JP2007514902A - Continuously variable variator for toroidal transmission - Google Patents

Abstract

  The present invention relates to a variator for toroidal transmissions, particularly for use in motor vehicles. The eccentric shaft is generally used to ensure the contact force between the toroidal disk of the variator (20a) of the toroidal transmission and the roller (21a), and the shaft (21a) supports the roller (21a) by the shaft (30a). Can be mounted against. According to the invention, the support (30a) is guided to the bearing unit (42a) so as to be displaced or pivoted towards the toroidal disc. This eliminates the need to use an eccentric shaft.

Description

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

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

  In known toroidal transmissions, the stepless change of the gear ratio is effected by a variator in which a roller is drivingly connected to two toroidal disks. The speed ratio is changed by changing the effective radius of the toroidal disk, and at this effective radius, the toroidal disk transmits drive torque to the rollers. The roller is attached to the support so as to be rotatable about an axis XX. In this case, it must be ensured that a defined contact pressure is applied in order to reliably transmit the drive torque between the roller and the toroidal disk.

  Japanese Patent Application Laid-Open No. H11-228867 is known for attaching the support body to the support means so as to be pivotable about its longitudinal axis and attaching the roller to the support body having a fixed rotation axis with respect to the support body. . In this case, the contact pressure is ensured by displaceably mounting the toroidal disk along the axis of rotation of the toroidal disk, so that the toroidal disk can be pressed against the roller.

  Patent Document 2 discloses that the toroidal disk is fixed in the axial direction while the support member supporting the roller can be pressed against the toroidal surface inward in the lateral direction with respect to the rotation axis of the toroidal disk by hydraulic means. Are known.

  Patent Document 3 is known for attaching a support to a housing having a rotation axis fixed to the housing. In this case, the contact pressure is ensured by the degree of freedom of the roller relative to the support in the direction of the axis of rotation of the toroidal disk, this degree of freedom being provided by two needle bearings between the roller and the support.

  A number of solutions are based on the use of an eccentric shaft that supports the roller radially in one axial region and is rotatably supported relative to the support in the other axial region (e.g. reference). In this case, a change occurs in the distance from the toroidal disk to the roller by turning the eccentric shaft. U.S. Pat. No. 6,057,086 also shows the use of an eccentric shaft, and the tilt of the support is designed so that the deformation as a result of the contact pressure is compensated in advance.

  Patent Document 6 discloses a variator having two chambers in which a shaft or an eccentric shaft is fixedly attached to a support in the chamber. All of the other chamber toroidal discs and rollers can be displaced in the axial direction, i.e. in the direction of the axis of rotation of the toroidal disc, so that the position of the chamber rollers is reliably defined and the contact pressure Is guaranteed.

  Patent Document 7 is known for attaching a support body to a long hole of a yoke that is oriented transversely to the rotational axis of a toroidal disk for installation. When the contact pressure acts on the roller and the support body, the support body is pressed into the end position toward the outside in the elongated hole, and as a result, the position shown in the drawing of this document matches the operating position.

  Japanese Patent Application Laid-Open No. 2004-151867 is known for providing a bearing between the support and the adjustment piston of the adjustment unit that allows the support to be displaced in the direction of the toroidal disk. In this case, the elastic connection between the support and the adjustment piston is made via a tie rod. This eliminates the need to use an eccentric shaft. As another solution, Patent Document 9 is known.

US Pat. No. 4,453,427 U.S. Pat. No. 4,484,487 European Patent Application No. 1245865A2 US Pat. No. 6,152,850 JP-A-6-280958 European Patent No. 0780599B1 US Pat. No. 6,117,043 German Patent Application Publication No. 10034454A1 German Patent Application Publication No. 10148399A1

  It is an object of the present invention to provide a continuously variable variator for a toroidal transmission that includes an alternative and / or improved method for ensuring the contact pressure of the toroidal transmission.

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

  According to the invention, the bearing unit is provided between the support and the components adjacent thereto. The adjacent component is a support device for the support, preferably a housing or a yoke, which coordinates the movement of the supports of the variator chamber.

  The bearing unit has a degree of freedom of displacement. The degree of freedom of displacement ensures that the support is displaced relative to adjacent components, 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 rotational axis (Z-Z) of the toroidal disk. Therefore, according to the present invention, the distance from the one or more toroidal disks to the support, that is, similarly to the rollers, is changed in a state where the displacement of the support coincides with the degree of freedom of displacement. This can affect the contact pressure between the roller and the one or more toroidal discs, or the contact pressure can be guaranteed by the degree of freedom of displacement. The displacement according to the degree of freedom of displacement can be performed regardless of the force against the frictional force or by applying an energy storage device (accumulated as a spring force). In this case, the displacement can be limited by a fixed stopper or an adjustable stopper.

