WO2005059406A1

WO2005059406A1 - Infinitely variable variator for a toroidal drive

Info

Publication number: WO2005059406A1
Application number: PCT/EP2004/013892
Authority: WO
Inventors: Wolfgang Elser; Harald Feuchter; Steffen Henzler
Original assignee: Daimlerchrysler Ag
Priority date: 2003-12-18
Filing date: 2004-12-07
Publication date: 2005-06-30
Also published as: JP2007514902A; DE10359394A1

Abstract

The invention relates to a variator for a toroidal drive, in particular for use in motor vehicles. An eccentric shaft is generally used to guarantee a contact force between toroidal discs and a roller (21a) of a variator (20a) in a toroidal drive, said shaft permitting a roller (21a) to be mounted in relation to a support (30a). According to the invention, the support (30a) is guided in a bearing unit (42a) in such a way that said support (30a) is displaced or pivoted towards the toroidal discs. This obviates the need for the use of an eccentric shaft.

Description

Infinitely variable variator for a toroidal gear

The invention relates to a continuously variable variator for a toroidal transmission according to the preamble of claim 1.

Furthermore, the invention relates to a toroidal transmission, in which a continuously variable variator according to the preamble of claim 1 is used.

In known toroidal gears, a step-by-step change in gear ratio takes place by means of a variator in which a roller with two toroidal disks is in the drive connection. A change in gear ratio takes place by changing the effective radii of the toroidal disks, at which they transmit the drive torque to the scooter. The scooter is rotatably mounted about an axis X-X relative to a carrier. It must be ensured that there is a defined contact pressure for the reliable transmission of a drive torque between the roller and the toroidal discs.

From US Pat. No. 4,453,427 it is known to mount the carrier such that it can be pivoted about its longitudinal axis with respect to a support and to support the roller with an axis of rotation that is fixed relative to the carrier relative to the carrier. In this case, a pressing force is ensured by a displaceable mounting of the torus disks along the axis of rotation of the torus disks, so that the torus disks can be pushed against the roller. It is known from US Pat. No. 4,484,487 to fix the toroidal disks axially, while the carrier supporting the roller can be pressed inwards against the toroidal surfaces by means of a hydraulic medium transversely to the axis of rotation of the toroidal disks.

From document EP 1 245 865 A2 it is known to mount the carrier with the axis of rotation fixed to the housing relative to the housing. In this case, a contact pressure is guaranteed by a degree of freedom of the roller relative to the carrier in the direction of the axis of rotation of the toroidal discs, which is provided by two needle bearings between roller and carrier.

A large number of solutions are based on the use of an eccentric shaft, which radially supports the scooter in one shaft area and is rotatably supported with respect to the carrier in another shaft area, cf. for example US 6,152,850. Here, a pivoting of the eccentric shaft leads to a change in the distance of the scooter from the torus disks. JP 06280958 A also shows the use of an eccentric shaft, with an inclined position of the carrier being provided which is designed in such a way that deformations due to the contact forces are compensated in advance.

From document EP 0 780 599 B1 a variator with two chambers is known, in which the shafts or eccentric shafts are fixed in one chamber in relation to the carrier. All torus disks as well as the rollers of the other chamber can be moved axially, ie in the direction of the axis of rotation of the torus disks, so that the contact pressure is guaranteed when the position of the roller in the chamber is fixed. From publication US 6,117,043 it is known, for reasons of mounting the carrier in a slot of a yoke to la ^¬ like, wherein the slot is oriented transverse to the axis of rotation of the toroidal discs. In the case of contact forces acting on the rollers and the carriers, the carriers in the elongated holes are pressed outward into an end position, so that the positions shown in the figures of this publication correspond to the operating position.

From the document DE 100 34 454 AI it is known to provide a bearing between a carrier and the actuating piston of an actuating unit which permits displacements of the carrier in the direction of the toroidal discs. Here, an elastic connection between the carrier and the actuating piston takes place via a tie rod. In this way, the use of an eccentric shaft can be dispensed with. Another solution is known from the publication DE 101 48 399 AI.

The object of the present invention is to propose a continuously variable variator for a toroidal transmission, which has alternative and / or improved options for ensuring a contact pressure in a toroidal transmission.

The object on which the invention is based is achieved by the features of claim 1.

According to the invention, a bearing unit is provided between the carrier and an adjacent component. The adjacent component is a support device for the carrier, preferably a housing or a yoke, by means of which the movements of several carriers of a chamber of a variator are coordinated. The storage unit has a degree of freedom of movement. The degree of freedom of movement ensures a displacement of the carrier relative to the neighboring component, in particular along a straight line, along a circular path or along a curve. The degree of freedom of displacement has at least one component in the direction of the axis of rotation (ZZ) of the toroidal discs. According to the invention, the distance of the carrier - and thus also of the scooter - from the torus disc (s) is thus changed with a displacement of the carrier in accordance with the degree of freedom of displacement. The degree of displacement can thus influence or ensure the contact pressure between the roller and the torus disc (s). The shift according to the degree of freedom of movement can be force-free, against a frictional force or by applying an energy store (spring store). The displacement can be limited by fixed or adjustable stops.

