JP6441082B2 - transmission - Google Patents

Description

  The present invention relates to a transmission (variator). More specifically, the present invention relates to a transmission that is a component of a mechanical transmission system.

  As used herein, a transmission interconnects two rotatable elements so that when rotating, the two rotatable elements have a rotational speed that is related to each other by a ratio (referred to as a “speed ratio”); This ratio is a component of the transmission that can vary substantially continuously between the minimum transmission ratio and the maximum transmission ratio. More particularly, the present invention relates to a transmission having a take-off drive device that applies a radial force in a direction perpendicular to the transmission axis.

Full Toroidal Transmissions A series of transmissions are known as “full toroidal” transmissions. A full toroidal transmission includes an input race and an output race within the transmission, which races about a common axis ("transmission axis"). Each race, usually in the form of a disk, has an operating surface, and each operating surface is configured to face in a direction parallel to the transmission axis. An annular recess having an arcuate cross section is formed coaxially with the transmission axis in each working surface. The recesses are positioned with substantially the same radius ("toroidal radius") relative to the transmission axis, and are arranged so that the cross-sections of these recesses are on a common virtual circle, the plane of the virtual circle being the transmission shaft The line intersects the line, and the center of the imaginary circle lies within a plane (“center plane”) that is parallel to the working surface and is evenly spaced between the working surfaces. By extending the virtual circle around the transmission axis, a virtual torus is drawn and the working surface occupies the border region opposite the torus. Thus, the space between the working surfaces of the race is called the “toroidal cavity”.

  The rotatable element is mounted to roll on the surface of the race and is referred to herein as a rolling element or roller. A plurality of rolling elements are provided in the toroidal cavity. Each rolling element has a rolling surface that contacts the respective working surface of the two races (according to the conditions discussed below). Each rolling element is carried by each carriage and can rotate with respect to the carriage around a rolling axis that is the center of the rolling surface.

  The rotation of one of the races relative to the carriage (referred to herein as the “input race”) causes each rolling element to rotate, and thus the other in the opposite direction to the rotation of the input race. The race (referred to herein as the “output race”) will rotate. If the output race is able to rotate in response to the applied torque, the output race will rotate in the opposite direction to that of the input race. During such rotation, each rolling element will contact the input and output races around a respective circular contact trajectory drawn on the respective working surface. If these two trajectories have the same radius, the output race and the input race will have the same rotational speed (although in opposite directions). However, if the radius of the track on the input race (“input radius”) is not equal to the radius of the track on the output race (“output radius”), the speed of the output race is greater or less than the speed of the input race. Become. Generally, the gear ratio is equal to the ratio of the input radius to the output radius.

  Each carriage is configured such that the rolling axis can move to change the input and output radii, and this movement is called “tilt”. At least when the transmission is operating in equilibrium, the input and output radii are symmetrically arranged around the toroidal radius.

  In the above description, reference is made to the contact between the working surface and the rolling element. However, this is simplified. Most embodiments of toroidal transmissions operate using traction drive force. In other words, the working surface and the rolling element are at least partially immersed in the traction fluid. This has the property of having a viscosity that increases rapidly when the pressure exceeds a threshold. As the race rotates, traction fluid is drawn into the nip formed between the rolling element and the working surface, creating a thin layer of traction fluid between the rolling surface and the working surface, thus literally these There is no contact between them. In order to obtain sufficient traction drive force, an end load is applied that biases the races toward each other along the transmission axis. The end load is a requirement that provides sufficient load to generate adequate traction at the interface between the working and rolling surfaces, but not to detract from the efficiency and durability of the transmission. Optimized to balance. In many embodiments, the race can cause slight movement along the transmission axis in response to end loads.

  Within the general configuration of the full toroidal transmission described above, numerous variations are possible with respect to freedom of carriage control, mounting and movement, number and configuration of races, number and configuration of rolling elements, etc. It is.

  The use of the terms “input” and “output” to define a race should not be construed as a functional or structural limitation on these components, they are merely signs. The transmission can be fully symmetrical. These will usually be chosen to provide a concise and understandable explanation in a particular context. For example, in the case of a vehicle transmission, the input is usually connected to the prime mover and the output is usually connected to the final drive system, indicating the standard power direction through the transmission. However, it will be appreciated that when the vehicle is in an overrun condition, power is actually directed from the output of the transmission to the input by the engine brake.

  In the remainder of this description, the term “transmission” refers to the full toroidal transmission described above unless the context indicates otherwise.

There are two main methods used to control the transmission: torque control and ratio control.