  At the same time, the bearing unit supports the support in the direction of the axis (XX) relative to the adjacent components. The direction of the support means of the axis (XX) and therefore relative to the adjacent components depends on the operating position of the variator, and the support is pivoted about the axis (YY) over the course of adjusting the variator. It changes by things. The axes (xx), (YY) and (ZZ) form in particular an orthogonal system fixed to the vehicle. In this case, the axis (xx) coincides with the axis (XX) at the position of the gear ratio i = −1 of the variator. For various transmission ratios, the axis (XX) is pivoted about the axis (YY) with respect to the axis (xx).

  By means of the present invention, which secures the support means in the direction of the axis (XX), optimum power transmission is guaranteed for the variator. In particular, the adjustment of the variator reliably prevents changes in the contact pressure between the roller and the toroidal disc.

  Thus, according to the present invention, an alternative to the known solutions described in the above-mentioned patent documents is provided to ensure the contact pressure. (In addition to the present invention, it is also possible to use further solutions known from the above-mentioned patent document or another patent document without departing from the scope of the present invention).

  In the maximum turning of the support centered on the 30 ° axis (YY) taken as an example, even if the degree of freedom of displacement is not directed in the direction of the axis (ZZ) for all of the turning movements, the turning Proved that the displacement in the direction of the toroidal disk is guaranteed when the degree of freedom of displacement has only one component in the direction of the axis (Z-Z). The same applies under some circumstances to absorb the bearing force in the direction of the axis (XX).

The bearing unit is preferably a multi-functional structure, i.e. according to this refinement of the invention, in addition to the degree of freedom of displacement, the bearing unit allows the support to rotate about the longitudinal axis of the support. Assured, the rotation is necessary, in particular, within the range of continuously variable adjustment of the transmission ratio of the variator. This makes it possible to provide a particularly simple and compact variator. In this case, identical bearing elements such as the bearing body and the bearing surface are
-Guidance in the direction of freedom of displacement-Support in the direction of the axis (XX)-Preferably used for guaranteeing rotation of the support about the axis (YY).

  According to a development of the toroidal transmission according to the invention, the bearing unit has at least one bearing surface. In this case, the bearing surface is oriented transverse to the axis (XX). The force acting on the roller and the support in the direction of the rotation axis (XX) of the roller is supported by the bearing unit on the bearing surface. For this purpose, at least one bearing body, in particular a sliding body or a rotating body, can be arranged between the support body and the components adjacent to it and on the bearing surface to absorb the forces mentioned above. Supported. In movement according to the degree of freedom of displacement, the bearing body slides along or rotates relative to the bearing surface. The bearing surface is a multi-functional structure because, on the one hand, the bearing surface functions to absorb the aforementioned forces, and on the other hand, the bearing surface supports the support of one or more toroidal disks. This is because it functions as a guide surface for moving in the direction.

  A particularly simple refinement of the toroidal transmission according to the invention is characterized in that the bearing unit has a bearing hole, for example an elongated hole. The lateral (long) boundary of the bearing hole or slot is formed by the bearing surface. In order to move the support in the direction of freedom of displacement, the bearing body slides along the bearing surface and along the bearing hole. In an alternative refinement, the bearing body has an arcuate outer contour and rotates on the bearing surface. The bearing body is held (substantially) free of play in a direction perpendicular to the degree of freedom of displacement, or is held by a suitable fit, or (US Pat. No. 6,117,043). As well as play), which is preferably overcome in the operating position as a result of the force acting on the support.

  According to another aspect of the invention, the bearing hole is assigned to the support while the yoke has a journal. A bearing body designed as a bearing ring is rotatably mounted on the journal, in particular by interconnection of the rotating bodies. The assignment of bearing holes to the support has the advantage that the bearing holes are swiveled by turning the support to adjust the transmission ratio of the variator. This results in the bearing surface being oriented in a cross section with respect to the axis (XX), irrespective of the turning angle, and thus ensuring an optimum support of the force.

  In an alternative refinement, according to another variant of the invention, the bearing hole is assigned to the yoke while the support has a journal. A bearing body designed as a bearing ring is rotatably mounted on the journal, in particular by interconnection of the rotating bodies.

  Preferably, the inner surface of the bearing ring is properly matched to the rotating body, while the outer contour of the bearing ring is, for example, a circular ring-shaped outer surface that ensures that the bearing ring fits easily into the bearing surface of the bearing hole Via the contour, the contact state with the bearing hole is met.

  According to a development of the invention, the support is attached to two adjacent components, in particular the yoke, by means of two bearing units. In this case, each of the two bearing units has a degree of freedom of displacement having at least one component in the direction of the axis (Z-Z). Thus, the two bearing units allow the support to be displaced and / or swiveled in a plane that is oriented in the direction of the rotational axis of the toroidal disk or substantially transverse to the axis (XX). . This makes it possible to produce a linear movement of the support, or a turning.