At the same time, the bearing unit supports the carrier in relation to the neighboring component in the direction of the axis (X-X). The direction of the axis (X-X) and thus the support with respect to the neighboring components depends on the operating position of the variator and changes with a pivoting of the carrier around the axis (Y-Y) by means of an adjustment of the variator. The axes (x-x), (Y-Y) and (Z-Z) in particular form an orthogonal system that is fixed to the vehicle. The axis (x-x) corresponds to the axis (X-X) in the position for the variator ratio i = -1. For different translations, the axis (X-X) is pivoted about the axis (Y-Y) with respect to the axis' (x-x).

By ensuring a support in the direction of the axis (XX) according to the invention, an optimal power flow in the variator is ensured. In particular, it is reliably excluded that an adjustment of the variator leads to a change in the contact pressure between the roller and the torus discs.

According to the invention there is thus an alternative to the known solutions according to the aforementioned document to ensure the contact pressure. (An additional ^¬ A set known from the above-mentioned or other publications solutions in addition to the invention is also possible without departing from the scope is that of the invention).

For exemplary assumed 30 ° maximum pivoting of the carrier about the axis (YY), it has been shown that a displacement in the direction of the torus disks is also guaranteed if the degree of freedom of displacement is not oriented for all pivotings in the direction of the axis (ZZ), but also if, according to the pivoting, the degree of freedom of displacement has only one component in the direction of the axis (ZZ). The same applies u. U. for the absorption of support forces in the direction of the axis (X-X).

The bearing unit is preferably designed to be multifunctional: in accordance with this embodiment of the invention, the bearing unit ensures, in addition to the degree of freedom of displacement, a rotation of the carrier about a longitudinal axis of the carrier, which is particularly necessary in the context of the stepless adjustment of the translation of the variator. In this way, a particularly simple and compact variator can be created. A support in the direction of the axis (XX) and a guarantee of rotation of the carrier about an axis (YY) are preferably used for guidance in the direction of the degree of displacement. the same bearing elements as the bearing body and contact surfaces.

According to a development of the toroidal gear according to the invention, the bearing unit has at least one contact surface. The contact surface is oriented transversely to the axis (X-X). Forces are supported on the contact surface in the bearing unit, which act on the roller and the carrier in the direction of the axis of rotation of the roller (X-X). For this purpose, at least one bearing body, in particular a sliding or rolling body, can be arranged between the carrier and the adjacent component, which is supported on the contact surface in order to absorb the aforementioned forces. For a movement according to the degree of freedom of displacement, the bearing body slides along or rolls against the contact surface. The contact surface is designed to be multifunctional, since on the one hand it serves to absorb the aforementioned forces and on the other hand it serves as a guide surface for moving the carrier in the direction of the toroidal disc (s).

A particularly simple embodiment of the toroidal transmission according to the invention is characterized in that the bearing unit has a bearing eye, for example with an elongated hole. The lateral (elongated) boundaries of the bearing eye or slot are formed with the contact surfaces. For a movement of the carrier in the direction of the degree of freedom of displacement, the bearing body slides along the contact surface and along the bearing eye. In an alternative embodiment, the bearing body has an outer contour in the form of a segment of a circle and rolls on the contact surfaces. The bearing body is preferably taken up in a direction perpendicular to the degree of freedom of movement (almost) free of play or with a suitable fit or (in the transfer of the publication US Pat. No. 6,117,043) to form a game. lvrr --ι * ^■ • ^• -

taken, the game is overcome in an operating position due to the forces acting on the carrier.

According to a variant of the invention, the bearing eye is assigned to the carrier, while the yoke has a pin. Ge ^¬ genüber the pin is designed as a bearing ring bearing body, in particular with the interposition of rolling elements rotatably gelager. The assignment of the bearing eye to the carrier has the advantage that the bearing eye is also pivoted when the carrier is pivoted to adjust the ratio of the variator. The result of this is that the contact surfaces are oriented transversely to the axis (XX) regardless of the swivel angle, which ensures optimal force support.

In an alternative embodiment, according to another variant of the invention, the bearing eye is assigned to the yoke, while the carrier has a pin. A bearing body designed as a bearing ring is rotatably mounted opposite the journal, in particular with the interposition of rolling bodies.

Preferably, the inner surface of the bearing ring is suitably adapted to the rolling elements, while the outer contour of the bearing ring is adapted to the contact conditions with the bearing eye, for example via an annular outer contour, which ensures a good osculation of the bearing ring against the contact surfaces of the bearing eye.

According to a development of the invention, the carrier is supported with two bearing units opposite two adjacent components, in particular yokes. The two bearing units each have a degree of freedom of displacement with at least one component in the direction of the axis (Z- Z). Thus, a displacement and / or pivoting is provided by the carrier in a plane through the two bearing units, which is entiert in the direction of the rotation axis of the toroidal discs ori ^¬ and is oriented approximately transversely to the axis (XX). This can be a linear movement or a swiveling of the carrier.

