JP2014508905A - Transmission - Google Patents

Abstract

  The present invention relates to an input shaft provided with an input shaft rotation axis, an adjustable eccentric drive device arranged corresponding to the input shaft, an output shaft provided with an output shaft rotation axis, and arranged corresponding to the output shaft. The freewheel device, the eccentric drive device and the freewheel device being adjustable between a minimum length and a maximum length, at least one first lever, at least one drive rod and a fixed length A coupling device for driving connection with at least one second lever with a maximum length of the first lever of the second lever for improved efficiency and / or increased durability The present invention relates to a continuously variable transmission for a power train of an automobile driven by an internal combustion engine, which corresponds to a length.

Description

  The present invention relates to an input shaft having an input shaft rotation axis, an adjustable eccentric body driving device arranged corresponding to the input shaft, an output shaft having an output shaft rotation axis, and an output shaft Correspondingly arranged freewheel device, eccentric drive and freewheel device with at least one first lever, at least one drive rod and fixed adjustable between a minimum length and a maximum length The present invention relates to a continuously variable transmission for a powertrain of an automobile driven by an internal combustion engine, in particular, having a coupling device that is driven and connected by at least one second lever having a length.

  In German Offenlegungsschrift 10 243 535, a continuously variable transmission is known. The transmission device includes at least one drive shaft and a driven shaft that are coupled to each other according to a drive type, and is provided at least on the drive shaft that is coupled to each other via a coupling element such as a coupling device. One eccentric body driving device and at least one freewheel device provided on the driven shaft are used. In this transmission device, the eccentric drive unit has a guide region that is arranged eccentrically with respect to the rotation axis of the drive shaft. In order to provide a continuously variable transmission in which the eccentric body component is pivotally supported in this guide region and can be produced in this eccentric body member in a particularly simple and economical manner. Is rotatably supported. In addition, the design aspect of the transmission allows for a simple structure of the transmission, but still allows a large output to be transmitted, so that the transmission can be used in an automobile powertrain. is there. In addition, the given structure ensures the kinematics and dynamics of the transmission, which easily prevents free inertial forces (freie massenkraefte) or free moments (freie Momente) based on reciprocating transmission or mechanical parts It has become. Furthermore, the transmission device is adapted to enable energy saving operation of the automobile.

  The object underlying the present invention is to improve the efficiency and / or improve the durability in a transmission of the type mentioned at the outset.

  The object is to provide an input shaft with an input shaft rotation axis, an adjustable eccentric drive device arranged corresponding to the input shaft, an output shaft with an output shaft rotation axis, and an output shaft. Correspondingly arranged freewheel device, eccentric drive and freewheel device with at least one first lever, at least one drive rod and fixed adjustable between a minimum length and a maximum length A coupling device for driving connection with at least one second lever having a length, in particular the maximum length of the first lever corresponds to the length of the second lever, in particular an internal combustion engine This is achieved with a continuously variable transmission for the powertrain of a driving vehicle.

  Infinitely variable transmissions (English: Continuously Variable Transmission, CVT) enable infinitely adjustable shifting. The continuously variable transmission device is a transmission device that shifts uniformly, in which the ratio of the rotation speeds of the input shaft and the output shaft, that is, the gear ratio can occupy many values within a predetermined range. The transmission can also include a stationary state of the output shaft or a reversal of the rotational direction. The continuously variable transmission may be disposed between the internal combustion engine and the drive wheel in the automobile powertrain. The input shaft of the transmission may be drivingly connected to the output shaft of the internal combustion engine, in particular the crankshaft. The output shaft of the transmission may be drivingly connected to the drive wheel.