  According to an alternative refinement, the support is attached to two adjacent components by two bearing units. According to this refinement, one of the two bearing units has a degree of freedom of displacement having at least one component in the direction of the axis (Z-Z), while the other bearing unit is a support at the center of rotation. Is fixed in the direction of the toroidal disk. In this case, the other bearing unit allows only the support to turn, and the rotation axis or center of rotation of the support is determined in advance by the other bearing unit. This is particularly advantageous when the other bearing unit is arranged in the immediate vicinity of the adjustment unit, so that the displacement of the support along the degree of freedom of displacement is related to a small displacement in the area of the adjustment unit. In this case, the center of rotation can be provided directly in the center or area of the bearing unit, or can be provided away from the bearing unit, for example in the area of the adjusting piston of the adjusting unit. A separate bearing unit is preferably provided between the adjustment piston and the support that allows the support to pivot relative to the adjustment piston. In this case, it is particularly advantageous if the center of rotation of this example is provided in the region of another bearing unit. Another bearing unit is, for example, a ball and socket joint. It is also possible for the adjustment piston to apply an axial force only to the support, while providing lateral play for the adjustment movement of the adjustment unit between the support and the adjustment piston. For the different construction of this type of bearing unit, reference is made to US Pat. No. 5,971,886, WO 02/44587, WO 94/94, which is the subject of this application for connecting the adjusting piston to the support. No. 01697 pamphlet and WO 92/11475 pamphlet.

  According to the invention, a rotatable eccentric shaft can be omitted according to a development of the invention. By this measure, the structure of the variator can be simplified, and in particular, the radial mounting portion for the eccentric shaft can be omitted. At the same time, the rigidity of the roller support means is improved. Therefore, according to the present invention, this makes it possible for the roller to be arranged with its axis fixed to the support so as to be rotatable.

  According to a preferred refinement of the toroidal transmission, a bearing journal is provided which functions to support the rollers radially with respect to the support. In this case, the bearing journal can be fixed to the support, otherwise fixed to the roller and connected. In this case, the bearing journal can be connected integrally with the above-described component, can be inserted into the above-described component, and / or can be connected to the above-described component via a fixing means or by adhesive or active connection.

  According to another embodiment of the present invention, the rotating body that functions to support the force acting on the roller in the direction of the rotation axis (XX) of the roller is disposed between the support body and the rotating body. Rotate along the bearing disk. This bearing disk can be selected according to the rotation conditions, in particular with regard to material, hardness, surface quality and manufacturing accuracy.

  According to an alternative refinement of the invention, the rotating body described above rotates directly along the operating surface of the support. According to this embodiment, the number of necessary components can be reduced. As a result, the facility cost can be reduced, and the function can be improved by not adding a contact surface.

  The bearing hole preferably has an arc-shaped inner contour in a longitudinal section (planes XX, YY). The radius of the inner contour approximately corresponds to the diameter of the bearing hole. This is advantageous if the bearing unit is intended to allow pivoting of the support relative to adjacent components, in particular the yoke, because the bearing body is in this case arcuate. This is because it can turn along the inner contour.

  Alternatively or additionally, it is conceivable that the bearing surface or path of travel is a curved or arcuate structure in the projection plane defined by the axes (ZZ) and (YY). This is the case when the support is supported to the adjacent yoke via two bearing units, and one bearing unit has no degree of freedom of displacement and forms the center of rotation of the support. It is advantageous. In this case, the support moves around the center of rotation in the region of the bearing unit having a degree of freedom of displacement along the arcuate bearing surface or the movement path.

  The distance between the bearing surfaces is preferably reduced in the direction of the axis (Z-Z). In this way, it is possible to improve the adhesion, particularly in the state of approaching the toroidal disk. Further, by reducing the distance between the bearing surfaces, the centering function at the center position where the distance between the bearing surfaces is at the maximum distance is easily performed under some circumstances. For example, the bearing hole has a slightly oval cross section.

  According to a preferred refinement of the toroidal transmission, the shaft used for mounting the roller in the direction (XX) relative to the support is on both sides of the roller, ie the viewing direction of the axis (XX). In FIG. 2, the support is supported before and after the roller. This is based in particular on the recognition that according to the invention the axis (XX) can be fixed in a fixed position relative to the support. The above support on both sides is particularly stiff. In addition or alternatively, the dimensions of the support can be changed.

  Advantageous developments emerge from the dependent claims, the detailed description of the invention and the drawings.

  Preferred exemplary embodiments of the toroidal transmission according to the invention or parts thereof will be described in more detail below with reference to the drawings.

  The present invention is used in a toroidal transmission for an automobile in which the variator 20 functions to continuously change the transmission ratio between at least one drive toroidal disk and one output toroidal disk. For this purpose, the roller 21 is mounted on the opposite side of the contact surface of the roller 21 with the two toroidal disks. In the exemplary embodiment shown in FIG. 1, the toroidal discs are respectively rotated about an axis oriented perpendicular to the projection plane and are arranged above and below the projection plane (not shown).

