is in each case a spring, which is supported and held on the webs 10 of the cage 5. The clamping body 4 is pressed by means of the clamping element 9 in a gap between the freewheel star 3 and the outer ring. The clamping body 4 are held by the cage 5 circumferentially by the webs 10 at a distance.

The damping cage 11 is arranged separately from the cage 5 and formed with webs 12. The webs 12 have ramp-like sections 13, each of which faces a clamp body 4.

Figure 8 - Figure 8, the freewheel device 1 is shown on an output shaft 14 of a crank mechanism not shown in a partial section through the outer rings 15. Figure 9 shows a section of this freewheel assembly. Each outer ring 15 is a freewheel device 1 is used. The outer rings 15 are in this case the freewheel rings 2 (outer rings) and hingedly connected to a connecting rod.

The freewheel units 1 are arranged axially next to each other on the output shaft 14 and supported one another axially. The outer freewheel units 1 in the arrangement are supported axially on shoulders 16 and 17 of the freewheel star 3. The freewheel units 1 are not completely shown in the illustrations according to FIGS. 8 and 9. The cage 5 is almost completely missing in the illustration. Instead, the originally radially and coaxially disposed within the cage 5 damping cages 11 is visible. However, the tensioning elements 9, which are detached from the cage 5, are also visible. The tensioning elements 9 consist of a main body 115 and two spring elements 116. The two spring elements are each two obliquely spread in the axial direction leg 117. The legs 117 each of a spring element 116 are biased against the clamping body. In the freewheel assembly a total of six of the damping cages 11 are arranged side by side. Between the end faces of the damping cages 11 and the paragraphs. 16 and 17 and between the end faces of the mutually supporting damping cages 11 each one or two damping elements 6 in the form of corrugated springs 21 are arranged. The damping cages 11 are on the respective corrugated springs 21 and the corrugated springs 21 in turn are either axially supported on thrust surfaces 18 of the paragraphs 16 or 17 of the freewheel star 3 or have frontally even axially facing thrust surfaces 19 and are limited relativbeweglich between the clamping bodies 4 and arranged the contact surfaces 18 and 19 respectively. Each damping cage 11 has a plurality of peripherally adjacent notches 20. The corrugated springs 21 are each separated by a disc 22 from each other or from the paragraphs 16 and 17, which may alternatively have contact surfaces. The respective disc 22 is, for example, a circlip on the output shaft 14 and the freewheel star 3. The arranged between the corrugated springs 21 discs 22 have at the same time facing away from each other two of the contact surfaces 19, which alternatively, if two corrugated springs are directly adjacent to each other can be formed on the corrugated springs. By the corrugated springs 21, the damping element is resilient.

LIST OF REFERENCE NUMBERS

Claims

claims

1. freewheel unit (1) with at least one freewheel star (3), a free-running ring (2) and clamping bodies (4) between the freewheel star and the

Free-running ring (2) and with a cage (5) by the clamping body (4) are guided, wherein the clamping body (4) for switching the freewheel unit (1) can be acted upon by a switching mechanism, characterized in that the switching mechanism by the cage ( 5) itself and by at least one coupled to the cage (5)

Adjusting unit (35) is formed, wherein the cage (5) by means of the adjusting unit (35) is pivotally driven.

2. freewheel device (34) according to claim 1, characterized in that the freewheel device (34) of a plurality of freewheel units (1) is formed, wherein the cage a plurality of axially adjacent juxtaposed clamping bodies (4) receives, each of the rows part of one of Freewheel units (1) is.

3. crank mechanism with at least one freewheel unit (1) according to claim 1, wherein each freewheel ring (2) of each of the freewheel units (1) is pivotally connected to a connecting rod of the crank mechanism.

4. Adjusting unit according to claim 1, characterized in that the adjusting unit (35) is double-acting and thereby on the one side of the adjusting unit (35) is a pivoting movement and on the other side of the adjusting unit (35) an axial stroke can be generated.

5. Adjusting unit according to claim 1, characterized in that the adjusting unit (35) consists of a rotatably drivable housing (38) with at least one circumferentially oriented and in its course of the circumferential direction deviating guide track (39), from a sliding sleeve (40), which is axially displaceable on a peripheral toothing (41), wherein the peripheral toothing (41) is fixed to a base (14) of a guide sleeve (43) which is rotatably mounted on the sliding sleeve (40), wherein the sliding sleeve (40) is axially actuated by means of the guide sleeve, from a guide pin (43). 44), which engages in the guide track (39), formed by a guide element (57), which is axially displaceable by the sliding sleeve (40) and which engages in a second guide track (58) of the cage (5)

6. Adjusting unit according to claim 1, characterized in that the adjusting unit is provided with at least one locking device (63), wherein the locking device (63) is resiliently latchable in a pivotable element of the adjusting unit (35) and, whereby the adjusting unit ( 35) is at least in an initial position not pivotally latched.

7. crank mechanism with at least one freewheeling unit and at least one adjusting unit (35) according to claim 4, characterized in that by means of the adjusting unit (35) on one side a pivoting movement on at least the freewheel unit (1) and on the other side an axial stroke a clutch (36) is exercisable, wherein the crank mechanism and the freewheel unit (1) by means of the coupling (36) are again engageable separable from each other.