According to an alternative embodiment, the carrier is mounted with two bearing units opposite two adjacent components. According to this embodiment, one of the two bearing units has a degree of freedom of displacement with at least one component in the direction of the axis (ZZ), while the other bearing unit fixes the carrier in a momentary pole in the direction of the toroidal discs. This other bearing unit only allows the carrier to be pivoted, the axis of rotation or an instantaneous pole of the carrier being predetermined by the other bearing unit. This is particularly advantageous if the other bearing unit is arranged in the immediate vicinity of an actuating unit, so that a displacement of the carrier along the degree of freedom of movement is accompanied by small displacements in the region of the actuating unit. The instantaneous pole can be provided directly in the middle or in the area of the bearing unit or can be provided at a distance from the bearing unit, for example in the area of the actuating piston of the actuating unit. A further bearing unit is preferably provided between the actuating piston and the carrier, which enables the carrier to be pivoted relative to the actuating piston. In this case, it is particularly advantageous if the instantaneous pole in this case is provided in the region of the further bearing unit. The further bearing unit is, for example, a ball joint. It is also conceivable that the actuating piston can only exert axial forces on the carrier while there is a play transversely between the carrier and the actuating piston is provided for the actuating movement of the actuating unit. For different designs of such a further bearing unit, reference is made to the publications US Pat. No. 5,971,886, WO 02/44587, WO 94/01697 and WO 92/11475, the disclosures of which for connecting the actuating piston to the carrier are made the subject of the present application.

According to a development of the invention, a rotatable eccentric shaft can be saved. As a result, the construction of the variator can be simplified, in particular a radial bearing for the eccentric shaft can be saved. At the same time, the stiffness of the scooter support increases. According to the invention, the stationary arrangement of the axis about which the roller is rotatably mounted relative to the carrier is thus made possible.

According to a preferred embodiment of the toroidal gear, a bearing pin is provided which serves to support the scooter radially with respect to the carrier. Here, the journal can either be fixed to the carrier or fixed to the scooter. The bearing journal can be integrally connected to the aforementioned components, inserted into them and / or connected to them via a fastening means or a material or positive connection.

According to a further embodiment of the invention, rolling elements, which serve to support the forces acting on the roller in the direction of its axis of rotation (XX), roll on a bearing disk arranged between the carrier and the rolling element. This bearing disc can be selected according to the rolling conditions, particularly with regard to material, hardness, surface quality and manufacturing accuracy. According to an alternative embodiment of the invention, the aforementioned rolling elements roll directly on a running surface of the carrier. According to this embodiment, the number of components required can be reduced. In this way, an assembly effort can be reduced and the functionality can be improved by avoiding additional contact surfaces.

The bearing eye preferably has an inner contour in the form of a segment of a circle in the longitudinal section (plane X-X; Y-Y). The radius of the inner contour corresponds approximately to the diameter of the bearing eye. This is advantageous if the bearing unit is intended to enable the support to be pivoted relative to the adjacent component, in particular the yoke, since in this case the bearing body can pivot along the inner contour in the form of a segment of a circle.

As an alternative or in addition, it is conceivable for contact surfaces or raceways to have a curved or circular shape in projection into the plane spanned by the axes (Z-Z) and (Y-Y). This is advantageous if the carrier is supported by two bearing units with respect to the adjacent yokes, one bearing unit having no degree of freedom of displacement and forming the instantaneous pole of the carrier. In this case, the carrier moves around the instantaneous pole in the area of the bearing unit with the degree of freedom of displacement along the contact surfaces or raceways in the form of a segment of a circle.

The distance between the contact surfaces in the direction of the axis (ZZ) preferably decreases. In this way, an improved osculation is made possible, in particular with increasing proximity to the torus disks. Furthermore, the reduction in the distance between the contact surfaces results in a simple manner Under certain circumstances, a centering function in a central position for the greatest distance between the contact surfaces. Beispielswei ^¬ se is formed the bearing eye in cross-section slightly elliptical.

According to a preferred embodiment of the toroidal transmission, the shaft used for mounting the scooter in the direction (X-X) with respect to the carrier is supported on both sides of the scooter, in other words in the direction of view of the axis (X-X) in front of and behind the scooter, with respect to the carrier. This is based in particular on the knowledge that, according to the invention, the axis (X-X) can be fixed in relation to the carrier. The aforementioned bilateral support is particularly stiff. The dimensioning of the carrier can be changed in addition or alternatively.

Advantageous further developments result from the subclaims, the description and the drawings.