  The roller 21 is supported in the radial direction with respect to the 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 accommodated. On the radially inner side, the radial bearing 23 rotates along a journal 24 that is formed concentrically with respect to the axis (XX).

  In addition to the journal 24, the eccentric shaft 22 has another journal 25 formed concentrically with respect to the axis (X'-X '). The axis (X′-X ′) is arranged in parallel to the axis (X-X) and away from it. In the transition region between the journals 24, 25, the eccentric shaft 22 has a circular ring-shaped enlarged portion 26, and the outer diameter of this enlarged portion 26 substantially matches the diameter of the roller 21. The thrust bearing 27 connects between the mutually facing end surfaces of the roller 21 and the enlarged portion 26, and these end surfaces are oriented in a direction perpendicular to the axis (XX). In the exemplary embodiment shown in FIG. 1, the thrust bearing 27 is a thrust ball bearing. The operating surface, which is matched to the ball 28 of the thrust bearing 27, is provided on the end surface of the roller 21 and of the enlarged portion 26, and the operating surface is provided with a suitable surface and advantageous material properties. The ball 28 is stored in a cage 29.

  The eccentric shaft 22 is supported with respect to the support 30. For this purpose, the support 30 has a blind hole in which the radial bearing 31 is accommodated. In the exemplary embodiment shown in FIG. 1, the radial bearing 31 is a needle bearing in which a bush 32 for guiding the needle in the direction of the axis (XX) is inserted between the support 30 and the needle. .

  The eccentric shaft 22 is supported with respect to the support 30 in the direction of the axis (XX) via a thrust bearing 33, in this case a needle bearing, and the thrust bearing 33 is transverse to the axis (XX). Acting between the mutually facing end faces of the support 30 and of the enlarged part 26. In the exemplary embodiment shown in FIG. 1, the needle of the thrust bearing 33 rotates directly along the enlarged portion 26 and on the rolling disk 34 supported by the support 30.

  In the longitudinal section shown, the support 30 has a base leg 35 on which the eccentric shaft 25 is mounted approximately in the middle, and two parallel side legs 36 between which the eccentric shaft 22 and the roller 21 are at least partially disposed. , 37 and a substantially U-shaped structure. In the end region located on the opposite side of the base leg 35, each of the side legs 36, 37 has a coaxial or continuous portion or journal 38, 39 oriented outwardly and parallel to the base leg 35. Have.

  The journals 38, 39 at least partially have cylindrical circumferential surfaces 40, 41 that function as inner bearing surfaces of the bearing units 42, 43, respectively.

  In the embodiment shown in FIG. 1, the bearing units 42, 43 are designed with rotating bodies 44, 45, in this case needles, that rotate along the circumferential surfaces 40, 41. The rotating bodies 44 and 45 rotate radially outward along bearing bodies 46 and 47 that guide the rotating bodies 44 and 45 in the direction of the axis (XX) through the collar on one side or both sides. The bearing bodies 46, 47 are formed concentrically with the axis (Y-Y) and have a spherical, in particular partly circular outer contour in the longitudinal section, the center point of the partial circle being the axis (Y-Y) ). The axial fixing of the bearing unit 42 takes place via a fixing element 48, which according to FIG. 1 is designed as a fixed disk supported by the bearing body 46 and the journal 38. The bearing unit 43 is fixed in the axial direction via a disk body 49 fixed to the journal 39, and the bearing body 47 is supported by the journal 39. The interlocking of the rotational movements of the plurality of supports 30 about the axis (Y-Y) is achieved through the disk body 49 by connecting a coupling means such as a cable around the circumferential surface of the disk body 49. Done.

  The outer peripheral surfaces of the bearing bodies 46 and 47 are accommodated in the recesses 50 and 51 of the yokes 52 and 53, respectively, by appropriate fitting with play or by press-fitting. In the longitudinal cross-sectional view shown in FIG. 1, the recesses 50 and 51 have a straight contour.

  The connection between the yokes 52 and 53 and the support body 30 via the bearing units 42 and 43 enables relative rotation about the axis (YY). For this reason, the bearing bodies 46 and 47 are connected to the yoke. 52 and 53 are arranged at fixed positions. Furthermore, the above-described connection enables the yokes 52 and 53 to pivot relative to the support body 30 about the axis oriented perpendicular to the axes (xx) and (YY). Inside, the angle between the longitudinal axis of the support 30 and the longitudinal axes of the yokes 52, 53 changes. In such turning, the bearing body rotates along the recesses 50, 51 having circumferential surfaces in the direction of the partially circular contour.

  The yokes 52, 53 function to coordinate the movement of the adjacent support 30 in the variator chamber. In order to work together, the two supports 30 and the yoke 52 form a substantially parallelogram, and the angle of the parallelogram changes with adjustment. The yokes 52, 53 are supported by appropriate attachment to components fixed to the housing.