  Since torque control relies on characteristics resulting from transmission characteristics, there is no direct equivalent in multi-speed transmissions. Torque control is described in a number of publications, including the parts of International Patent Publication No. 2010/070341 related to FIGS. 1-3, and only provides an overview necessary to enable an understanding of the invention. This will be described here.

Torque control relies on a transmission having several design features.
Each carriage has a degree of freedom of rotation about a reaction force axis inclined at a slight angle with respect to the center plane.
Each carriage can move in the axial direction along the reaction force axis against the force applied by the actuator.

  Note that the first of these requirements means that the tilt angle is not directly controlled by the actuator while under torque control.

  Each race applies a force acting on the working surface in a tangential direction to each rolling element. Accordingly, equal and opposing tangential forces are provided by each actuator to maintain the rolling axis of the corresponding rolling element fixed along the reaction force axis. When the force applied by the actuator changes, the force acting on the carriage becomes unbalanced, and thus the rolling shaft moves. The geometry of the transmission is configured such that a connection is created around the reaction force axis upon movement along the reaction force axis, thereby causing the carriage to rotate. This changes the tilt angle and thus the gear ratio so as to reduce the imbalance of forces acting on the carriage. Thus, the carriage moves asymptotically towards a new tilt angle where the force returns to equilibrium, and the transmission ratio changes when this occurs. That is, the force applied by the actuator determines the torque that will be generated across the transmission, and the transmission incorporates the gear ratio required to obtain that torque.

  Ratio control bears the closest similarity to transmission control at a plurality of discretely spaced ratios. In the ratio control configuration, the displacement of the roller and the carriage is controlled by means that does not respond to the reaction force received by the rotor carriage. The basic operating principle of ratio control is that the control system determines the gear ratio required to achieve the desired operating conditions, operates the actuator and rolls the shaft to the angle required to achieve the target ratio. Is to move the carriage so that it tilts directly.

Introduction Toroidal transmissions of the present invention can be used in a wide range of applications, including those requiring high power density, such as vehicle main drive transmissions and auxiliary drive devices, and low power density applications, such as lawn mowers. Traditionally, it has dual toroidal cavities with three rollers per cavity to allow the desired power level to be transmitted with the desired level of mechanical efficiency, especially in high power density applications. A transmission can be used. The roller can have an independent roller control mechanism, or the roller control mechanism can be coupled so that the load can be shared evenly between the two cavities. Correspondingly, the cost and complexity associated with such a transmission is increased over that of a single toroidal cavity transmission. In addition, the size of the transmission housing required to accommodate the individual control mechanisms may be excessively large, and parts may protrude from the housing at an undesirable angle, resulting in an undesirable external shape. This can cause packaging problems when incorporating the transmission into applications such as vehicular main drive transmissions and auxiliary drive units. To reduce weight, complexity, cost, and packaging problems, it is advantageous to employ a configuration that includes only two rollers in each of one or two cavities.

  The output of the transmission can be utilized through a mechanism located radially in the transmission axis and is one of the transmission or other means (eg, gear on the circumferential surface of the output shaft or output disk). Or operably coupled to more output disks. As an example, an output disk having gear teeth on the circumferential surface can mesh with a gear mounted in the radial direction of the transmission axis, from which the output is taken out and used. A configuration in which an output is used by a chain action on a plane perpendicular to the transmission axis is known. Such a take-off drive configuration applies force to the output disc in a direction perpendicular to the transmission axis. This force places the input shaft and roller under radial load, and the shaft and roller act as a beam, thereby deflecting the shaft and roller, causing the distal side of the input shaft to become tensioned and close. The rear side can be in a compressed state.

  The bending moment applied to the shaft and roller is accommodated by different contact normal loads between the disk and the roller, depending on the position of the disk-roller contact point. If a sprocket and chain configuration is used as the take-off drive, the rollers located on the same side of the take-off drive and the transmission are normally unloaded, and if a gear configuration is used, the distal roller Is usually unloaded. Thus, the rollers can be exposed to different contact normal forces, leading to problems associated with "overclamping" which leads to poor transmission of drive force and traction and reduced durability. This problem has been addressed by providing a transmission output disk support, but may be increased in weight or cost, or impractical due to packaging limitations.

International Patent Publication No. 2010/070341 European Patent EP-A-1 846772

  The object of the present invention is to solve this problem by improving the adverse effects of distortion or bending without increasing the complexity, weight or cost of the transmission.

  The inventors have stated that the disk-roller contact point is generally located in a plane substantially perpendicular to the direction of the radial force generated by the contact between the take-off drive and the output drive. It has been found that this can be achieved by mounting the roller in a toroidal cavity so that this surface preferably passes through the transmission axis.