  The first lever may be a crank. The length of the first lever may be adjustable by an eccentric body driving device. The second lever may be a crank. The second lever may have a fixed length. The length of the second lever may correspond to its maximum length of the first lever. In another adjustment position where the first lever does not have a maximum length, the length of the second lever may be greater than the length of the first lever. The drive rod may be a coupling device or a coupling rod. Driving is performed from the input shaft to the output shaft through the first lever, at least one drive rod and the second lever. The drive rod can perform a combined translational and rotational movement during operation of the transmission. The drive rod can perform a swiveling motion during operation of the transmission. The drive rod can serve to switch the rotational movement to a rocking movement. The drive rod can serve for transmission of rotational movement.

  The freewheel device can reciprocate during operation of the transmission. The freewheel device can perform a motion without switching the direction when the transmission is operated. The transmission can have a plurality of drive rods. The plurality of drive rods may be arranged in pairs. The freewheeling device can have at least one freewheel. The freewheel device can have a plurality of freewheels. The freewheel device can entrain the output shaft when the peripheral speed of the freewheel is higher than the peripheral speed of the output shaft. The plurality of freewheels can be accompanied by shifting the output shaft in time. The plurality of freewheels can be accompanied by overlapping the output shafts in time. Multiple freewheels can simultaneously entrain the output shaft. The plurality of freewheels can be free-run simultaneously (frei laufen) without accompanying the output shaft. At the same time, the first free wheel can be driven along the output shaft, and the second free wheel can travel freely without being accompanied by the input shaft.

  The freewheel may be a clamped roller type freewheel. The freewheel may have a star-shaped inner member. The freewheel may have clamping rollers. The freewheel may have an outer ring. The freewheel may be switchable.

  The eccentric body drive device may have a rotatable eccentric body element. The eccentric element may be rotatable relative to the input shaft. The eccentric body element may have an inner dentition. The addendum circle of the inner dentition of the eccentric body element can serve for the pivotable support of the eccentric body element. The eccentric body drive device may have a pinion shaft. The pinion shaft may have an outer dentition. The addendum circle of the outer tooth row of the pinion shaft can serve for the pivotable bearing of the pinion shaft. The outer dentition of the pinion shaft can mesh with the inner dentition of the eccentric element. The rotation of the pinion shaft can bring about the rotation of the eccentric element. The rotation of the pinion shaft or the rotation of the eccentric body element can bring about the extension or shortening of the first lever.

  With the transmission device according to the present invention, when the length of the first lever is the maximum, the turning motion of the first lever can be converted into the turning motion of the second lever. Therefore, in the free wheel device, it is possible to form a rotating motion that circulates without switching the rotation direction. Load switching can be omitted. Oscillating motion can be omitted. Switching between the entrained state and the freewheel state in the freewheel device can be omitted. The freewheeling device can be operated in entrained and / or freewheeling conditions over a relatively long period of time. The operation of the eccentric drive unit is simplified. The load on the eccentric drive is reduced.

  The transmission gear ratio i may be adjustable between ∞ ≧ i ≧ 1. When the transmission gear ratio i is i = ∞, motion transmission from the input shaft to the output shaft is not performed. When the transmission gear ratio i is i = 1, the maximum motion transmission from the input shaft to the output shaft is performed. The output shaft can be driven at the same rotational speed as the input shaft or at a lower rotational speed than the input shaft.

  The drive rod includes a first drive rod rotation axis on the eccentric body drive device side, a first drive rod eye on the eccentric body drive device side, a second drive rod rotation axis on the free wheel device side, and a free wheel. A second drive rod eye on the device side, the first lever can be formed between the input shaft pivot axis and the first drive rod pivot axis, and the second lever The output shaft rotation axis and the second drive rod rotation axis can be formed.

  The output shaft rotation axis and the second drive rod rotation axis may be disposed radially inward of the second drive rod eye. The second drive rod eye can surround the freewheel device from the radially outer side. Therefore, in order to rotationally drive the freewheel device, structural preconditions are given. Therefore, the second lever may be configured to be decisively shorter than the conventionally known structure. The radial dimensions of the freewheel device are not limited. Therefore, the adjustable first lever may be similarly short. The adjustment area of the first lever may be small. The first lever can have a smaller maximum length. The eccentric body driving device may be configured to be smaller. The required configuration space can be reduced. Can reduce weight.

