Device for infinitely variable control of reduction ratio (variator)

FIELD: machine building.

SUBSTANCE: invention relates to rolling variator, particularly to control mechanism by roller orientation. Device of infinitely variable control of reduction ratio (variator) contains couple of rotating rolling path, installed for rotation around its common axis (218) of variator. Drive force is passed from one rolling path to the other by means of at least one roll (200), running by it. Connection between roll (200) and its carrier (214) provides roller precession relative to around axis (228) of precession, where it is defined relative to axis of precession and non-parallel to roller axis. Precession leads to changing of angle between axis (222) of roller and axis (218) of variator and corresponding to changing of reduction ratio. Carrier itself allows toothing (206), by means of which it is engaged with central tooth gear (212) and gear rim (214). Rotation of carrier (204) around axis of carrier serves to changing of axle orientation (228) of precession and accompanied by changing of reduction ratio of variator.

EFFECT: invention provides by means of control of displacement of carrier to change reduction ratio of variator.

16 cl, 21 dwg

 

The present invention relates to a variable-speed applications where the actuator thrust is transmitted from one raceway to another through one or more rollers, the orientation of which varies according to the change of gear ratio. In particular, the invention relates to a new mechanism to control the orientation of the roller.

Used here, the term "variable" refers to the transmitting device that allows stepless adjustment of the gear ratio. Figure 1 is illustrated only as an example and not of limitation, and in an extremely simplified form some of the peripheral components known variator 10 rolling, in which the actuator thrust is transmitted from the outer discoidal tracks 12, 14 rolling to the internal discoid track 16 rolling (or Vice versa) by means of rollers 18, rolling on the raceway. It shows only two rollers, however, in practice, variable usually contains six rollers, three in both cavities 38, limited raceways. Adhesive force between the rollers and raceways is provided by bias them toward each other, which is provided in this example by means of a hydraulic actuator 20, shift one track 14 rolling to the other. In the illustrated example, the left outer on the cone 14 of the roller mounted on the shaft 22 of the variator for joint rotation, while the right outer track 12 rolling in the illustration is made with the shaft in one piece. The inner track 16 roller mounted on the shaft for rotation around the shaft, the actuator may be a motor, schematically indicated by the reference position 23. Rotation of the outer tracks 12, 14 turns rolling the rollers 18 and, consequently, also the inner track 16 rolling. The PTO from the inner raceway may be missed around her chain or with any coaxial devices, well known in the prior art. The rollers are capable of "precession". This means that each of them can change their sexual orientation by changing the inclination of the roller axis to the axis of the variator 21, reduced shaft 22. Two alternative orientations of the rollers 18, respectively, indicated in figure 1 by solid lines and dotted line. It is obvious that by moving from one orientation to another, each roller changes the ratio of circumferences that it passes through the inner and outer raceways, thus causing the change gear ratio of the variator.

Therefore, the mounting of the roller should allow him to rotate around their own axes and turn around the other axis, which will be referred to as "the axis of precession". Accordingly, rotary motion, which is smenet the orientation of the roller, will often be referred to here as "precession". The precession of the roller is not manipulated directly, i.e. by application to the roller Assembly torque directed around the axis of precession. Instead, the nature of the installation roller allows the roller to freely conduct precession, and the orientation of the roller is controlled by a control effect, which creates a roller raceway. As an example let's consider the famous design of the variator, illustrated in figure 2 and 3. These drawings are taken from the United Kingdom patent 2227287, and for details relating to the structure and operation of this and other types of CVT should refer to this document. Figure 2 and 3 shows only two of the tracks 12, 16 rolling of the variator. Each roller 18, which shows only one is installed in the movable carrier 30, which is connected to the piston 32, which operates in the cylinder 34. The roller and its carrier may jointly exercise the precession around the axis of precession 36, which is defined in this particular construction the position of the cylinder 34. It should be noted that the axis of precession is not located in a radial plane. Instead, as shown in figure 2, it forms with the radial plane of the wheel angle CA. When the piston performs a reciprocating motion along the cylinder, the roller does the same section is atno-and-forth motion. Tracks 12, 16 rolling in this case, given the form in which they restrict containing rollers toroidal cavity of circular cross section, similar to the cavities 38, shown in figure 1. Raceway limit the roller 18 so that when the reciprocating motion of its center follows the path which is an arc of the Central circle of the torus. Moving the roller along this path depends on the balance between (a) a circular component 2F bias efforts to the carriage roller piston 32, and (b) two efforts F, applied to the roller 18 corresponding tracks 12, 16 rolling.