  To achieve this object, the present invention provides, in a first aspect, an input surface mounted for rotation on an input shaft defining a transmission axis, and coaxially mounted for rotation with the input surface and An output surface defining a toroidal cavity with the input surface, two rollers in driving engagement with the input surface and the output surface, and operatively engaged with the output surface and disposed in a radial direction of the transmission axis, whereby the transmission shaft And a take-off drive that generates a radial contact force that intersects perpendicularly to the line, wherein the roller has an input surface and an output surface at one specific ratio within the operating range of the transmission. The contact points of the rollers are arranged so as to lie substantially in a plane substantially perpendicular to the direction of the contact force.

  In one particular ratio, the roller / disk contact point is approximately located in a plane that is substantially perpendicular to the radial force. One or more contact points include the actual action when the transmission ratio changes, and the plane through the majority of the roller / disk contact points to account for other factors such as load balancing between the rollers. This is indicated by reference to a roller / disk contact point located "approximately" in the plane. Therefore, this term should be interpreted as taking into account the function that the roller / disk contact point is in a substantially planar relationship, and what this exact mechanical is, which plane is substantially perpendicular to the radial load. It will be understood that it does not imply or imply suitability. This plane is located on or close to the neutral axis of the transmission bend, thus resulting in the normal contact load between the disk and the two rollers in each cavity of the transmission being approximately the same.

  The plane of the roller / disk contact point is preferably substantially perpendicular to the radial force. The plane preferably passes through the transmission axis or is sufficiently close to the transmission axis so that the roller / disk contact point is substantially affected by the radial load from the take-off drive. Disappear.

  The input and output surfaces that define the toroidal cavity are preferably formed on the input and output discs, respectively.

  The transmission preferably includes an input shaft on which the input disk is mounted and a coaxial output shaft on which the output disk is mounted.

  Preferably, the transmission includes an output drive through which a take-off drive is operatively engaged with the output disk. The output drive is preferably mounted to rotate coaxially with the output disk. The output drive can have a different diameter than the output disk. Alternatively, the output drive can be formed on the circumferential surface of the output disk. Preferably, the output drive is selected from gears and sprockets. The circumferential surface of the output disk may comprise teeth that define an output gear or sprocket for engagement with a take-off drive, e.g. via a chain or belt radially arranged on the output gear. it can.

  The output drive and take-off drive are preferably gears that mesh with each other, but provide a contact force in a direction perpendicular to the plane defined by the contact points between the two rollers and the input and output surfaces , Belts, or sprockets connected by any other means for transmitting driving force.

  Each roller can operate together or independently. Where separate actuation is required, the rollers are preferably hydraulically operated and the transmission includes a hydraulic roller actuator for each roller. The roller can be mounted on the carrier. The carrier can be mounted to pivot, or can be mounted to translate or otherwise move relative to the transmission axis, depending on the type of roller control system required. The carrier can have radial and optionally non-radial oscillations as described below. The transmission can include one and only one input surface, an output surface, and a toroidal cavity. Alternatively, the transmission can include two toroidal cavities.

  In a second aspect, the present invention provides a first input surface and a first input surface that define a first toroidal cavity and are coaxially mounted to rotate about a transmission axis. And a first pair of rollers drivingly engaged with the first output surface, a second toroidal cavity defining a second toroidal cavity, and a second input surface and a second coaxially mounted for rotation about the transmission axis An output surface, a second input surface and a second pair of rollers in driving engagement with the second output surface, and a radial direction of the transmission axis operatively engaged with the first and second output surfaces And a take-off drive device that generates a contact force that intersects the transmission axis perpendicularly, whereby a first pair of rollers and a second pair of Roller with each of the input and output surfaces at one specific ratio within the range Contact point of les are arranged so as to be substantially positioned in a substantially vertical plane in the direction of the contact force. Advantageously, the dual cavity transmission of the present invention is less complex and less expensive than a dual cavity transmission in which each roller is controlled independently. The transmission also provides a smaller external size and shape, allowing use in applications where space is limited, such as small vehicle applications. The present invention provides a dual-cavity transmission that is more economical to manufacture and assemble than known double-cavity transmissions, and can be advantageously and economically used in low-cost applications. The transmission of the present invention also provides a balance of reaction torque from the two cavities, allowing for improved transmission efficiency and reliability. Fewer actuators are required, which can reduce the size of the transmission as well as unwanted protrusions from the transmission housing and can provide increased flexibility in positioning the control assembly.

  In another embodiment of the second aspect of the present invention, the transmission includes a roller in the first cavity and a roller in the second cavity rotatably mounted, and a reaction torque from the first cavity, There is no control assembly adapted to balance the reaction torque from the second cavity.