  The freewheel device may be arranged radially inward of the second drive rod eye. The second drive rod eye can have a larger diameter than the freewheel device.

  An eccentric element may be disposed between the second drive rod eye and the freewheel device. Therefore, a predetermined amount of eccentricity is given between the second drive rod eye and the free wheel device. The second drive rod rotation axis may be spaced from the rotation axis of the freewheel device. The rotation axis of the freewheel device may coincide with the output shaft rotation axis. The distance between the second drive rod rotation axis and the rotation axis of the freewheel device can form a second lever. The second lever may be formed together with the eccentric element. Thus, the second lever can have a small length compared to known structures.

  The eccentric element may have an outer contour and an inner contour, the outer contour may be arranged corresponding to the second drive rod eye, and the inner contour may be arranged corresponding to the freewheel device. The outer contour can have a cylindrical shape. The inner contour can have a cylindrical shape. The outer contour of the eccentric element may be in contact with the inner contour of the second drive rod eye. The inner contour of the eccentric element may be in contact with the outer contour of the freewheel device, in particular the outer wheel of the freewheel.

  When the transmission gear ratio i is i = 1, the second drive rod rotation axis can go around the output shaft rotation axis. When the transmission gear ratio i is i = 1, the second drive rod rotation axis can circulate in the first direction around the output shaft rotation axis and output in the first rotation direction. Axis can be entrained. When the transmission gear ratio i is i = 1, the second drive rod axis can circulate in the second rotation direction around the output shaft rotation axis, and in the second rotation direction, It is possible to realize a free wheel state without accompanying the output shaft. The freewheel device can have a plurality of freewheels. The first free wheel of the plurality of free wheels can circulate in the first rotation direction. The second free wheel of the plurality of free wheels can circulate in the second rotation direction. The first free wheel can circulate in the first rotation direction, and at the same time, the second free wheel can circulate in the second rotation direction.

  Therefore, in summary and in other words, the present invention provides, inter alia, a crank variator with an increased transmission ratio. In this crank variator, the basic geometric and kinematic relationship between the crank mechanism and the special configuration (Sonderkonfiguration) has been expanded. As a result, a shift to a special configuration with high efficiency in the overdrive speed change region is made, so that significant efficiency improvement in a group of cranks is possible. This improvement is very useful in this area, as known crank variators are limited in principle and have low efficiency values in overdrive.

  During the transition to the special configuration, the eccentric radius on the drive side can be adjusted until the magnitude of the eccentric radius on the driven side is achieved. Furthermore, the drive and the driven can be operated at the same rotational speed, and the eccentric radius of the drive side is reduced again. In order to make this possible, it may be necessary to adjust the adjustment region in which the eccentric radius on the drive side is set. The freewheel is tightened once and can no longer be operated at high cycles. This improves the overall service life of the freewheel and thus the overall system robustness. The inertial forces of the individual driven levers result in passing through a singulaere position of the crank mechanism.

  Some peculiarities of a multi-crank variator constructed according to the present invention, for example a six-crank system, may be taken into account during design. In the special configuration of the variator in the case of the gear ratio 1, all the connecting devices of the plurality of crank variators do not transmit force. Depending on the position of each component, a "+" or "-" configuration or configuration of the crank mechanism is realized. A mechanism with a “−” configuration in which the freewheel state is repeated does not transmit force. After leaving the special configuration, the driven lever can be located above the axis spacing plane and / or below the axis spacing plane. In this configuration, the drive and driven side coupling device bearings are required not only for traction but also for coasting depending on the configuration of each crank mechanism. This may be taken into account when designing the bearing.

  In order to achieve 360 ° rotation of the freewheel outer ring in the overdrive special state, the principle of the eccentric body on the driven side can be used. This structural solution allows the mechanism to be shifted to a special configuration with a gear ratio of 1. In a special configuration, the driven device no longer pivots, but rotates around the driven axis.