Preferred exemplary embodiments of the toroidal transmission according to the invention or parts thereof are explained in more detail below with reference to the drawing. The drawing shows:

1 is a partial section of a variator according to a first embodiment with a cut transverse to the axis of rotation of the toroidal disks,

2 shows a partial section from a variator according to a second embodiment with a cut transverse to the axis of rotation of the toroidal disks,

Fig. 3 shows a bearing unit between a yoke and a carrier, for example according to FIG. 2, with a cut transverse to the axis (YY),

4 shows a longitudinal section through a bearing eye when looking in the direction of the axis (X-X) with a raceway and a contact surface,

5 shows a longitudinal section through a bearing unit when looking in the direction of the axis (Z-Z),

6 a bearing unit with a linear guide in cross section,

7 a bearing unit in partial cross section,

8 shows a partial section from a variator according to a third embodiment with a cut transverse to the axis of rotation of the toroidal disks,

9 shows a partial section from a variator according to a fourth embodiment with a cut transverse to the axis of rotation of the toroidal disks,

10 is a partial section of a variator according to a fifth embodiment with a cut transverse to the axis of rotation of the torus disks,

11 is a partial section of a variator according to a sixth embodiment with a cut transverse to the axis of rotation of the torus disks,

12 is a partial section of a variator according to a seventh embodiment with a cut transverse to the axis of rotation of the toroidal disks, Fig. 13 is a partial section of a variator according to a th ah ^¬ embodiment when cut along transverse to the rotation-axis of the toroidal discs,

14 is a partial section of a variator according to a ninth embodiment with a cut transverse to the axis of rotation of the toroidal disks,

15 shows a partial section from a variator according to a tenth embodiment with a cut transverse to the axis of rotation of the toroidal disks.

The invention is used in toroidal gears for motor vehicles, in which a variator 20 is used to continuously change the transmission ratio between at least one drive torus and one output torus. For this purpose, a roller 21 is clamped on opposite sides of its circumferential surface between the toroidal disks. For the exemplary embodiment shown in FIG. 1, the torus disks each rotate about an axis oriented perpendicular to the plane of the drawing and (not shown) are arranged above or below the plane of the drawing.

The roller 21 is supported radially with respect to an eccentric shaft 22. For this purpose, the roller 21 has a central blind hole in which a radial bearing, in particular a needle bearing 23, is received. The radial bearing 23 rolls radially on the inside on a pin 24 which is formed concentrically to the axis (X-X).

In addition to the pin 24, the eccentric shaft 22 has a further pin 25, which is concentric to the axis (X ^ -X). The axis (X'-X ^) is arranged parallel and spaced apart from the axis (XX). In the transition area between the Pins 24,25 has the eccentric shaft 22 an annular _APPROACH 26 whose outer diameter approximately corresponds to the diameter of the scooter 21st Between facing end faces of the roller 21 and the lug 26, which are oriented transversely to the axis (XX), a thrust bearing is connected rule 27 Zvi ^¬. For the exemplary embodiment shown in FIG. 1, the axial bearing 27 is an axial ball bearing. In the end faces of the roller 21 and the shoulder 26 are adapted to the rolling elements 28 of the axial bearing 27, which are provided with a suitable surface and advantageous material properties. The rolling elements 28 are guided in a cage 29.

The eccentric shaft 22 is supported against a carrier 30. For this purpose, the carrier 30 has a blind hole in which a radial bearing 31 is received. In the exemplary embodiment shown in FIG. 1, the radial bearing 31 is a needle bearing, in which a bush 32 guiding the needles in the direction of the axis (X-X) is inserted between the carrier 30 and the needles.

The eccentric shaft 22 is supported in relation to the carrier 30 in the direction of the axis (X-X) via an axial bearing 33, here a needle bearing, which is located between mutually facing end faces of the carrier 30 and the shoulder 26; which are oriented transversely to the axis (X-X) acts. In the exemplary embodiment shown in FIG. 1, the rolling bodies of the axial bearing 33 roll off directly on the shoulder 26 and on a running disk 34, which is supported on the carrier 30.

In the illustrated longitudinal section, the carrier 30 is approximately U-shaped, with a base leg 35, in which the eccentric shaft 25 is mounted approximately in the center, and two parallel side legs 36, 37, between which at least partially the eccentric shaft 22 and the roller 21 are arranged. The side legs 36,37 have in the base ^¬ leg 35 opposite end portion respectively to the outside and parallel to the base limb 35 and coaxially o- rien oriented projections or pins 38,. 39

The pins 38, 39 at least partially have a cylindrical outer surface 40, 41, which each serve as the inner bearing surface of a bearing unit 42, 43.

In the exemplary embodiment shown in FIG. 1, the bearing units 42, 43 are formed with rolling bodies 44, 45, here needles, which roll on the lateral surfaces 40, 41. The rolling elements 44, 45 roll on one side or both sides of the rolling elements 44, 45 on a bearing body 46, 47 leading the rolling elements 44, 45 in the direction of the axis (XX). The bearing bodies 46, 47 are formed concentrically to the axis (YY), with an outer contour which is spherical, in particular part-circular, in longitudinal section, the center point of the pitch circle being on the axis (YY). The bearing unit 42 is axially fixed by means of a securing element 48 which, according to FIG. 1, is designed as a locking washer, which is supported on the bearing body 46 and the pin 38. The bearing unit 43 is axially secured via a disk body 49 which is fixed relative to the pin 39 and on which the bearing body 47 is supported. Rotating movements of a plurality of carriers 30 about the axis (YY) are coupled via the pulley body 49, in that a coupling means, such as a rope, is wrapped around the outer surface of the ^' pulley body 49.