Each of the rollers is committed to the position at which at contacts between the roller 18 and the tracks 12, 16 rolling (the term "contact" is used here in a broad sense, since these components do not actually touch each other, being separated by a thin film of a traction fluid, known in the art) movement of the periphery of the roller is parallel to the moving surface raceway. Inaccurate line of movement of the roller and the raceway when the contacts causes the steering torque to rotate the roller about the axis of precession, that is, the desire to cause precession of the roller to reduce inaccurate matching. The condition of parallelism of the two movements (i.e. for zero driving the th moment) is the roller axis must intersect the axis of the variator.

What follows is a description of what happens when a node of the roller and the carriage 18, 30 is shifted to the left or to the right in figure 3. If the axis of the roller 41 is initially crosses the axis 21 of the variator, the offset roller takes her from this intersection, but only temporarily, because the resulting control point causes the precession of the roller when it is offset. Thanks a corner wheels SA this precession can recover the intersection of the two axes. The result is that the angle of precession" of the roller depends on its displacement along the circular path 40. In this known construction the relationship between the position of the roller and the angle of precession depends on the angle of the wheel.

This design provides control of the variator by means of torque. Such a method of operation of the variator is well known to specialists in the art and disclosed, for example, in EP 444086. If to explain briefly, CVT with controlled torque is not directly control the gear ratio of the variator. Controlled bias force (force 2F figure 2) is applied to each of the rollers, and in equilibrium it must be balanced by efforts to the roller raceways of the variator (effort F in figure 2). The efforts of the tracks kachen the I to the rollers, determined torques on the respective raceways of the variator, and the radii of the paths that the rollers draw on the disks. A simple analysis shows that:

Bias force of the actuator α Tin+Tout

where Tinand Toutare the torques on the inner and outer disks of the variator, respectively. The amount of Tin+Toutdenoted here as "reactive torque and directly controlled by this value, and not the gear ratio of the variator. Changes in transmission ratio of the variator occur due to the application of Tinand Tout(added to the applied external torques, for example, from the drive motor to the inertia acting on the input and output of the variator. The rollers move automatically and are precessing according to a subsequent change gear ratio of the variator.

Another type of construction of the variator disclosed, for example, in the publication GB 1002479 and illustrated in figure 4. In this case, the variator rollers also denoted by the reference position 18, although shown here is a full set of three videos in one cavity and mounted on bearings 50 and the holders 52 at the opposite ends of which spigot 54, 56 are inserted into the one line channels in the cross-piece 58. the thus, the the holder may slightly move back and forth along a line transverse to the axis of the variator. Such movement of the carriage is controlled by perceiving the stop element 60 with three spokes connected to each relevant holder ball joint 62. A small rotational movement of element 60 about the axis causes the variator rollers and holders to move along the mentioned transverse line. In line channels, in which the inserted spigot 54, 56 can be displaced along the axial direction to create the angle of the wheel, as described above, the control effect is used to control the orientation of the roller. The bearings 50 of the roller allow its small side "swimming", so that it can follow the desired circular path around the axis of the variator, despite the fact that the holder 52 should be in a straight line.

These implementation options provide for joint rotation of the holder and the roller to achieve the required precession of the roller. A different approach to the management of the roller disclosed in the publication WO 03/062670, and appropriate technical solution is shown in figure 5. In this case, the holder 70 has at its opposite ends two piston heads 72, 74, which go to the respective cylinders 76, 78. Each roller variator, the only example which again about what is meant by the reference position 18, can rotate around its own axis due to the roller bearing 80, and can also make the precession relative to the carrier, since the bearing 80 is connected with the carrier by means of a universal joint, containing the ball 82 and the plug 84 and the plug forms the axis around which the roller performs precession relative to the carrier. In this case the carrier cannot rotate, because the center of the roller is offset from the axis of the piston heads 72, 74. One advantage of this design is that the angle of the wheel, which is determined by the position of the pins 84 may be freely selected. In the previously described variable-speed capabilities of the angle of the wheel is limited by problems associated with, for example, grazing disk of the variator.

However, all the above-described variable-speed drives have in common is that the control effect is required to control the orientation of the roller is achieved simply by reciprocating movement of the carrier along the Central circle of the toroidal cavity.

The aim of the present invention to provide improvements in the method of controlling the roller (rollers) in CVT transmissions.