  On the drive side, no fundamental changes in structure are required. However, the adjustment range can be adjusted according to the basic design conditions. A relatively small driven-side radius can be realized by an appropriate structural principle of the introduction of the secondary-side coupling device force. Accordingly, the adjustment range on the drive side can be reduced accordingly. Thereby, an adjustment unit and a drive shaft can be comprised small and lightweight, and efficiency can be improved in all the operating points. The drive shaft unbalance is also reduced.

FIG. 7 is a diagram showing a crank variator comprising an adjustable drive crank, a coupling device, a driven crank, and a free wheel in a first rotation direction on the free wheel side where the driven shaft is entrained; The crank and the driven crank have the same length. A crank variator comprising an adjustable drive crank, a coupling device, a driven crank, and a free wheel in a second rotation direction on the free wheel side where a free wheel state without accompanying driven shaft is performed. In the figure, the drive crank and the driven crank have the same length. FIG. 7 is a diagram showing a lever / connector arrangement of a crank variator when a driving crank and a driven crank are shifted to a special position having the same length. FIG. 7 shows the lever / connector arrangement of the crank variator in a special position where the drive and driven cranks have the same length after passing through the singular position. FIG. 5 shows the crank variator lever / coupler arrangement after the drive crank has returned to its normal position with a length less than the driven crank. It is a graph regarding the shift transition of a crank variator. It is a graph regarding the gear ratio and efficiency of a crank variator.

  Embodiments of the present invention will be described below in detail with reference to the drawings. From this description, other features and advantages will become apparent. Specific features of this embodiment may be common features of the present invention. Features of the above embodiments linked to other features may be individual features of the present invention.

  FIG. 1 shows a crank provided with an adjustable drive crank 102, a coupling device 104, a driven crank 106 and a free wheel 108 in a first rotation direction 110 on the free wheel side where the driven shaft is entrained. A CVT crank variator 100 is shown. In this embodiment, the drive crank 102 and the driven crank 106 have the same length.

  The crank CVT has an input shaft having an input shaft rotation axis and an output shaft having an output shaft rotation axis. The input shaft rotation axis and the output shaft rotation axis extend in parallel to each other.

  The input shaft is formed as a crankshaft. The input shaft has an offset portion. The input shaft has a shaft portion concentric with the input shaft rotation axis. The input shaft has a crank portion that is radially displaced with respect to the shaft portion. The input shaft has a central hole. This hole extends along the input shaft rotation axis in the radial center of the shaft portion. In the crank portion, the hole opens radially outward. A pinion shaft having an outer dentition is disposed in the hole. The pinion shaft is rotatably supported in the hole by the tip circle of the outer dentition. The pinion shaft is rotatable relative to the input shaft in the hole.

  An eccentric element is disposed in the crank portion of the input shaft. The eccentric element can be rotated relative to the crank portion. The eccentric body element has an eccentric body axis. The eccentric body axis and the input shaft rotation axis extend in parallel to each other. The eccentric body axis and the input shaft rotation axis are spaced from each other. The drive crank 102 is formed such that the eccentric body axis and the input shaft rotation axis are spaced apart from each other. The eccentric body element has an inner dentition. The eccentric element is rotatably supported on the crank portion by a tip circle of its inner tooth row. The eccentric body element is rotatable relative to the crank portion. The outer dentition of the pinion shaft meshes with the inner dentition of the eccentric body element.

  Relative rotation of the pinion shaft relative to the input shaft results in relative rotation of the eccentric body element relative to the crank portion, which in turn results in a change in the length of the drive crank 102. The pinion shaft and the eccentric body element are part of the eccentric body driving device.

  The eccentric drive is adjustable between two end positions. In the first end position, the drive crank 102 has a minimum length. In the first end position, the drive crank 102 has a length of zero. At the first end position, the crank CVT has a gear ratio i of i = ∞. In the second end position, the drive crank 102 has a maximum length. At the second end position, the crank CVT has a gear ratio i of i = 1. This transmission ratio is an overdrive transmission ratio. The overdrive transmission ratio is an extremely long transmission ratio in this relation. FIG. 1 shows the eccentric body driving device at the second terminal position.