The lateral surfaces of the bearing bodies 46, 47 are accommodated in a recess 50, 51 of a yoke 52, 53 with play, a precise fit or under pretension. In the in Fig. 1st shown longitudinal section, the recesses 50, 51 have a rectilinear contour.

The compound of the yokes 52,53 to the carrier 30 via the La ^¬ gereinheiten 42,43 allows relative pivoting about the axis (YY) for which the bearing member 46,47 fixedly disposed opposite to the yokes 52,53. In addition, the aforementioned connection enables the yokes 52, 53 to be pivoted relative to the carrier 30 about an axis which is oriented vertically to the axes (xx) and (YY) and during which the angle between the longitudinal axis of the carrier 30 and the longitudinal axis the yokes 52.53 changed. For such a pivoting, the bearing bodies roll with the lateral surface in the direction of the part-circular contour on the recesses 50, 51.

The yokes 52, 53 serve to couple the movements of adjacent carriers 30 of a chamber of a variator. As a result of the coupling, two carriers 30 and the yokes 52 form approximately parallelograms, the angles of which change with an adjustment. The yokes 52, 53 are supported by a suitable bearing in relation to a component fixed to the housing.

The carrier 30 and the eccentric shaft 22 have suitable channels 54 for supplying lubricant to the bearing units 23, 27, 31, 33, 42, 43.

The variator 20 according to the invention is integrated in any toroidal gear, for example in any gear of the IPC class F16H037 / *. As an example, reference is made to the publications US Pat. No. 6,059,685, DE 100 40 039 AI and DE 101 21 042 C2 with regard to the transmission surrounding the variator. With regard to the coupling of the movements of a plurality of carriers 30, reference is made only by way of example to the publication DE 102 06 200 AI and the unpublished application DE 103 0.9 569.1 by the applicant. For Ermögli ^¬ monitoring and regulation of the contact pressure between the roller 21 and toroidal discs by a suitable displacement of the toroidal discs is exemplarily referred to unveröf entlichten documents DE 102 33 089.1, DE 102 33 091.3 and DE 102 33 090 of the applicant. The carriers 30 can be displaced in the direction of the axis (YY) by means of a suitable actuating unit in order to adjust the variator. In this regard, reference is made, for example, to the unpublished applications DE 102 36 619.5, DE 103 00 569.2-14 and DE 103 08 496.7 of the applicant with regard to structure, regulation and function.

The cited documents are made the subject of the present applications by the citations.

The following movements are possible for an embodiment according to FIG. 1:

- According to an actuator, movement of the carrier 30 in the direction of the axis (Y-Y) is possible.

The bearing units 43, 42 enable the carrier 30 to be pivoted about the axis (Y-Y).

- The roller 21 is rotatable about the axis (X-X) relative to the eccentric shaft 22. This rotary movement correlates with the rotary movement of the associated toroidal discs.

- The eccentric shaft 22 is pivotable, which allows a change in the distance between the roller 21 and toroidal discs. For the following figures for components which correspond to components in principle in Fig. 1, the same reference numerals, and these one letter for Distinguishing ^¬ voltage of the associated character is appended.

1, a bearing unit 43a including the associated areas of carrier 30a and yoke 53a corresponding to FIG. 1 is formed for the exemplary embodiment shown in FIG. 2. This bearing unit is preferably a bearing unit arranged adjacent to an actuating unit for displacing the carrier 30a. In the area of the other bearing unit 42a, the carrier 30a is designed without a pin 38. The side leg 37a of the carrier 30a has a recess which is oriented in the longitudinal direction of the carrier 30a and forms a bearing eye 60a. The associated yoke 52a is provided with a crank, the end region of which forms a pin 61a. The pin 61a is mounted in the bearing eye 60a via the bearing unit 42a, in which case the rolling elements 44a roll on the pin 61a radially on the inside and roll on the outside in the bearing body 46a. The bearing body 46a is accommodated in the bearing eye 60a of the carrier 30a with play, a precise fit or with pretension. Pin 61a, bearing eye 60a are formed in the longitudinal section shown in FIG. 2 mirror-symmetrically to the axis (Y-Y) '.

Fig. 3 shows the bearing eye 60a in cross section. The bearing body 46a lies in the direction X (parallel to the axis (XX)) on contact surfaces 62a, 63a of the bearing eye 60a. The bearing eye 60a is designed as an elongated hole in the direction of the axis (ZZ). This results in a clearance 64a, 65a between the bearing eye 60a and the bearing body 46a in the direction ZZ, around which the bearing body and thus also the pin 61a relative to the carrier 30a is movable. Games 64a and 65a are preferably one to three or approximately two millimeters each. The contact surfaces 62a and 63a can in this case be parallel to each other and oriented to the axis (ZZ), to be a curved shape or corresponding to that in Fig. 2 shown exporting ^¬ approximately example be formed approximately circular, so that from a movement from the position shown in Fig. 3 Center position in the direction of the axis (ZZ) results in an increased osculation or contact pressure of the bearing body 46a against the bearing eye 60a.