  The support 30 and the eccentric shaft 22 have suitable flow paths 54 for supplying lubricating oil to the bearing units 23, 27, 31, 33, 42, 43.

The variator 20 according to the invention is integrated in any desired toroidal transmission, for example in any desired transmission of IPC classification F16H037 / ^* . For a transmission with a variator, it is only an example, but see US Pat. No. 6,059,685, DE 10040039A1 and DE 10121042C2. .

  The interlocking of the plurality of supports 30 is only an example, but please refer to German Patent Application Publication No. 10206200A1 and unpublished DE 10309569.1 of the present applicant. By way of example, the applicant's unpublished DE10233089.1, DE10233091.3 and DE10233090 are described by way of example to allow and adjust the contact pressure between the roller 21 and the toroidal disk by appropriately displacing the toroidal disk. Please refer to. In order to adjust the variator, the support 30 can be displaced in the direction of the axis (YY) by means of a suitable adjustment unit. In this connection, as regards structure, adjustment and function, reference is made, for example, to the applicants' unpublished DE 10236619.5, DE 10300569.2-14 and DE 10308496.7.

  The above mentioned patent documents are cited for the subject matter of the present application.

The improvement according to FIG. 1 allows the following movements:
-After providing the adjusting unit, the support 30 can be moved in the direction of the axis (YY).
-The bearing units 43, 42 allow the support 30 to pivot about the axis (YY).
The roller 21 is attached to the eccentric shaft 22 so as to be rotatable about the axis (XX). This rotational motion correlates with the rotational motion of the assigned toroidal disc.
The eccentric shaft 22 is pivotable, thus making it possible to change the distance between the roller 21 and the toroidal disc.

  In the subsequent drawings, the same reference numbers are used for components that basically match the components of FIG. 1, and the same reference numbers are assigned to the symbols that indicate the associated shapes.

  In the exemplary embodiment shown in FIG. 2, which is a modification of FIG. 1, the bearing unit 43a including the associated areas of the support 30a and the yoke 53a is designed according to FIG. This bearing unit is preferably a bearing unit disposed adjacent to an adjustment unit for displacing the support 30a. In the region of the other bearing unit 42a, the support 30a is designed without a journal 38. The side leg 37a of the support 30a has a recess that is oriented in the longitudinal direction of the support 30a and forms a bearing hole 60a. The related yoke 52a is provided with a bent portion, and an end region of the bent portion forms a journal 61a. The journal 61a is attached to the bearing hole 60a via the bearing unit 42a. In this case, the rotating body 44a rotates radially inward along the journal 61a and rotates radially outward in the bearing body 46a. The bearing body 46a is accommodated in the bearing hole 60a of the support body 30a by appropriate fitting with play or by press fitting. In the longitudinal sectional view shown in FIG. 2, the journal 61a and the bearing hole 60a have a mirror-symmetric structure with respect to the axis (YY).

  FIG. 3 shows a cross-sectional view of the bearing hole 60a. The bearing body 46a abuts against the bearing surfaces 62a and 63a of the bearing hole 60a in the direction X (parallel to the axis (XX)). The bearing hole 60a is designed as a long hole in the direction of the axis (Z-Z). Accordingly, the bearing bodies, that is, the play 64a and 65a in which the journal 61a can be displaced with respect to the support body 30a are formed in the direction ZZ between the bearing hole 60a and the bearing body 46a, respectively. Each of the play 64a and 65a is preferably between 1 and 3 or approximately 2 millimeters. In this case, the bearing surfaces 62a and 63a can be oriented parallel to each other and parallel to the axis (Z-Z), can be curved structures, or the exemplary embodiment shown in FIG. Therefore, the bearing body 46a can be brought into close contact with or pressed against the bearing hole 60a by the movement from the center position shown in FIG. 3 in the direction of the axis (Z-Z). It will become stronger.

  As described above, as a result of enabling the degree of freedom of displacement in the direction of the axis (Z-Z), the support 30a is placed on the surface that crosses the axis (XX) and passes through the axis (Y-Y). Can be swiveled. Such turning is performed around the rotation center 66a of the support 30a that is arranged on the axis (YY) and substantially in the region of the bearing unit 43a. The rotation center 66a preferably coincides with the center point of the partially circular outer contour of the bearing body 47a. During the course of the swivel motion described above, the distance from the toroidal disk to the roller can be changed, thus providing a method for omitting the eccentric shaft 22. As a result, according to the exemplary embodiment shown in FIG. 2, the radial bearing 31 and the thrust bearing 33 can be omitted. The journal 24a is preferably fixedly connected to the support 30a. In this case, the journal 24a is formed integrally with the support 30a, is connected to the support 30a actively or by adhesion, or is connected via suitable fixing means.