According to the present invention a device for stepless gear ratio, containing the first and second raceways mounted for rotation in the Rog common axis (the axis of the variator"), and at least one roller, which is connected with the carrier for rotation about the roller axis defined relative to the carrier, and which rolls on both raceways for power transmission drive between them at a variable ratio. The device according to the present invention contains concentric spaced Central gear and the crown gear, and the carrier has teeth, through which it engages with the Central gear and a ring gear, and the connection between the roller and its carrier provides the possibility of precession relative to the carrier about the axis of precession, which is defined relative to the carrier and not parallel to the axis of the roller, so that the relative rotation of the Central gear and the ring gear causes rotation of the carrier around its axis that is not parallel to the axis of the roller and the axis of precession, the resulting precession of the roller and the respective change gear ratio of the variator.

Preferably, the axis of the carrier passes through the center of the roller.

Preferably, the axis of the medium is parallel to the axis of the variator.

Preferably, the axis of precession is always inclined at a nonzero angle of the wheels to the plane perpendicular to the axis of the variator.

Preferably, the axis of precession passes through the center of the roller.

Preferably, the carrier is made with the possibility of reciprocating movement along the path around the axis of the variator.

Preferably, the device comprises means the application of controlled force to a Central toothed wheel and a toothed crown for displacement of the carrier along its trajectory.

Preferably, the carrier comprises a gear wheel with an incomplete circular periphery, containing the inner and outer toothed area on a common circular position for engagement respectively with the Central toothed wheel and a toothed crown.

Preferably, as the Central gear and the ring gear rotate around the axis of the variator.

Preferably, the Central gear and the ring gear are connected so that the position of one depends on the position of the other.

Preferably, the device further comprises a carrier mounted for rotation around the axis of the variator and moving at least one satellite, which is in mesh with the Central gear and a ring gear.

Preferably, the Central drive gear is carried out by means of the ring gear and planetary gear.

Preferably, the device further comprises a rack with linear movement, interacting with, ENISA least one of the Central gears and gear.

Preferably, as the Central gear and the crown gear is made with the possibility of bringing one or more racks with linear movement.

Preferably, the device further comprises a linear actuator for the application of controlled forces and means to convert this force into torque applied to at least one of the Central gears and gear.

Preferably, the linear actuator is a hydraulic mechanism.

Thus, according to the present invention provides a simple and convenient the necessary management support. Drive media can be a Central toothed wheel and a toothed crown in the form of a satellite in a planetary transmission.

The axis of the carrier is preferably parallel to the axis of the variator. It is also desirable that the axis of the carrier passed through the center of the roller, so that the rotation of the carrier does not cause radial displacement of the center roller.

Particularly preferably, the axis of precession passed through the center of the roller. If this movie can precession without radial displacement of the center. In the conventional design of the variator opportunity center of the roller to follow the penny is the real line of the torus, formed between the two raceways, limited, and therefore it is not capable of substantial radial offset.

The orientation of the axis of precession is not constant, since this axis is set relative to the carrier, which itself can be rotated. However, it is desirable that the axis of precession was always inclined at a nonzero angle of the wheels to the plane perpendicular to the axis of the variator. Thanks to the corner of the wheel in the rotation of the carrier roller may be returned due to precession in a position in which the roller axis intersects the axis of the variator.

Particularly preferably, the carrier was able not only to rotate around the axis of the carrier, but could make reciprocating movement in a circular path around the axis of the variator. This design is used for torque control. You can use the funds for the application of the regulated efforts aimed at moving the carrier along the track. To balance this bias force must then be balanced by efforts to the roller from the side of the raceway, which is the basis of the torque control.

If, when making a carrier reciprocating motion along the path around the axis of the variator was maintained constant slope to a line extending from the axis of the variator, no change of gear ratio vari the Torah should not happen. In a particularly preferred embodiment, the present invention uses a tool rotational drive of the drive so that the inclination of the carrier to a line which is radial relative to the axis of the variator and passing through the center of the roller varies depending on the position of the carrier on the track, passing around the axis of the variator. This way you can establish that the offset of the carrier along the path around the axis of the variator is accompanied by a change in the slope of the media and the subsequent change gear ratio of the variator.

The present invention provides wide possibilities of determination by the appropriate governing media interdependence between the offset of the carrier and the gear ratio of the variator.

In practice, the problem of the variator can be associated with prevention of "stalk" one movable component with another within the cavity bounded by the two raceways. Such problems can be expected if the media is made in the form of integral gears with full circular periphery. However, the media does not need to spin in a full 360° relative to the Central gear and ring gear, and therefore it does not need a full circular periphery. Instead, in the preferred embodiment of the present invention, the medium contains subca the second wheel, having internal and external teeth, plots, which are in General circular position for engagement respectively with the Central toothed wheel and a toothed crown.