As a result of the degree of freedom of displacement in the direction of the axis (Z-Z) made possible in this way, the carrier 30a can be pivoted in a plane which is oriented transversely to the axis (X-X) and extends through the axis (Y-Y). Such a pivoting takes place around a momentary pole 66a of the carrier 30a, which lies on the axis (Y-Y) and is arranged approximately in the region of the bearing unit 43a. The instantaneous pole 66a preferably corresponds to the center point of the part-circular outer contour of the bearing body 47a. The distance of the scooter from the toroidal disks can be changed by means of the aforementioned pivoting, as a result of which the eccentric shaft 22 can be omitted. As a result, according to the embodiment shown in FIG. 2, the radial bearing 31 and the axial bearing 33 can be omitted. The pin 24a is preferably fixedly connected to the carrier 30a. Here, the pin 24a is formed in one piece with the carrier 30a, connected to it in a form-fitting or material-locking manner or connected via a suitable fastening means.

In the exemplary embodiment shown in FIG. 2, a running surface of the axial bearing 27s opposite the running surface of the roller 21a is formed by a bearing disc 67a, which is designed in the form of a ring and is located radially on the inside supported on the journal 24a, forms a running surface for the thrust bearing 27a in the region of an end side and is supported on the opposite end side in the direction of the axis (XX) ge ^¬ genüber the carrier 30a.

According to the embodiment in FIG. 2, the guidance of the lubricant can be decisively simplified since it is not necessary to lubricate the radial bearing 31 and the axial bearing 33 and it is not necessary to transfer the lubricant from the carrier 30a to the eccentric shaft.

For a movement around the instantaneous pole 66a, a movement in the direction of the degree of freedom of displacement results in a movement of the contact surface 62a, 63a on a circular path corresponding to FIG. 4, the radius 68a corresponding to the distance of the contact surface 62a, 63a from the instantaneous pole 66a.

According to the exemplary embodiment shown in FIG. 5, the contact surfaces 62a, 63a are formed in a longitudinal section through the bearing eye corresponding to the outer contour of the bearing body 46a, in particular part-circular. This results in guidance of the bearing body 46a in the direction of the axis (Y-Y), while pivoting of the bearing body 46a relative to the carrier 30a is made possible.

According to the exemplary embodiment of the invention shown in FIG. 6, at least one linear guide bearing 69b can be interposed between the bearing body 46b and the associated contact surfaces 62b, 63b. The linear guide bearing 69b is designed as a sliding or rolling bearing. In the exemplary embodiment shown in FIG. 6, a roller bearing with cylindrical rollers, barrel rollers, balls or needles as roller bodies, possibly with a cage, is used as the linear guide bearing 69b. Fig. 7 shows an alternative embodiment of a Lagerau ^¬ ges 60c, in which the abutment surfaces 62c and 63c in cross section through the bearing eye ^¬ straight or 60c are formed with a large radius of curvature.

For the exemplary embodiment shown in FIG. 8, the pin 24d is formed separately from the carrier 30d, with the configuration corresponding essentially to FIG. 2. The carrier 30d has a bore 70d, into which the pin (preferably with an interference fit) is firmly inserted. The bearing disk 67d is formed in one piece with the carrier 30d, so that the axial bearing 27d is supported directly opposite the carrier 30d and a running surface of the axial bearing 27d is formed by the carrier 30d.

For the exemplary embodiment shown in FIG. 9, the pin 24e is fixed, in this case in one piece, connected to the roller 21d. With the axial bearing 27e designed according to FIG. 8, the radial bearing 23e acts between the pin 24e and the carrier 30e. The radial bearing 23e runs radially on the inside on the pin 24e. The radial bearing 23e runs radially on the outside in a bore 70e of the carrier 30e. The radial bearing 23e and the roller 21e are axially secured by means of securing elements 71e, here a securing ring which is supported on the one hand in a groove of the pin 24e and on the other hand rests on the carrier 30e. For the exemplary embodiment shown in FIG. 9, the disk body 49 has been omitted. Instead of (or in addition to) the disk body 49, the rotation of the carriers 30e is coupled about the axes (YY) via a coupling means designed as a rope, which partially wraps around the carrier 30e in the region of the bearing unit 42e or in the region of the bearing eye 60e. For this purpose, in the outer surface of the 30e carrier in the region of the bearing eye grooves 60e 72e for ^¬ On acceptance of the coupling agent is introduced. Here Kopp ^¬ can healing powers positive and / or transferred reibschlüsslich.