  The transmission can be torque controlled or ratio controlled. The rollers in the first cavity can be controlled individually or in cooperation with each other. The rollers in the second cavity can be controlled individually or in cooperation with each other, for example, each roller can be controlled independently by a respective actuator that can include a hydraulic piston. In one embodiment, the rollers in the first cavity cooperate with each other, but are controlled independently of the rollers in the second cavity, and the rollers in the second cavity also cooperate with each other. To be controlled. In one embodiment, the transmission comprises two toroidal cavities, each cavity having two rollers, each roller being independently controlled by a respective actuator that can include a hydraulic piston. Preferably, the roller in the first cavity and the roller in the second cavity are adapted to balance the reaction torque from the first cavity and the reaction torque from the second cavity. Mounted rotatably on top.

  The control assembly preferably includes a first roller carrier that holds a first pair of rollers in a first cavity, and a second roller carrier that holds a second pair of rollers in a second cavity. , And a mechanical linkage between the first and second roller carriers, which can balance the reaction torque of the rollers. A roller is rotatably mounted on the first and second carriers. The term “carrier” is used herein to mean a component that holds two or more rollers, as in the present invention. As used herein, the term “carriage” refers to the part that holds a single roller, as in the prior art. Preferably, the control assembly controls the load applied to all of the rollers simultaneously.

  When the transmission is torque controlled, the mechanical linkage is preferably mounted to rotate about a pivot point. In ratio controlled transmissions, the mechanical linkage can be pivotally mounted, but need not be pivotally mounted. The mechanical linkage preferably comprises a pivotally mounted lever that is operably coupled to the first and second roller carriers. The mechanical linkage preferably extends across the two toroidal cavities.

  Preferably, the control assembly allows the reaction torque of the first and second toroidal cavities to be balanced or equalized utilizing a mechanical linkage between the roller carriers. If the torque is not responding evenly, the mechanical linkage moves and moves between the reaction torque from the roller in the first cavity and the reaction torque from the roller in the second cavity. Redistribute torque until equilibrium is restored. Each roller produces a control force that reacts back to its carrier, which depends on the roller position, tilt, disk-roller contact normal load, and input and output surface speeds. If any roller control force acting on the carrier is not equal in magnitude to each of the other roller control forces acting on the same carrier, the carrier translates radially in the toroidal cavity and in that cavity The roller control force can be equalized. The roller load equalization within the cavities and the balance or equalization of the reaction torque from each cavity ensures that all roller control forces in the transmission are equalized or controlled within precise limits. It becomes like this. The load balancing mechanism provided by the carrier assembly can widen manufacturing tolerances of subsequent components, thereby enabling cost reduction and ease of assembly.

  The transmissions of the first and second aspects of the present invention can be torque controlled or ratio controlled.

  The ratio controlled transmission is configured to receive a control signal indicative of the required speed ratio and adjust the orientation of the rollers in response to the control signal to obtain a desired ratio. The rollers can be directed to different positions to provide the desired speed ratio, for example, by tilting the rollers. The transmission preferably includes a control input for the roller from an external source to provide the desired drive ratio.

  In one embodiment of “ratio control”, the plurality of rollers in the toroidal cavity are controlled by a control member. Preferably, the at least one control member is operably coupled to the plurality of rollers on the same side of the plane passing through the transmission axis. When there are a plurality of control members, it is more preferable that all the control members are located on the same side of the plane passing through the transmission axis. Preferably, the control member imparts to the roller a rotational component about an axis that passes through the roller center and is parallel to the transmission axis, so that the roller slopes with a new slope. As a result, the rotation shaft of the roller moves away from the intersection with the transmission axis, and the roller is steered to a new inclination that intersects the transmission axis again.

  In this mode of operation, referred to as “tilt steering”, the present invention can advantageously operate the control member with a relatively low output. The present invention further provides a transmission having a control member capable of operating at an output of less than 25 watts, preferably less than 20 watts, especially less than 10 watts, desirably less than 5 watts.

  In the case of the dual cavity transmission of the second aspect of the present invention, preferably a control input for the rollers in the first toroidal cavity and / or the second toroidal cavity is provided, the transmission further comprising: Means for detecting the reaction force torque in the roller carrier and the second roller carrier, and means for correcting the control signal in response to the difference between the two reaction force torques detected by the reaction force detection means. Prepare. The control input preferably comprises an external input to the roller carrier that is separate from the mechanical linkage. The input to the carrier can comprise a dedicated input from an external input, or can comprise an input from an external input and from a mechanical linkage. The mechanical linkage functions as a detection means that provides information from which an external input to the carrier is obtained.