  In the exemplary embodiment shown in FIG. 2, the operating surface of the thrust bearing 27a located on the opposite side of the operating surface of the roller 21a is formed by a bearing disk 67a, which has a circular ring-like structure. , Is supported by the journal 24a radially inward, and forms a rolling surface for the thrust bearing 27a in a region on one end side, and on the opposite end side, an axis ( XX).

  According to the embodiment of FIG. 2, the guide of the lubricating oil can obviously be simplified, because the lubrication of the radial bearing 31 and the thrust bearing 33 is not required and the lubricating oil is used as a support 30a. This is because it is not necessary to pass through to the eccentric shaft.

  In the movement around the rotation center 66a, the movement of the bearing surfaces 62a and 63a in the circular path according to FIG. 4 is generated by the movement in the displacement direction with a degree of freedom. Match the distance to.

  According to the exemplary embodiment shown in FIG. 5, the bearing surfaces 62a, 63a in the longitudinal section of the bearing hole are designed to coincide with the outer contour of the bearing body 46a, in particular partially circular. . Thus, the bearing body 46a is guided in the direction of the axis (Y-Y) while the bearing body 46a can be turned with respect to the support body 30a.

  According to the exemplary embodiment of the invention shown in FIG. 6, at least one linear guide bearing 69b can be connected between the bearing body 46b and the associated bearing surfaces 62b, 63b. The linear guide bearing 69b is designed as a sliding bearing or a rolling bearing. In the exemplary embodiment shown in FIG. 6, a rolling bearing having a cylindrical roller, a spherical roller, a ball or a needle as a rotating body, and having a cage as required is used as the linear guide bearing 69b.

  FIG. 7 shows an alternative modification of the bearing hole 60c, in which the bearing surfaces 62c and 63c are linear or the section of the bearing hole 60c has a larger radius of curvature. Designed to.

  In the exemplary embodiment shown in FIG. 8, otherwise, in a form essentially corresponding to FIG. 2, the journal 24d is formed separately from the support 30d. The support 30d has a hole 70d into which the journal is inserted and fixed (preferably by press-fitting). Since the bearing disk 67d is integrally formed with the support 30d, the thrust bearing 27d is directly supported with respect to the support 30d, and the operating surface of the thrust bearing 27d is formed by the support 30d.

  In the exemplary embodiment shown in FIG. 9, the journal 24e is fixed to the roller 21d and in this case is integrally connected. Due to the axial mounting part 27e designed according to FIG. 8, the radial bearing 23e acts between the journal 24e and the support 30e. The radial bearing 23e operates on the journal 24e on the radially inner side. On the radially outer side, the radial bearing 23e operates in the hole 70e of the support 30e. The radial bearing 23e and the roller 21e are fixed in the axial direction via a fixing element 71e, in this case, a fixing ring. One side of the fixing element 71e is supported by a groove of the journal 24e, and the other side is a support. 30e abuts. In the exemplary embodiment shown in FIG. 9, the disk body 49 is omitted. Instead of (or in addition to) the disk body 49, the rotation of the support 30e about the axis (Y-Y) is performed via interlocking means designed as a cable. In the region of the unit 42e or in the region of the bearing hole 60e, it is partially wrapped around the support 30e. For this purpose, a groove 72e for receiving the interlocking means is formed on the circumferential surface of the support 30e in the region of the bearing hole 60e. In this case, the interlocking force can be transmitted actively and / or by frictional resistance.

  The exemplary embodiment shown in FIG. 10 essentially corresponds to the exemplary embodiment shown in FIG. 2, in which the journal 24f is integrally formed with the support 30f and the bearing A disk 67a is formed integrally with the support 30f (see the embodiment of FIG. 8).

  In the exemplary embodiment according to FIG. 11, which is a modification of FIG. 10, the bearing hole 60g is a modification of FIG. 3, and in particular, the portion of the bearing hole arranged on the left side of the axis (Z-Z) Simplified to be omitted. Therefore, the bearing body 46g is supported only by the bearing surface 62g facing the central drive shaft 73g. In the simplest example, in the end region of the side leg 37g facing away from the base leg 35g, the support 30g is oriented parallel to the base leg 30g and in the opposite direction from the roller 21g. It has only one continuous part 74g facing. The bearing body 46g contacts the continuous portion 74g in the region of the bearing surface 62g. In this case, the operation surface for the bearing surface 62g has a linear structure or a curved structure in the direction of the degree of freedom of displacement (Z) (see FIG. 4). The contour of the working surface in the direction of the axis (YY) is in this case a linear structure or matched to the contour of the bearing body 46g (corresponding to FIG. 5). In the cross section in the direction of the axes X and Z, the operation surface has a linear structure or a curved structure.

  This improvement is based on the recognition that during the operation of the toroidal transmission, the roller 21g is pushed in the opposite direction to the central drive shaft 73g, so that the support via the bearing surface 62g is sufficient.