  A connecting device 104 is disposed on the eccentric element. The coupling device 104 is arranged in the eccentric body element so as to be rotatable about the coupling device axis on the eccentric body driving device side. The connecting device axis on the eccentric body driving device side coincides with the eccentric body axis of the eccentric body element. The connecting device 104 has a connecting device eye on the side of the eccentric body driving device. The eccentric element has an outer radius. The connecting device eye of the connecting device 104 is rotatably supported on the outer radius of the eccentric element. The coupling device is supported by the rolling bearing in the eccentric body element.

  A freewheel device including a plurality of freewheels 108 is disposed on the output shaft. These free wheels 108 are clamping roller type free wheels having a star-shaped inner member, an outer ring, and a clamping roller effective between the star-shaped inner member and the outer ring. The star-shaped inner member extends across all freewheels 108 of the freewheeling device in the axial direction. The star-shaped inner member forms an output shaft and / or is drivingly connected to the output shaft. The free wheel 108 is disposed concentrically with respect to the output shaft rotation axis. The output shaft rotation axis coincides with the rotation axis of the freewheel 108.

  The outer ring of the free wheel 108 is accommodated in the eccentric body element. The eccentric element has an outer radius with an outer radial axis and an inner radius with an inner radial axis. The inner radius is arranged to be shifted in the radial direction with respect to the outer radius. The inner radius axis coincides with the output axis rotation axis and the rotation axis of the freewheel 108. The inner radial axis and the outer radial axis extend parallel to each other. The inner radial axis and the outer radial axis have a fixed spacing from each other. The driven crank 106 is formed with an interval between the inner radial axis and the outer radial axis.

  The connecting device 104 has a connecting device eye on the freewheel device side. The connecting device 104 includes a connecting rod that firmly connects the connecting device eye on the eccentric body drive device side and the connecting device eye on the freewheel device side. Each of the connecting devices 104 is integrally formed with a connecting rod and a connecting device eye of the connecting device. The coupling device 104 is disposed on the driven-side eccentric element. The coupling device eye on the freewheel device side of the coupling device 104 is arranged on the eccentric element on the driven side. The connecting device 104 is disposed in the eccentric element on the driven side so as to be rotatable about the connecting device axis on the freewheel device side. The freewheel device side coupling device axis coincides with the outer radial axis of the driven side eccentric element. The coupling device eye on the freewheel device side of the coupling device 104 is rotatably supported at the outer radius of the driven-side eccentric element. The coupling device axis and the eccentric body axis have a predetermined distance from each other. The coupling device 104 is supported on the driven-side eccentric element by a rolling bearing, in this embodiment a ball bearing or a roller bearing.

  The connecting device eye on the freewheel device side has a larger diameter than the connecting device eye on the eccentric body drive device side. The connecting device eye on the freewheel device side has a larger diameter than the outer ring of the freewheel 108. The connecting device eye on the freewheel device side is arranged eccentrically with respect to the freewheel 108. The connecting device eye on the freewheel device side is arranged so that the connecting device rotation axis on the freewheel device side is arranged radially inward of the star-shaped inner member of the freewheel 108 compared to the outer ring of the freewheel 108. With respect to the large diameter and the freewheel 108, the coupling device axis on the freewheel device side has an eccentric amount that is disposed radially inward of the star-shaped inner member of the freewheel 108.

  The drive crank 102 and the driven crank 106 have the same length at the positions shown in FIG. When the input shaft rotates, the end portion on the drive crank side of the coupling device 104 is driven to rotate in correspondence with the arrow direction 112. The driving motion is transmitted to the driven end of the coupling device 104 by the coupling device 104. Since the drive crank 102 and the driven crank 106 have the same length, the driven crank 106 similarly performs a rotational motion. The freewheel 108 is operated at the driven end of the coupling device 104.