  In a torque controlled transmission, a signal indicating the required transmission reaction torque is usually provided, for example by applying a force to the roller carriage, eg by hydraulic means, which is the torque at the transmission input and output. It is the sum. The reaction torque is a net torque that tends to rotate the transmission disc, and this torque must also react to the transmission housing. The transmission responds to ratio changes resulting from engine or vehicle acceleration or deceleration, regardless of reaction torque.

  In the dual cavity transmission according to the second aspect of the invention, the first roller carrier, the second roller carrier, and preferably both roller carriers are preferably about a unique fulcrum or pivot point. Pivotably mounted, the mechanical linkage can act on both roller carriers to pivot about their respective pivot points. Preferably, each of the carriers is pivotally mounted on a pivot axis that is substantially parallel to the transmission axis and perpendicular to the basic pivot point of the mechanical linkage. The mechanical linkage is mounted to move in a direction substantially parallel to the transmission disk tangent. The control assembly includes an actuator that moves the mechanical linkage in a direction substantially parallel to the tangent to the transmission disk. Preferably, the actuator acts on the mechanical linkage. The actuator for the mechanical link mechanism can be single-acting or double-acting, and preferably double-acting. The actuator can be controlled by conventional means, for example hydraulic or electric.

  A transmission controlled by both torque and ratio preferably provides an end stop, such as a control member of a control assembly or a mechanical linkage in a dual cavity transmission. At least one restriction mechanism for restricting movement of the mechanical components of the machine.

  The following description applies to a transmission controlled by both torque and ratio of the first and second aspects of the present invention unless otherwise stated.

  In the first aspect of the invention, the roller can be mounted for rotation on the carrier as described above. A limiting mechanism can be provided to limit the movement of the roller carrier and preferably includes a slot of a limited defined length in the transmission housing where the carrier fulcrum is located. Alternatively, the limiting mechanism can include a mechanical end stop that is independent of the slot in the housing.

  In the case of a dual cavity transmission having a control assembly as described herein, the limiting mechanism preferably acts on a mechanical linkage to limit its rotational movement about a pivot point; This provides a rotating end stop. By limiting the rotational movement of the mechanical linkage in the control assembly, it is possible to reduce any significant differences between carrier torques due to the adverse effects of mechanical, hydraulic or other component failures. . Advantageously, any torque generated due to contact between the mechanical linkage to the limiting mechanism is uniformly carried by the rollers in the first and second cavities. Preferably, the control assembly is mounted for rocking in the radial direction so that the load between the rollers without each of the first and second cavities can be balanced.

  In a preferred embodiment, both the first roller carrier and the second roller carrier comprise a limiting mechanism. In a torque controlled transmission, the mechanical linkage preferably comprises a limiting mechanism that limits movement in the tangential direction of the disk in the transmission controlled by both ratio and torque, the mechanical linkage comprising: Preferably, it has a mechanism to limit rotation about its pivot point. Providing a limiting mechanism on either or both carriers advantageously improves the robustness of the transmission.

  Preferably, each of the limiting mechanisms is a mechanical end stop, such as a lug, whether it is a mechanical linkage, an actuator, a first roller carrier, or a second roller carrier.

  Preferably, the two rollers are mounted on a carrier that is radially movable with respect to the transmission axis, as described, for example, in European patent EP-A-1 846772. The carrier preferably comprises a pivot pin which is displaceable along a slot extending radially with respect to the transmission rotation axis. The diameter of the pivot pin is preferably substantially the same as the width of the slot, thereby constraining the pivot pin from moving in the longitudinal direction of the slot. In another embodiment, the pivot pin can be mounted in a slider block that is movable along the slot so that the carrier is in a direction having only a radial component and also in radial and non-radial directions. It can move in a direction that has both components. Preferably, the pivot axis is movable over a predetermined distance in the radial direction.

  The roller carrier preferably comprises a damper. The damper preferably serves to damp carrier motion to reduce “hunting”. Also, the damping means acting in the radial direction of the carrier motion can be used to reduce carrier hunting.

  The one or more toroidal cavities of the transmission are preferably full toroidal cavities, although semi-toroidal cavities may be utilized if desired.