Especially preferably, as the Central gear and the ring gear can rotate around different axes. In such embodiments of the invention, these components can be functionally connected, for example, by gearing, so that the position of one depends on the position of the other. Preferably, this design assumes that the rotation of one of them in any direction accompanied by the rotation of the other in the same direction and with a different speed. This can provide a constant ratio of speeds between the Central gear and a ring gear.

In such embodiments of the invention requires some technical solutions, which may be the Central drive gear and need to ensure it is a way to avoid touching other components of the variator, that is, rollers, carriers, etc. In a preferred embodiment, the present invention has a carrier that moves at least one satellite that communicates with the Central toothed wheel and a toothed crown. In this variant implementation of the ia of the invention the Central gear wheel, gear and satellite work together epicycle way. The Central drive gear through the crown and the satellite.

Next will be described the specific embodiments of the present invention solely as examples, with reference to the accompanying drawings, on which:

figure 1 is a greatly simplified view in partial section of a known variable, when viewed in the radial direction;

figure 2 is a view in partial section of a portion of another known variable-speed drive, when viewed in the radial direction;

figure 3 is another view in partial cut parts of the variator shown in figure 2, when viewed mainly in the axial direction, to illustrate the components that are behind him;

figure 4 is another view in partial cut parts of the variator, when viewed mainly in the axial direction, with a fully lowered raceway of the variator, which should be in the foreground, to illustrate internal components;

figure 5 is another view in partial cut parts of the variator, when viewed mainly in the axial direction, with a fully lowered raceway of the variator, which should be in the foreground, to illustrate the internal components, and in the drawing by the dotted line shows some of the internal devices;

figa is a very schematic view of the Department the high node of the roller and the media and certain associated parts of the variator according to the present invention, when viewed along the axis of the variator;

fig.6b - view site figa having a different configuration;

Fig.7 is a perspective view of some details of the composition of the carrier and bearing the same variator;

Fig is a perspective view of the roller and reinforcing rings of the same variator;

Fig.9 is a perspective view of the node that contains the roller carrier and the bearing in the layout with 7 and 8;

figure 10 and 11 is another variator according to the present invention, when viewed in the axial direction is omitted in the foreground of the raceway of the variator to illustrate internal components;

Fig is a perspective view in section along the axis of the selected components of another variator according to the present invention, is omitted in the foreground of the drawing the raceway of the variator to illustrate internal components;

Fig - type CVT with Fig, when viewed in the axial direction, with the front raceway variator also omitted to illustrate internal components;

Fig is a schematic view of another variator according to the present invention, when viewed in the axial direction;

Fig is a schematic view of another variator according to the present invention, when viewed in the axial direction;

Fig - schematic perspective view of selected parts of another variator according to us is oedema invention;

Fig is a perspective view in section along the axis of the roller node roller, holder and casing intended for use in variable-speed drives according to the present invention;

Fig - cut view in a radial plane through the variator according to the present invention, which includes a node with Fig;

Fig is a view in section through an axial plane of one of the variator according to the present invention; and

Fig is a perspective view of the carrier used in the various embodiments of the invention.

All embodiments of the invention, which will be described hereinafter, provide for the installation of each of the pulleys of the variator in an appropriate carrier, which can be tilted by means of a drive device. The principle can be understood when studying figa and 6b, which shows only one of the rollers, indicated by the reference position 200 (which is largely contained in the casing 202, which will be described later), and the carrier indicated by the reference position 204. When comparing fig.6b with figa carrier 204 is tilted about the axis 226 of the carrier so that the angle θ of inclination is not equal to zero. Short-changing the angle separates the roller axis from the intersection with the axis of the variator, and the resulting control point causes the precession of the roller to restore the crossing. Subsequent tilting of the ro is the IR corresponds to the changed ratio, which is no longer 1:1.

The design used in this and subsequent embodiments of the invention as for the installation media 204 so that he could swing around an axis 226 of the media and to drive this rocking movement, has a Central gear wheel 212 and the annular outer ring gear 214, which are both mounted concentric with the axis of the variator 218 and can be rotated around it. The carrier 204 is executed in the form of a gear wheel and is located in the space between the Central gear wheel 212 and ring gear being in mesh with both. The media cannot move along the axis of the variator, because the position of the roller on which it is placed, is determined by the raceways of the variator. Themselves raceway on these drawings are not shown, however, (as will be clear from subsequent drawings) they are located in front of the roller 200 and behind him and rotate around a common axis 218, which is referred to as the axis of the variator and is perpendicular to the plane of the drawing. The carrier can rotate around the axis 226 of the carrier, which is also perpendicular to the plane of the drawing. Provided a device for bringing media into rotation around this axis and changes thus "angle". The angle indicated on fig.6b as θ, is defined as the angle between (1) linea, outgoing from the axis 218 of the variator (i.e. the axis of the raceways of the variator), and (2) some arbitrary line 220, passing along the media. Control points required for the implementation of the precession of the roller, and then changing the gear ratio of the variator, caused by changes of the angle θ of inclination.