  The exemplary embodiment shown in FIG. 12 essentially corresponds to the exemplary embodiment shown in FIG. 8, in which the support 30h is a closed annular structure in a cross section in the direction of the axes X and Y. The roller 21h is disposed inside the support 30h. For this reason, the end of the bearing hole 60h facing in the direction opposite to the base leg 35h is connected to the end of the side leg 36h facing in the direction opposite to the base leg 35h via the connection web 75h. Connected. In this case, the connecting web 75h is oriented substantially parallel to the base leg 35h. As a result, the rigidity of the support 30h and the bearing hole 60h is improved.

  According to FIG. 13, which is a modification of the exemplary embodiment shown in FIG. 12, the journal 24i passes through the roller 21i and in the end region protruding from the roller in the direction of the central drive shaft 73i, the connecting web 75i. Against. The journal 24i has a first sub-region fixedly connected to the support 30i, a second sub-region abutting on the radial bearing 23i for supporting the roller 21i on the radially outer side, and a radial play. And a third sub-region that is inserted and fixed in the hole of the connecting web 75i through the central hole of the roller 21i, and the three sub-regions described above are in the direction of the axis (X) in the order described above. Arranged side by side. Alternatively, the journal 24i in the support 30i or in the connecting web 75i and the assigned mating portion may have a non-circular cross-section in the first and third sub-regions in order to fix against rotation. Conceivable.

  According to the exemplary embodiment shown in FIG. 14, the connecting web 75j is not integrally formed with the support 30j but is designed as a separate component, which is also in the region of the bearing hole 60j. In the end region of the side leg 36j, it can be fixedly connected to the support 30j actively, by gluing, by frictional resistance or via connecting means. On the side facing the support 30j, the connecting web 75j has a journal 76j. On the side facing the connecting web 75j, the journal 24j has a central blind hole, and in the mated state, the journal 76j fits precisely in the central blind hole to support the journal 24j against the connecting web 75j. To be accommodated.

  This is also possible when the connecting web 75k and the support 30k are in an integral structure (see FIG. 15).

Another feature, especially
-The shape of the illustrated component,
-Related dimensions of the illustrated plurality of sizes of the same or different components;
-The relative arrangement of the components of each other-The operational connections of the components of each other can be read from the drawings.

  It is also possible to combine the features of the different improvements shown in the different drawings with the features of the prior art improvements mentioned.

It is a fragmentary sectional view of the variator by a 1st embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is a fragmentary sectional view of the variator by a 2nd embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. For example, according to FIG. 2, it is a drawing of a bearing unit between a yoke and a support body as seen from a cross section in a direction transverse to the axis (YY). It is a longitudinal cross-sectional view of the bearing hole which has the movement path | route and bearing surface which were seen from the direction of the axis line (XX). It is longitudinal direction sectional drawing of the bearing unit seen from the direction of the axis line (ZZ). It is sectional drawing of the bearing unit which has a linear guide. It is a fragmentary sectional view of a bearing unit. It is a fragmentary sectional view of the variator by a 3rd embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is the fragmentary sectional view of the variator by a 4th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is the fragmentary sectional view of the variator by a 5th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is a fragmentary sectional view of the variator by a 6th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is the fragmentary sectional view of the variator by a 7th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is a fragmentary sectional view of the variator by an 8th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is the fragmentary sectional view of the variator by a 9th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk. It is the fragmentary sectional view of the variator by a 10th embodiment seen from the section of a transverse direction to the axis of rotation of a toroidal disk.

Claims (30)