  In the crank state shown in FIG. 1, the drive crank 102 and the driven crank 106 are provided on the same side of the axis passing through the rotation axis 114 of the drive crank 102 and the rotation axis 116 of the driven crank 106. Accordingly, the driven crank 106 has the same rotation direction 110 as the drive crank 102. In this rotational direction 110 of the driven crank 106, the freewheel 108 is operated by the driven crank 106 in the entraining direction in which the driven crank 106 transmits the driving force to the output shaft. This crank state can also be referred to as a “+” configuration.

  FIG. 2 shows an adjustable drive crank 202, a coupling device 204, a driven crank 206, and a free wheel in a rotation direction 210 on the second free wheel side in which a free wheel state without accompanying driven shaft is performed. In this embodiment, the drive crank 202 and the driven crank 206 have the same length.

  In the crank state shown in FIG. 2, the drive crank 202 and the driven crank 206 are provided on different sides of the axis passing through the rotation axis 212 of the drive crank 202 and the rotation axis 214 of the driven crank 206. Accordingly, the driven crank 206 has a rotation direction 210 opposite to the driving crank 202. In the rotation direction 210 of the driven crank 206, the free wheel 208 is operated by the driven crank 206 in a free wheel direction in which the driven crank 206 does not transmit the driving force to the output shaft. The crank state can also be referred to as a “−” configuration. For other points, reference is made in particular to FIG. 1 and the accompanying description.

  FIG. 3 shows that the crank variator lever / drive lever 302, 304, 306, 308, 310, 312 and the driven cranks 314, 316, 318, 320, 322, 324 move to a special position having the same length. A coupling device arrangement 300 is shown. Each drive crank is drivingly connected to the driven crank by a coupling device. Each drive crank therefore has an associated driven crank. The drive crank 302 is drivingly connected to the driven crank 314. The driven crank 304 is drivingly connected to the driven crank 316. The drive crank 306 is drivingly connected to the driven crank 318. The drive crank 308 is drivingly connected to the driven crank 320. The drive crank 310 is drivingly connected to the driven crank 322. The drive crank 312 is drivingly connected to the driven crank 324.

  The transition to the special position shown in the drawing is based on the normal position where the drive cranks 302, 304, 306, 308, 310, 312 have smaller lengths than the driven cranks 314, 316, 318, 320, 322, 324. This is performed by appropriate adjustment of the eccentric body driving device. In this embodiment, the crank variator lever / coupler arrangement 300 has six drive cranks 302, 304, 306, 308, 310, 312 evenly distributed in the circumferential direction. Thus, at the drive side pivot axis 326, an angle of 60 ° is provided between adjacent drive cranks. The driven cranks 314, 316, 318, 320, 322, and 324 may be at the positions shown in FIG. 3, for example, when shifting to the special positions. In this embodiment, the three driven cranks 314, 316, 318 may have a “+” configuration, and the three driven cranks 320, 322, 324 may have a “−” configuration. The input shaft is driven only by driven cranks 314, 316, 318 having a “+” configuration. For other points, reference is made in particular to FIGS. 1 and 2 and the accompanying description.

  FIG. 4 shows a crank variator in a special position where the drive cranks 402, 404, 406, 408, 410, 412 and the driven cranks 414, 416, 418, 420, 422, 424 have the same length after passing through the singular position. A lever / coupler arrangement 400 is shown. The singular position is a position where the driven cranks 414, 416, 418, 420, 422, 424 shift from reciprocating motion to rotating motion. The driven cranks 414, 416, 418, 420, 422, 424 can then be brought into a changed state. In any case, the driven crank on the same side of the axis 430 that passes through the axis of rotation 426 of the drive crank and the axis of rotation 428 of the driven crank together with the associated drive crank has a “+” configuration. A driven crank with an attached drive crank on the other side of the axis 430 has a “−” configuration. In this embodiment, the driven cranks 414, 418, 422 have a “+” configuration, and the driven cranks 416, 420, 424 have a “−” configuration. For other points, reference is made in particular to FIGS. 1, 2 and 3 and the accompanying description.