On figa angle equal to zero, and the variable-speed drive operates with a gear ratio of approximately 1:1. Axis 222 of the roller perpendicular to the axis 218 of the variator and crosses it, as it must be in equilibrium.

Because the range of angular displacement of the carrier is limited, it is not necessary to its outer periphery was a full circle. Instead, the media has an inner radius of the sector gear section 206 connected by passing in a generally radially outward part 208 with an outer radius of the sector gear section 210. Such structure of the carrier 204 allows you to insert it into the available space without touching other parts, such as the videos.

Consider as an example, what should happen if the Central drive gear and ring gear 212, 214 should be implemented so that they are rotated with the same speed, so they - and the carrier 204 is simply rotated around the axis of the variator, while maintaining a constant state is relative to each other. The angle θ of inclination must not be changed. If the axis 222 of the roller initially intersected by the axis 218 of the variator, as shown in Fig.6, it should be kept in this position and do not cause a change gear ratio of the variator.

However, consider what happens if the Central drive gear and ring gear is carried out at various speeds. In General, this again leads to the displacement of the carrier in a circular path around the axis of the variator. The center of the roller should be in a circle 224, which is the Central circle of the torus bounded by the raceways of the variator. However, at the same time, the carrier 204 is rotated around the axis 226 of the carrier to change its angle θ of inclination.

The roller can precession relative to the carrier 204 through the use of the bearing, through which it connects with the carrier, and the object of the present invention will now be discussed with reference to Fig.7-9. Bearing application allows the roller 200 (1) to rotate around its own axis and (2) to perform a precession around the axis 228 of precession, installed and fixed relative to the carrier 204.

The rotation of the roller 200 around its own axis is provided by a needle bearing 230 (see Fig)installed in the Central channel of the roller. The roller bearing p is meshaetsia reinforcing ring 232 (see Fig). Thanks corrugated design reinforcing ring provides some consistency between the roller and the bearing. When using the roller is exposed from the side of the raceways of the variator significant compressive force directed along the diameter of the roller. As a result, the roller runs in the danger of some elastic deformation. Reinforcing ring is elastically deformed, sensing the deformation of the roller, and thus ensures that the compressive force can withstand the movie instead of its transmission to the bearing 230. The inner raceway needle bearing 230 is formed in two parts, 234, 236, gathered around the sleeve 238 media 204 (see Fig.7). Two parts 234, 236 can be, for example, welded together with subsequent machining of their outer periphery to obtain the correct circular surface required for the inner raceway of the bearing. On the other hand, they may be bonded together by tape along their circumference (not shown), which should serve as a bearing surface. Centering protrusions 240 protrude from each side of the sleeve 238 and are concentric and aligned with the axis 228 of precession. Centering protrusions inserted into a complementary circular recess 242 in the inner surface 241 of the relevant portions 234, 236 of the inner raceway, and washers 244 from elaut the inner surface from the adjacent surfaces of the sleeve 238. The design allows the inside track 234, 236 of the rolling bearing and, therefore, set it to the roller 200 to effect precession relative to the carrier 204 about the axis 228 of precession, as mentioned above. It should be noted that the axis of precession is not located in a plane which is radial (perpendicular) relative to the axis of the variator (such as the plane of the drawing 6). Instead, the axis of precession 228 inclined to such plane, forming an angle of wheels. This point can best be understood by Fig showing the carrier 204 in the direction perpendicular to the axis 228 of precession. It is seen that the prongs 246 gear carrier rather inclined to the axis of precession, than are perpendicular to it. Position angle of the teeth of the toothed wheel determines in the present embodiment of the invention the angle between the axis of the wheel of precession and the radial plane. One of the advantages of such technical solutions are compared with applicable technical solution is illustrated in figure 2, is that the angle of the wheels is not limited to the design of the variator. In the CVT with figure 2, the maximum possible angle of the wheel is limited to the grazing of the actuator raceways of the variator. In contrast, considered here, the design provides more freedom in the choice of the angle of the wheel to which it is necessary to meet the requirements of the response speed of the variator and resistance to oscillation.