  In the dual cavity transmission of the present invention, the first and second output surfaces of the transmission are preferably directed outward from each other and are disposed between the first and second input surfaces. The first and second output surfaces can be formed on both sides of a single disk, or can be formed on separate disks that are mounted back to back to rotate coaxially with the shaft. If the output surface is formed on a separate disk, the output drive can preferably be mounted coaxially with and between the separate output disks to rotate coaxially. The output drive can have a different diameter than the output disk. Where a single output disk is utilized, an output drive is preferably provided on the circumferential surface. Preferably, the output drive is selected from gears and sprockets. The circumferential surface of the output disc is provided with teeth that define an output gear or sprocket for engaging the take-off gear or sprocket via a chain or belt, preferably arranged radially with respect to the output gear. Can do.

  In the first and second aspects of the invention, other rollers can be used, but these rollers do not have contact points simultaneously in a plane defined by the contact points of the pair of rollers. When a vertical contact force is generated, these disc contact points located away from the neutral shaft of the transmission are subjected to compression and / or tension. However, in a preferred embodiment, the transmission comprises only two rollers per toroidal cavity.

  Preferably, the drive engagement between the disk and the roller is through traction fluid.

  A transmission embodying the present invention is preferably a component in a transmission system that transmits power from a prime mover to a drive system, and according to another aspect, the present invention provides such a transmission system. . The drive system can be a main drive system for a vehicle. Such a drive system can include a single prime mover, such as an internal combustion engine. Alternatively, the drive system can include multiple prime movers, such as a hybrid drive system. In such a configuration, the prime mover typically includes an internal combustion engine and an electric motor. The drive system can further include a kinetic energy recovery system that can store and recover energy from the or each prime mover.

  The invention is illustrated in the accompanying drawings.

1 is a side view of a dual cavity transmission that is one embodiment of the present invention with a take-off drive engaged with an output drive of the transmission. FIG. FIG. 2 is an end view of the transmission shown in FIG. 1 as viewed from line I-II. 1 is a side view of a single cavity transmission according to the present invention with a take-off drive engaged with an output drive of the transmission. FIG.

  The transmission shown in FIGS. 1 and 2 is a transmission according to the invention which in this case is torque controlled. The continuously variable ratio transmission system includes a transmission having a first toroidal embedded input disk 10 and a first toroidal embedded (not shown) output disk 12 facing. The output disk 12 also has a toroidal recess 11 on the opposite side to provide a second toroidal embedded output surface. A second toroidal embedded input disk 13 is provided and defines an output surface 11 and a second toroidal cavity. Two rollers 14,16 are mounted in a first toroidal cavity defined between opposing toroidal embedding surfaces of the input and output discs 10,12 and are variable by tilting the rollers 14,16. The driving force is transmitted from the input disk 10 to the output disk 12 in a ratio. Two rollers 15, 17 are mounted in a second toroidal cavity defined between opposing toroidal embedding surfaces of the input and output disks 11, 13 and are variable by tilting the rollers 15, 17. The driving force is transmitted from the input disk 11 to the output disk 13 by the ratio.

  The output disk 12 includes teeth 30 on the circumferential surface of the disk 12 so that drive force can be extracted through a take-off drive (eg, gear 32) on a lay shaft parallel to the transmission axis. A radial force Fg in the direction shown in FIG. 1 is generated to impart a bending moment to the input shaft, thereby bending or spreading the more distal parts of the input surfaces 10, 13 and output surfaces 12, 11. Can be.

  The roller is in a plane where the force Fg passes through all roller-disk contact points when the transmission has a ratio of -1.0 (a negative value indicating that the direction of rotation between input and output is reversed). It is mounted so as to be perpendicular to it. In this orientation, the roller-disk contact point is located on the neutral axis of the transmission shaft, the normal contact force is substantially unaffected by the radial force Fg, and each roller contact is applied at an equal rate. The end load force is carried.

  When the roller-disk contact portion is oriented away from the plane perpendicular to the force Fg, the roller 30 is more distant from the meshing of the gears 30 and 32 and receives a smaller contact force and is closer to the meshing gears 30 and 32. As a result of the greater contact force, unbalance and poor performance are presented.

  The input disk 10 is connected to the system input shaft 18 and rotates together. The transmission provides output via an output shaft (not shown), which can be tubular, is connected to the output disk 12 and is coaxial with and disposed about the input shaft 18. . An output disk 12 having a first output surface and a second output surface provides an output drive for the transmission and is mounted on the output shaft.

  The transmission is housed in a generally tubular casing (not shown) that supports the outer section of the input shaft. The output shaft is inside the casing.