  FIG. 5 shows the crank variator after the drive cranks 502, 504, 506, 508, 510, 512 have returned to their normal positions having a length less than the driven cranks 514, 516, 518, 520, 522, 524. A lever / coupler arrangement 500 is shown. The transition to the normal position shown in the drawing starts from a special position where the drive cranks 502, 504, 506, 508, 510, 512 and the driven cranks 514, 516, 518, 520, 522, 524 have the same length, This is performed by appropriate adjustment of the eccentric body driving device. As shown in FIG. 5, the driven cranks 516, 518, 522 have a “+” configuration, and the driven cranks 514, 520, 524 have a “−” configuration. , 524 changed states. Regarding other points, reference is made in particular to FIGS. 1, 2, 3 and 4 and the description of affiliation.

  FIG. 6 shows a graph 600 relating to a change ratio 602 of a predetermined crank variator. The gear ratio transition 602 is represented by a gear ratio i that changes over time t. The change of the speed ratio i is brought about by appropriate adjustment of the eccentric body drive device. Starting from a high or short transmission ratio, the transmission ratio is reduced or extended. In this embodiment, starting from region 604 with good efficiency, efficiency is reduced in subsequent regions 606. On the lower side of the gear ratio i≈3.5, a region 608 where the efficiency is further reduced continues. This region 608 is quickly passed by switching to the special position 610. In the special position 610, the gear ratio i = 1 is adjusted. The efficiency is good at the special position 610. Therefore, the overdrive shift is performed with good efficiency. Regarding other points, reference is made in particular to FIGS. 1, 2, 3, 4 and 5 and the accompanying description.

  FIG. 7 shows a graph 700 showing the relationship between the transmission ratio i of the crank variator and the efficiency η. As the speed ratio i changes, an efficiency transition 702 is brought about. The change of the speed ratio i is brought about by appropriate adjustment of the eccentric body drive device. When the gear ratio decreases or extends starting from a high or short-time gear ratio, the efficiency η is first reduced. In a given region 704, the efficiency η can still be ranked good. In the subsequent region 706, the efficiency η is reduced. Further, in the subsequent region 708, the efficiency η is further reduced. When the gear ratio i = 1, switching to the special position 710 is performed. With the switch to the special position 710, the efficiency increases rapidly from the reduced efficiency 712 to the good efficiency 714. Therefore, the overdrive speed ratio can be performed with good efficiency. In other respects, reference is made in particular to FIGS. 1, 2, 3, 4, 5 and 6 and the accompanying description.

DESCRIPTION OF SYMBOLS 100 Crank variator 102 Drive crank 104 Connection device 106 Driven crank 108 Free wheel 110 Rotation direction 112 Arrow direction 114 Rotation axis 116 Rotation axis 200 Crank variator 202 Drive crank 204 Connection device 206 Driven crank 208 Free wheel 210 Rotation direction 212 Rotation axis 214 Rotation axis 300 Lever / coupling device arrangement 302 Drive crank 304 Drive crank 306 Drive crank 308 Drive crank 310 Drive crank 312 Drive crank 314 Driven crank 316 Driven crank 318 Driven crank 320 Driven crank 322 Driven crank 324 Driven crank 326 Rotation axis 400 Lever / coupling device arrangement 402 Drive crank 404 Drive crank 406 Drive clan 408 Drive crank 410 Drive crank 412 Drive crank 416 Driven crank 418 Driven crank 420 Driven crank 422 Driven crank 424 Driven crank 426 Rotating axis 428 Rotating axis 430 Axis 500 Lever / linker arrangement 502 Drive crank 504 Drive crank 506 Drive crank 50 Drive Crank 510 Drive Crank 512 Drive Crank 514 Driven Crank 516 Driven Crank 518 Driven Crank 520 Driven Crank 522 Driven Crank 524 Driven Crank 600 Graph 602 Speed Change Ratio 604 Region 608 Region 610 Special Position 700 Graph 702 Region 70 Region 704 Region 704 Region 710 Special position 712 Efficiency 714 Efficiency