Figure 10 and 11 shows to explain the movement of carriers 204 and rollers 200. These drawings show a practical solution, in which three rollers are arranged through the right angular intervals within the toroidal cavity formed between a pair of toroidal raceways of the variator. The details of these raceways are not shown on these drawings, however, they can be formed like the tracks 12, 14, 16 of the roller shown in figure 1. The circular track, which is followed by the centers of the rollers about the axis of the variator when the media do reciprocating motion, figure 10 indicated by the reference position 224. In fact, the Central line of the toroidal cavity described raceways. In this embodiment of the invention the design of a cross with spokes 248 is used to drive the Central gear wheels 212, as will be described later.

Shown in figure 10, the regulator operates at a transmission ratio of approximately 1:1. The axis of the rollers is approximately perpendicular to the axis of the variator (the angle should be measured in the plane containing the axis of the variator, i.e. in the plane perpendicular to the plane of the drawing, and therefore cannot be identified in this image). Each axis 222 of the roller intersects the axis 218 of the variator, because they must be in balance. Under this condition, the total angle θ NAC is it every carrier 204 must be zero.

11 differs from figure 10 that the Central gear wheel 212 and gear 214 advanced clockwise, with the Central toothed wheel moves more than gear. In the result, there are a few changes:

i) since the Central gear and the ring gear rotate in the same direction (clockwise), the carriers 204 and rollers 200 also move in a clockwise direction, and the center of each roller 200 moves in a circle 224;

ii) since the Central gear wheel 212 moves faster than the ring gear 214, each carrier 204 begins to swing, i.e. to rotate around the axis 226 of the carrier, causing a change in the angle θ of inclination;

iii) changing the angle of inclination of the carrier causes the angular displacement of the axes of the rollers, briefly interrupting their intersection with the axis of the variator. Thus the rollers, as described previously applied control effect, calling them precession around the axis 228 of the precession described with reference to the storage media 204) to the illustrated positions, restoring thus the intersection. It should be obvious that the rollers are no longer perpendicular to the axis of the variator, but tilted with respect to it. Accordingly varies the gear ratio of the CVT, the CVT is actually shown in one of the positions close to the limit PE datachem respect.

It should be noted that with the Central gear and the ring gear 212, 214 may be managed by the variator. The implementation of the Central drive gear 212 is a difficult task due to the position of the gears inside the cavity of the variator. Still we proposed two different solutions. The first of these solutions is shown in figure 10 and 11, according to which the structure 248 type contains cross shaped radial parts 250, which pass through the cavity and connect the Central gear wheel 212 with the wheel on the outside of the cavity, is applied to the actuator. The wheel itself on these drawings is not in the foreground, and its perimeter is shown by the dotted line and denoted by the reference position 251. Radial parts 250 must be formed in a way to avoid touching the rollers and carriers during their movement, which depends on their shape.

The second tool for the implementation of the Central drive gear provides for the inclusion of the Central gear and ring gear in an epicycloidal design. The variator shown in Fig and 13, is one of the examples will now be described in detail. On these drawings shows the variator similar to the CVT with 6, which has two toroidal cavity. On Fig the inner lane is achene denoted by the reference position 252, and on the right side of the drawing is visible to one of the outer tracks 254 rolling. The design includes one outer raceway, which should be on the left side of the drawing, but is not shown to better illustrate other components. The media and the rollers are denoted by the reference position 204 and 200, respectively. For simplicity, Fig not shown bearing systems, connecting the media with rollers, while they are shown on Fig. Each cavity of the variator includes three roller 200 and each has an associated ring gear 214, 214' and the Central gear wheel 212, 212'. The design also contains in each cavity of the carrier 256, 256', mounted for rotation around the axis of the variator and contains a sleeve 258 and radial parts 260, which serve as support for satellites 262, and to connect drove with one-piece outer wheel 264. Each of the satellites 262 is engaged with the Central gear wheel 212 and ring gear 214, forming a gear system type epicycle. In the result, by controlling the rotation of the led 256 and ring gear 214 is controlled by the rotation of the Central gear. The principles underlying the gear system epicycle type, well-known specialists in this field of technology. This solution is convenient because the satellites 262 can be is emeny between the carriers 204 and move along with them, so avoiding the grazing one another. Like media 204 satellites 262 does not have a full circular periphery, and instead have the inner and outer sector gear sections 266, 268. Again, this helps to avoid damaging the components inside the cavities of the variator.