  The roller 14 is rotatably mounted in the roller carrier 40. Each roller 14, 16 and 15, 17 is similarly mounted. The roller carrier 40 includes roller carriages 44 and 46 for the roller 14 and a corresponding roller carriage for the roller 16 in the first toroidal cavity. The roller carrier 41 comprises similar roller carriages for the rollers 15 and 17 in the second toroidal cavity. The rollers 14, 16 and 15, 17 are each mounted using a stub axle 42 that is rotatably mounted within a roller carriage defined by opposing flat support plates 44, 46. Roller mountings are numbered only on one roller for purposes of illustration and clarity. The rollers are mounted on the carriers 40 and 41 via spherical bearings (for example, Rose Bearing). Each of the roller carriers 40, 41 includes two bars that hold two rollers and are pivotally mounted. The cross bar 48 connects the two rollers 14 and 16 in the first cavity, and the cross bar 49 connects the two rollers 15 and 17 in the second cavity. The pivot point of each carrier 40, 41 is located between the center points of the two spherical bearings holding the two rollers. Preferably, the pivot point comprises a pivot pin 72 mounted in a block 73, which is received in a slot 71 having the same width as the diameter of the pivot pin and is on the transmission axis of rotation. On the other hand, it is elongated in the radial direction. The slot is provided in a mounting lug that projects into the space between the input and output disks 10, 12 for the carrier 40 and the input and output disks 11, 13 for the carrier 41 in the transmission. Carriers 40 and 41 pivot about an axis parallel to the transmission axis.

  Each of the crossbars 48 and 49 includes operating arms 60 and 61 that project radially from the transmission rotation shaft in a direction perpendicular to the axis of the crossbars 48 and 49. The ends of the arms 60, 61 projecting out of the transmission housing have the shape of a wrench with a terminal opening for direct mechanical engagement with the mechanical linkage 64.

  The mechanical linkage 64 includes a coupling lever 66 mounted to pivot about a pivot point 68 and is operably coupled to the carriers 40, 41 through the arms 60, 61. The connecting lever 66 is movable in a direction perpendicular to the line of the lever 66 and in a straight line parallel to the tangent to the disk 12. The connecting lever 66 rotates about a pivot point 68 to allow the reaction torque from one cavity to be balanced or equalized with the reaction torque from the other cavity, thereby providing a connection lever. The end of 66 rotates and moves the arms 60 and 61 in a plane perpendicular to the transmission axis, and balances the reaction torque from the cavity. Actuator 70 is preferably a hydraulic actuator, and the stroke of the cylinder serves to provide a limiting mechanism for movement of coupling lever 66 in a direction parallel to the tangent to disk 12.

  As the crossbars 48, 49 pivot, both rollers 14, 15 in each cavity are pushed and the other rollers 16, 17 are pulled, both with the same force. The carriers 40, 41 can move radially away from and toward the transmission axis, which ensures that the roller control force in each cavity is equalized. The limitations associated with the actual manufacturing and assembly process make precise control of roller position and thus disk-roller contact conditions in low cost transmissions difficult. Accordingly, equalization of force between different rollers is particularly important in low cost assemblies, where component manufacturing is likely to be less accurate or specified with wide tolerances. The pivotal radial movement of the carriers 40, 41 allows the carrier to move to a position where force is generated by different rollers attached to the carrier, which arises from manufacturing differences and is reduced or desirable. Will be eliminated.

  In the variant shown in FIG. 4, the coupling mechanism is eliminated and each arm 60, 61 operates independently by an individual actuator 80, 82.

  FIG. 2 shows a roller carrier restricting mechanism comprising a slot 71 in the carrier 60 and a pin 72 mounted on the transmission housing and engaged with the slot 71 through the block 73. 73 is pivotally mounted on the pin 72 and is slidable along the slot 71 in a radial or non-radial direction relative to the transmission axis.

  FIG. 3 shows a single cavity transmission according to the present invention. The continuously variable transmission system includes a transmission having a toroidal embedded input disk 10 and a toroidal embedded output disk 12. Two rollers 14, 16 (16 not shown) are mounted in a toroidal cavity defined between opposing toroidal embedding surfaces of the input and output discs 10, 12 to tilt the rollers 14, 16 Thus, the driving force is transmitted from the input disk 10 to the output disk 12 at a variable ratio.

  The output disk 12 includes teeth 30 on the circumferential surface of the disk 12 so that drive force can be extracted through a take-off drive (eg, gear 32) on a lay shaft parallel to the transmission axis. A gear force Fg in the direction shown in FIG. 3 is generated to impart a bending moment to the input shaft, thereby causing the more distal parts of the input surface 10 and output surface 12 to spread apart.

  Each roller contacts the input and output disks such that when the transmission is at a ratio of -1.0, the force Fg is perpendicular to the plane passing through all roller-disk contact points. In this orientation, the roller-disk contact point is located on the neutral axis of the transmission shaft, the normal contact force is substantially unaffected by the radial force Fg, and each roller contact is applied at an equal rate. The end load force is carried.