Claims (10)

An input shaft provided with an input shaft rotation axis, an adjustable eccentric drive device arranged corresponding to the input shaft, an output shaft equipped with an output shaft rotation axis, and arranged corresponding to the output shaft The freewheel device (108, 208) and the eccentric drive and freewheel device (108, 208) at least one first lever (102) adjustable between a minimum length and a maximum length. 202, 302, 304, 306, 308, 310, 312, 402, 404, 406, 408, 410, 412, 502, 504, 508, 510, 512), at least one drive rod (104, 204) and fixed. At least one second lever (106, 206, 314, 316, 318, 320, 322, 324, 414, 416, 418, 420, 22, 424, 514, 516, 518, 520, 522, 524), in particular, a continuously variable transmission (100, 200) for a powertrain of an automobile driven by an internal combustion engine Because
The maximum length of the first lever (102, 202, 302, 304, 306, 308, 310, 312, 402, 404, 406, 408, 410, 412, 502, 504, 508, 510, 512) is The length of the second lever (106, 206, 314, 316, 318, 320, 322, 324, 414, 416, 418, 420, 422, 424, 514, 516, 518, 520, 522, 524) A transmission device characterized by being equivalent to   Transmission device according to claim 1, characterized in that the transmission ratio i of the transmission device (100, 200) is adjustable between ∞ ≥ i ≥ 1.   The drive rods (104, 204) include a first drive rod rotation axis on the eccentric body drive device side, a first drive rod eye on the eccentric body drive device side, and a second drive rod rotation on the freewheel device side. The first lever (102, 202, 302, 304, 306, 308, 310, 312, 402, 404, 406, 408, 410) has a moving axis and a second drive rod eye on the freewheel device side. , 412, 502, 504, 508, 510, 512) are formed between the input shaft rotation axis (114, 212, 426) and the first drive rod rotation axis, and the second Lever (106, 206, 314, 316, 318, 320, 322, 324, 414, 416, 418, 420, 422, 424, 514, 516, 518, 520, 522, 5 The transmission device according to claim 1 or 2, wherein 4) is formed between the output shaft rotation axis (116, 214, 428) and the second drive rod rotation axis. .   The output shaft rotation axis (116, 214, 428) and the second drive rod rotation axis are disposed radially inward of the second drive rod eye. Transmission device.   5. The transmission device according to claim 1, wherein the freewheel device is arranged radially inward of the second drive rod eye. 6.   Transmission device according to any one of claims 1 to 5, characterized in that an eccentric element is arranged between the second drive rod eye and the freewheel device (108, 208). .   The eccentric element has an outer contour and an inner contour, the outer contour is disposed corresponding to the second drive rod eye, and the inner contour is disposed corresponding to the freewheel device (108, 208). The transmission device according to claim 6, wherein:   When the transmission gear ratio i of the transmission device (100, 200) is i = 1, the second drive rod rotation axis may go around the output shaft rotation axis (116, 214, 428). The transmission device according to any one of claims 1 to 7, wherein the transmission device can be used.   When the transmission gear ratio i of the transmission device (100) is i = 1, the second drive rod rotation axis is centered on the output shaft rotation axis (116, 428) in the first rotation direction ( 110. The transmission device according to claim 8, characterized in that it can circulate around 110) and the output shaft is entrained in the first direction of rotation (110).   When the transmission gear ratio i of the transmission device (200) is i = 1, the second drive rod rotation axis is centered on the output shaft rotation axis (214, 428) in the second rotation direction ( The transmission device according to claim 8, characterized in that a freewheeling state in which the output shaft is not accompanied is performed in the second rotation direction (210).

Images