A continuously variable transmission variator for a toroidal transmission having a toroidal disk that rotates about an axis (Z-Z), wherein a roller (21) is centered on an axis (XX) relative to a support (30) A continuously variable transmission variator, wherein the support (30) is rotatably mounted about an axis (YY),
The support (30) is attached to at least one adjacent component by a bearing unit (42), the bearing unit comprising:
-Having a degree of freedom of displacement having at least one component in the direction of said axis (Z-Z);
A continuously variable transmission variator, characterized in that the support is supported in the direction of the axis (XX) with respect to the adjacent components.   The degree of freedom of displacement is directed to a transverse plane with respect to the axis (XX) independently of the turning of the support (30) about the axis (YY). The variator according to claim 1.   3. The variator according to claim 2, wherein the adjacent component is a yoke (52, 53) connecting a plurality of supports (30).   The rotation of the support (30) about the axis (YY) is guaranteed by the bearing unit (42) in addition to the degree of freedom of displacement. Variator.   The variator according to claim 4, wherein a sub-region of the yoke (52) assigned to the bearing unit (42) is arranged to be displaceable in the direction of the axis (YY). The bearing unit (42) has at least one bearing surface (62, 63);
a) the bearing surface is oriented transverse to the axis (XX);
b) A force directed in the direction of the axis (XX) and acting on the roller (21) and the support (30) is supported by the bearing surface;
c) Variator according to claim 5, characterized in that the bearing body (46) of the bearing unit (42) slides or rotates along the bearing surface according to the degree of freedom of displacement during movement.   The bearing unit (42) has a bearing hole (60), and a lateral boundary of the bearing hole is formed by the bearing surface (62, 63). In the bearing hole, the bearing body (46) The variator according to claim 6, wherein the variator is held without play in a lateral direction with respect to the degree of freedom of displacement.   The support (30) has the bearing hole (60), the yoke (52) has a journal (61), and a bearing body (46) designed as a bearing ring rotates relative to the journal. The variator according to claim 7, wherein the variator can be attached.   The yoke (52) has the bearing hole (60), the support (30) has a journal (38), and a bearing body (46) designed as a bearing ring rotates relative to the journal. The variator according to claim 7, wherein the variator can be attached.   The support (30) is attached to two adjacent components (yokes 52, 53) by two bearing units (42, 43), each of the two bearing units (42, 43) being The variator according to any one of claims 1 to 9, wherein the variator has a displacement degree of freedom having at least one component in a direction of the axis (Z-Z).   The support (30) is attached to two adjacent components (yokes 52, 53) by two bearing units (42, 43), the one bearing unit (42) being at least one The other bearing unit (43) has the support (30) at the center of rotation (66) with respect to the axis (Z-). The variator according to claim 1, wherein the variator is fixed in the direction of Z).   The axis (XX) to which the roller (21) is rotatably mounted is disposed at a fixed position with respect to the support (30). The variator described in 1.   A bearing journal (24) is fixedly connected to the support (30) or the roller (21) to support the roller (21) in the radial direction with respect to the support. The variator according to any one of claims 1 to 12.   A bearing disk (67) in which a rotating body of a thrust bearing (27) between the roller (21) and the supporting body (30) is disposed between the supporting body (30) and the rotating body (28). The variator according to any one of claims 1 to 13, wherein the variator is rotated along the axis.   The rotating body of a thrust bearing (27) between the roller (21) and the support (30) rotates directly along the operating surface of the support (30). The variator according to any one of ˜13.   16. Cable according to any one of the preceding claims, characterized in that a cable used to synchronize the adjusting movement of a plurality of supports (30) is wound directly around the support (30). Variator.   The variator according to claim 16, characterized in that the cable is wound around the support (30) in the region of the circumferential surface of the bearing hole (60).   The support (30) has essentially an E-shaped cross section, and at least one of the outer horizontal legs (36, 37) of the E-shaped cross section forms a bearing hole (60), and the central horizontal leg The variator according to any one of claims 13 to 17, characterized in that forms the bearing journal (24) for the roller (21).   19. A variator according to any one of the preceding claims, characterized in that the bearing hole (60) has an arcuate inner contour in the longitudinal section.   The bearing surface (62, 63) or the movement path of the bearing body (46) is a curved structure in a projection plane defined by the axes (ZZ) and (YY). Item 20. The variator according to any one of Items 11 to 19.   The bearing surface (62, 63) or the movement path of the bearing body (46) has a radius substantially matching the distance from the rotation center (66) to the bearing surface (62, 63) or the movement path, 21. The variator according to claim 20, wherein the projection surface defined by the axes (ZZ) and (YY) has an arcuate structure.   The distance between the bearing surfaces (62, 63) opposite to each other decreases in the direction of the axis (Z-Z). Variator.   23. A variator according to any one of claims 6 to 22, characterized in that at least one bearing surface (62, 63) has an arcuate structure in the section of the bearing hole (60).   A linear bearing (69) has bearing surfaces (62, 63) assigned to the support (30) or to the adjacent component (yoke 52); and the adjacent component (yoke 52) or the support ( 30). The variator according to any one of claims 6 to 23, wherein the variator is connected to 30).   The yoke (52) has a bearing journal (61), and a bearing ring (46) having a spherical outer surface that rotates along the bearing surfaces (62, 63) of the support (30). The variator according to any one of claims 1 to 24, wherein the variator is rotatably mounted and the bearing surface extends in the direction of the axis (Z-Z).   The shaft (journal 24) used for attaching the roller (21) to the support (30) is supported on the support (30) on both sides of the roller (21). The variator according to any one of claims 12 to 25.   The bearing unit (42g) only supports the support (30g) on one side with respect to the adjacent component (yoke 52g), and the support action acts in the direction of the axis (XX). The variator according to any one of claims 1 to 26.   The said support body (30) forms an installation unit with the said roller (21) and the said thrust bearing (27) connected to the middle, The one of Claims 1-27 characterized by the above-mentioned. Variator.   The variator according to any one of claims 1 to 28, wherein a ball, a tapered roller or a barrel is used as the rotating body (28) of the thrust bearing (27).   A toroidal transmission comprising a continuously variable variator (20) according to any one of the preceding claims.

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