  The input disk 10 is connected to the system input shaft 18 and rotates together. The transmission provides output via an output shaft (not shown), which can be tubular, is connected to the output disk 12 and is coaxial with and disposed about the input shaft 18. . An output disk 12 having a first output surface and a second output surface provides an output drive for the transmission and is mounted on the output shaft.

  The rollers 14, 16 can each be actuated by an actuator 70 or can be actuated together by a single actuating mechanism. Preferably, ratio control is provided utilizing a hydraulic actuator. The transmission can be torque controlled as needed.

10 Input disk 11 Input disk 12 Output disk 13 Output disk 14, 15, 16, 17 Roller 18 Input shaft 40, 41 Roller carrier 44, 46 Roller carriage 44, 46 Support plate 48, 49 Crossbar

Claims (20)

A transmission,
An output surface mounted coaxially with the input surface to rotate about the input surface and the transmission axis, wherein the input surface and the output surface form a first toroidal cavity. When,
Two rollers drivingly engaged with the input and output surfaces;
An output driving device;
A take-off drive device operatively engaged with the output surface through the output drive device and disposed in a radial direction of the transmission axis, the take-off drive device being perpendicular to the transmission axis in operation. Generating a radial force,
The roller, in one specific ratio within the operating range of the transmission, in contact with the input surface and the output surface at a first contact point, said first contact point in the direction of the force of the radial A transmission substantially located in a substantially vertical plane, wherein the output drive and the take-off drive are operatively engaged by a chain or belt. The transmission of claim 1, wherein the transmission has a single first toroidal cavity. Further, a second input surface and a second output surface forming a second toroidal cavity, wherein the second input surface and the second output surface are coaxial so that they rotate about the transmission axis. The second input surface and the second output surface mounted on
A second pair of rollers drivingly engaged with the second input surface and the second output surface;
At a specific ratio within the operating range of the transmission, each roller in the second toroidal cavity contacts a second input surface and a second output surface at a second contact point, and the first The transmission of claim 1, wherein the contact point and the second contact point are substantially located in a plane substantially perpendicular to the direction of the radial force.   The transmission according to any one of claims 1 to 3, wherein the roller is mounted on at least one carrier.   A roller in the first toroidal cavity and a roller in the second toroidal cavity are rotatably mounted on a control assembly, and the control assembly has a first reaction from the first toroidal cavity. The transmission of claim 3, wherein the transmission is adapted to balance a force torque with a second reaction torque from the second toroidal cavity. The control assembly comprises:
A first roller carrier holding the first pair of rollers in the first toroidal cavity;
A second roller carrier holding the second pair of rollers in the second toroidal cavity;
A machine that is between the first and second roller carriers to balance the first reaction force from the first toroidal cavity and the second reaction force from the second toroidal cavity. The transmission according to claim 5, further comprising a mechanical link mechanism. The transmission of claim 4 , wherein the at least one carrier is capable of translating radially within the first toroidal cavity to equalize the roller control force within the at least one carrier. Transmission according to claim 4 or 7 , wherein at least one of said carriers is pivotally mounted. The transmission according to any one of claims 4 , 7, and 8, wherein the at least one carrier includes a limiting mechanism.   The transmission according to any one of claims 1 to 9, wherein a transmission ratio is controlled by tilting the roller.   The rollers are arranged to rotate around their respective rolling shafts such that when the rollers rotate around the rolling shafts, the rollers rotate away from the point where they intersect the transmission axis. The transmission according to claim 10.   The transmission according to any one of claims 1 to 11, which is torque-controlled.   The transmission according to any one of claims 1 to 11, wherein the transmission is ratio controlled.   14. A transmission as claimed in any one of the preceding claims, wherein the roller is controlled using a control member capable of operating with an output of less than 25 watts. Wherein each of the first and second toroidal cavity, only two comprises a roller, transmission according to any one of claims 3, 5 and 6.   The transmission according to any one of claims 1 to 15, wherein each roller is independently controlled by a hydraulic piston. It said first and said second rollers of each of the toroidal cavity, are independently controlled by a hydraulic piston, transmission according to any one of claims 3, 5 and 6.   A transmission system for transmitting power from a prime mover to a drive system, wherein the transmission system includes the transmission according to any one of claims 1 to 17.   19. A transmission system according to claim 18 for an auxiliary drive device of a vehicle. When the direction of the radial force is such that power is transmitted from the input disk to the output disk,
The transmission of claim 1, wherein the transmission is substantially perpendicular to the plane both when power is transmitted from the output disk to the input disk.

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