The exemplary embodiment shown in FIG. 10 essentially corresponds to the exemplary embodiment shown in FIG. 2, the bearing disk 67a being formed in one piece with the carrier 30f when the pin 24f is formed in one piece with the carrier 30f (cf. explanations of FIG. 8).

In contrast to FIG. 10, the bearing eye 60g is simplified for the exemplary embodiment according to FIG. 11 such that, in contrast to FIG. 3, the part of the bearing eye arranged to the left of the axis (Z-Z) has been omitted. Accordingly, the bearing body 46g is supported only on the contact surface 62g facing a central gear axis 73g. In the simplest case, the carrier 30g only had an extension 74g in the end region of the side leg 37g facing away from the base leg 35g, which extension is oriented parallel to the base leg 30g and is directed away from the roller 21g. The bearing body 46g bears against the extension 74g in the region of the contact surface 62g. The running surface for the contact surface 62g is straight or curved in the direction of the degree of freedom of movement (Z) (cf. FIG. 4). The contour of the tread in the direction of the axis (Y-Y) is formed in a straight line or (according to FIG. 5) adapted to the contour of the bearing body 46g. When cutting in the direction of the axes X and Z, the tread is straight or curved.

This embodiment is based on the knowledge that the roller 21g is pushed away from the central gear shaft 73g during operation of the toroidal gear, so that support via the contact surface 62g is sufficient. The exemplary embodiment shown in FIG. 12 essentially corresponds to the exemplary embodiment shown in FIG. 8, the carrier 30h here being designed as a closed ring structure with a cut in the direction of the axes X and Y, in the interior of which the roller 21h is arranged. For this purpose, the end of the bearing eye 60h facing away from the base leg 35h is connected via a connecting web 75h to the end of the side leg 36h facing away from the base leg 35h. The connecting web 75h is oriented approximately parallel to the base leg 35h. This results in an increased rigidity of the carrier 30h and the bearing eye 60h.

In contrast to the exemplary embodiment shown in FIG. 12, the pin 24i penetrates the roller 21i according to FIG. 13 and is supported in an end region projecting from the roller in the direction of the central gear axis 73i with respect to the connecting web 75i. The pin 24i has a first partial area which is fixedly connected to the carrier 30i, a second partial area which carries the radial bearing 23i on the radially outer side for supporting the roller 21i and a third partial area which penetrates a central bore of the roller 21i with radial play and which is firmly inserted into a bore from the connecting web 75i, the three aforementioned partial areas being arranged one behind the other in the order mentioned in the direction of the axis (X). Alternatively, it is conceivable for the pin 24i and the associated receptacle in the carrier 30i or in the connecting web 75i to have a non-circular cross section for securing against rotation in the first and third partial areas.

According to the exemplary embodiment shown in FIG. 14, the connecting web 75 is not integral with the carrier 30 formed, but rather as a separate component, which is in the region of the bearing eye and 60j in Endbe ^¬ rich side of the leg 36 with the carrier 30j form-locking, material-locking, friction fit, or permanently connected via a connecting means. On the side facing the carrier 30j, the connecting web 75j has a pin 76j. The pin 24j has, on the side facing the connecting web 75j, a central blind hole, within which the pin 76j is accommodated in a precisely fitted state to support the pin 24j with respect to the connecting web 75j.

This is equally possible if the connecting web 75k and the carrier 30k are formed in one piece (cf. FIG. 15).

Further features are the drawing, in particular the geometries of the components shown, the relative dimensions of a number of dimensions of the same or different components shown, the relative arrangement of the components to one another and their operative connections to one another,

refer to. The combination of features of different configurations shown in different figures and / or with features of the configurations of the cited prior art is also possible.

Claims

claims

1. Infinitely adjustable variator for a toroidal gear with torus discs rotating about an axis (ZZ), in which a roller (21) is rotatably mounted about an axis (XX) relative to a carrier (30) and the carrier (30) is rotatable about an axis (YY), characterized in that the carrier (30) is mounted with a bearing unit (42) opposite at least one adjacent component, the

Bearing unit has a degree of freedom of displacement with at least one component in the direction of the axis (Z-Z) and supports the carrier relative to the adjacent component in the direction of the axis (X-X).

2. Variator according to claim 1, characterized in that the degree of freedom of movement is oriented independently of the pivoting of the carrier (30) about the axis (Y-Y) transversely to the axis (X-X).

3. Variator according to claim 2, characterized in that an adjacent component is a yoke (52, 53) connecting a plurality of supports (30).

4. variator according to claim 3, characterized in that the bearing unit (42) ensures rotation of the carrier (30) about the axis (YY) in addition to the degree of freedom of displacement.

5. variator according to claim 4, characterized in that the bearing unit (42) associated portion of the yoke (52) is arranged displaceably in the direction of the axis (Y-Y).

6. variator according to claim 5, characterized in that the bearing unit (42) has at least one contact surface (62,63) which a) is oriented transversely to the axis (XX), b) on which in the direction of the axis (XX ) oriented forces acting on the roller (21) and the support (30) and c) along which a bearing body (46) of the bearing unit (42) slides or rolls during a movement according to the degree of freedom of displacement.