Need some tools to drive the Central gear and the ring gear 212, 214. On Fig this is achieved by a toothed rails 270, 272 which engages with the toothed outer periphery of the ring gear 214 and with the toothed outer periphery of the annular portion 264 drove respectively. Drive the Central gear is not directly, but through satellites 262. Two rack 270, 272 may be connected to each other so that they move together. If the movement of the rails are aimed at changing the angle of inclination of the carrier and thus leads to a change gear ratio of the variator, Reiki should drive the crown 214 and drove 256 different speeds. This is achieved in the embodiment of the invention shown in Fig, using the fact that the outer periphery of the ring gear 214 has a diameter different from the diameter of the outer wheel 264 drove. Therefore, when the reciprocating movement of the rails 270, 272 they cause movement of the ring gear and drove with various what korostil. Accordingly, the ring gear and the Central gear wheel to rotate at different speeds, causing a change in the slope of the media and, consequently, the change gear ratio of the variator.

This type of design allows you to control the torque of the variator. The Central gear and the ring gear are developing bias force, shifting each roller 200 in a circular path 224. This force counteracts the efforts applied to the roller paths 252, 254 rolling. The movement of the rollers 200 via path 234 leads to the change of the angle θ of inclination and, therefore, the gear ratio of the variator. As a result, as in the known construction described above with reference to figures 1 and 2, the variator creates a reactive torque which is determined by the bias force applied to each wheel. For the application of controlled force to the toothed rails 270, 272 requires some means, according to Fig used for this purpose hydraulic cylinder with a piston connected to the two rails 270, 272 and schematically indicated by the reference position 274. It is a unit dual action, having two working chambers 276, 278 formed in the cylinder 282 on each side of the piston 284. Thus, the control behavior of the variator is carried out by means of the pressure of the fluid applied the two working chambers 276, 278.

There are numerous alternative ways in which the necessary torque can be applied to the Central toothed wheel and a toothed crown. On Fig schematically illustrates an alternative design for the implementation of the drive gear, which is mounted on the hinge cylinder 286 contains a piston 288 connected through a piston rod 290 with eyelet 292 which is connected with the Central toothed wheel or ring gear 212, 214, or planet carrier 256. In this construction the piston 288 shall drive any of these parts gear on a straight line, and to drive the other part of the gear you need another tool.

On Fig shows a construction in which around one of the components of the gear to drive it skipped circuit 292, while the torque generated by the circuit is determined by the difference between the working pressure in the working chambers 294, 296 hydraulic actuators 298, 300, pulling the chain in opposite directions.

On Fig for application to one of the components of the gear required torque is used, the design containing the wire and the pulley. This type of design is considered to be potentially provide benefits in obtaining a compact design of the variator, as is the actuating mechanisms (not shown in the drawing, but, as should be understood, pull on the lines indicated by arrows 300, 302) is not required to align in the transverse direction with the axis of the variator. Wire 303 skipped around the component gears (which again may be a Central gear wheel 212, gear 214 or satellite 256) and around pulleys 304, 306, through which the designer can, for example, to improve the layout, choose the direction in which the actuators are drawing the line.

As mentioned above, the rollers 200 and paths 252, 254 rolling usually do not have physical contact with each other as they are separated by a thin film of fluid. Traction between the rollers and raceways occurs due to shifting efforts in this liquid film. To save the film on the rotating parts is a stream of traction fluid. The known device for feeding the traction fluid is described, for example, in the publications WO 03/062675 and EP 0930449, and based on the flow of the fluid through the media on which are mounted rollers. Submission pulling the fluid through the media is less direct in variable-speed drives of the type previously illustrated in Fig.6, due to the nature of the movement of the carrier; however, Fig and 18 illustrates one way that this can be achieved. As most clearly shown in Fig, inside media 204 formed T-obratnyiy 308 for supplying a fluid medium, leading from the open end of the inner toothed section 206 of the carrier to the appropriate Kalam 310, 312 within their respective halves 234, 236 of the inner raceway of the bearing. These channels lead into the inside needle bearing 230, and from there the fluid passes into the chamber bounded by the roller 200 and the surrounding casing 202. The housing 202 includes two similarly formed half of that collected around the roller 200 and connected between the outer flanges 318. The casing is mounted on the components 234, 236 of the inner raceway of the bearing, and therefore moves with the roller 200. He has a cut, denoted by the reference position 320 at 6, 10 and 11, in order to ensure the cooperation of the roller 200 with paths 252, 254 rolling of the variator. Along with the function implementation clutch between the rollers and raceways of the progressive transmission fluid serves to cool the rollers. The illustrated construction provides by supplying the fluid to the inner radius portion of the clip and through the use of a casing for a long period of fluid around the roller, which ensures efficient cooling.