7. variator according to claim 6, characterized in that the bearing unit (42) has a bearing eye (60), the lateral boundaries are formed with the system surfaces (62,63) and in which the bearing body (46) in one direction transversely is added to the degree of freedom of movement without play.

8. variator according to claim 7, characterized in that the carrier (30) has the bearing eye (60) and the yoke (52) has a pin (61), against which a bearing body (46) designed as a bearing ring is rotatably mounted.

9. variator according to claim 7, characterized in that the yoke (52) has the bearing eye (60) and the carrier (30) has a pin (38) against which a bearing body designed as a bearing ring (46) is rotatably mounted.

10. Variator according to one of the preceding claims, characterized in that the carrier (30) with two bearing units (42, 43) is mounted opposite two adjacent components (yokes 52, 53), the two bearing units (42, 43) each over have a degree of freedom of movement with at least one component in the direction of the axis (ZZ).

11. Variator according to one of claims 1 to 9, characterized in that the carrier (30) with two bearing units (42, 43) is mounted opposite two adjacent components (yokes 52, 53), a bearing unit (42) being displaced Degree of freedom with at least one component in the direction of the axis (Z-Z), while the other bearing unit (43) fixes the carrier (30) in a momentary pole (66) in the direction of the axis (ZZ).

12. Variator according to one of the preceding claims, characterized in that the axis (X-X), about which the roller (21) is rotatably mounted, is arranged stationary with respect to the carrier (30).

13. Variator according to one of the preceding claims, characterized in that a bearing pin (24) for radially supporting the scooter (21) with respect to the carrier is firmly connected to the carrier (30) or the scooter (21).

14. Variator according to one of the preceding claims, characterized in that rolling elements of an axial bearing (27) roll between roller (21) and carrier (30) on a bearing disc (67) arranged between carrier (30) and rolling elements (28).

15. Variator according to one of claims 1 to 13, characterized in that rolling elements of an axial bearing (27) roll between roller (21) and carrier (30) directly on a running surface of the carrier (30).

16. Variator according to one of the preceding claims, characterized in that ropes used for synchronizing the adjusting movements of a plurality of carriers (30) directly loop around the carrier (30).

17. variator according to claim 16, characterized in that the ropes loop around the carrier (30) in the region of a lateral surface of a bearing eye (60).

18. Variator according to one of claims 13 to 17, characterized in that the carrier (30) has an essentially E-shaped cross-section, at least one of the outer horizontal legs (36, 37) of the E-shaped cross-section being a La- forms (60) and the middle horizontal leg forms the bearing journal (24) for the roller (21).

19. Variator according to one of the preceding claims, characterized in that the bearing eye (60) has a circular segment-shaped inner contour in longitudinal section.

20. Variator according to one of claims 11 to 19, characterized in that contact surfaces (62, 63) or raceways of the bearing body (46) are curved in projection into the plane spanned by the axes (Z-Z) and (Y-Y).

21. Variator according to claim 20, characterized in that contact surfaces (62, 63) or raceways of the bearing body (46) are designed in the form of a segment of a circle in projection into the plane spanned by the axes (ZZ) and (YY) with a radius which is approximately that Distance of the contact surface (62,63) or track from the instantaneous pole (66) corresponds.

22. Variator according to one of claims 6 to 21, characterized in that the distance between the opposing contact surfaces (62, 63) decreases in the direction of the axis (Z-Z).

23. Variator according to one of claims 6 to 22, characterized in that at least one contact surface (62, 63) is designed in the form of a circular arc in cross section through the bearing eye (60).

_24th Variator according to one of claims 6 to 23, characterized in that between a contact surface (62, 63) which is assigned to the carrier (30) or the adjacent component (yoke 52) and the adjacent component (yoke 52) or a linear bearing (69) is interposed between the carrier (30).

25. Variator according to one of the preceding claims, characterized in that the yoke (52) has a bearing pin (61), against which a bearing ring (46) with a spherical outer surface is rotatably mounted, which on a in the direction of the axis (ZZ) rolling contact surface (62,63) of the carrier (30).

26. Variator according to one of claims 12 to 25, characterized in that the shaft (pin 24) used for mounting the roller (21) relative to the carrier (30) on both sides of the roller (21) relative to the carrier (30) is supported.

27. Variator according to one of the preceding claims, characterized in that the bearing unit (42g) forms only a one-sided support of the carrier (30g) with respect to the adjacent component (yoke 52g), the support acting in the direction of the axis (X-X).

28. Variator according to one of the preceding claims, characterized in that the carrier (30) with the roller (21) and the intermediate axial bearing (27) forms an assembly unit.

29. Variator according to one of the preceding claims, characterized in that balls, tapered rollers or barrels are used as the rolling elements (28) of the axial bearing (27).

30. Toroidal transmission with a continuously variable variator (20) according to one of claims 1 to 29.