The bypass tube 322 is inserted in the open end of the channel 308 for supplying a fluid medium, and a radial hole 324 of the Central gear wheel 212, forming a passage for passing the fluid from poslednego to the first. The angle between the channel 308 and the opening 324 is changed by tilting the media, and the perception that the bypass tube 322 has a partially spherical head 326, 328, each of which can turn a little, preserving the integrity. Fluid flows through the axial channel to achieve radial holes 324.

On Fig shows an axial section of the variator according to a variant of embodiment of the present invention and shown as part of the two cavities of the variator can be connected together. Shows only half of the variator, with one side of the axis of the variator 218. The shaft of the variator 330 is connected through a not shown gear with the engine of the vehicle. Raceway variable denoted by reference positions 252, 254, and 255. Left outer track 255 roller mounted on the shaft of the CVT 330 the dowels that allow it to move along the shaft and eliminate its rotation relative to it. She is the "ultimate load" side of the hydraulic actuator formed by the cylinder 332, which itself is mounted on the shaft of the variator 330 and receives the outer track 255 rolling elements in the form of a piston. Right outer track 254 rolling fixedly mounted on the shaft and an inner track 252 rolling has some freedom of axial movement by bearing 334 on which it is installed is. As a result, the effect of a finite load is the introduction of all three raceways in contact with the rollers 200, providing the traction rollers and raceways. In this drawing, the rollers 200 are shown in three different positions corresponding to the transmission ratio 1:1 and the largest and smallest existing transfer relations, respectively, with the latter two positions indicated by the dotted line.

In this drawing, the Central gears 212, 212' in two toroidal cavities of the variator shown as United first sleeve 336, located around and concentric with the shaft 330 of the variator, causing movement of the two Central gears in unison. Two led 256, 256' are connected to the second sleeve 338, and in this embodiment of the invention the radial parts 260, 260' drove arranged in pairs with the planetary shaft 340 mounted between each pair for setting the appropriate satellite 262 bearings 342. Toothed outer part of the wheel carrier indicated in the previous drawings, the reference position 264. Sprockets 214, 214' in this embodiment of the invention located between the parts 260, 260' of the corresponding led. The design allows you to apply force to the actuator to epicycle components only one cavity of the variator and pass it through the liner components is applying to ingredients in the other cavity.

On the inner track 252 rolling variator must be submitted and/or to take away from her the rotating force of the actuator, and in many applications it is desirable to do so through the element, which rotates around the axis of the variator (instead of the tools with chain or gear, leading to displacement of the shaft from the axis of the variator). Is coaxially connected with the inner raceways may be relatively difficult to implement the invention with the existing structures of the variator, in which the control mechanism rollers located radially outside of the cavities of the variator. However, in the present embodiment of the invention coaxial power connection on a straight line can be achieved using a rotor 344 connected to the internal path 252 rolling variator and passing through the axis beyond the rightmost outer track 254 rolling, and the outer part of the rotor is connected with another gear (not shown). This simple form of coaxial connections are possible due to the fact that the gears in the right cavity of the variator substantially contained within the cavity, having a large radial protrusions that could hurt the rotor.

1. The device continuously variable gear ratio, containing the first and second raceways that are installed to rotate the district common axis (the axis of the variator"), and at least one roller, which is connected with the carrier for rotation about the roller axis defined relative to the carrier, and which rolls on both raceways for power transmission drive between them at a variable transmission ratio, characterized in that it further comprises a concentrically located Central gear and the crown gear, and the carrier has teeth, through which it engages with the Central gear and a ring gear, and the connection between the roller and its carrier provides the possibility of precession relative to the carrier about the axis of precession, which is defined relative to the carrier and not parallel to the axis roller, so that the relative rotation of the Central gear and the ring gear causes rotation of the carrier around its axis that is not parallel to the axis of the roller and the axis of precession, the resulting precession of the roller and the respective change gear ratio of the variator.

2. The device according to claim 1, characterized in that the axis of the carrier passes through the center of the roller.

3. The device according to claim 1, characterized in that the axis of the medium is parallel to the axis of the variator.

4. The device according to claim 1, characterized in that the axis of precession is always inclined at a nonzero angle of the wheels to the plane perpendicular to the axis of the variator./p>

5. Device according to any one of claims 1 to 4, characterized in that the axis of precession passes through the center of the roller.

6. The device according to claim 1, characterized in that the carrier is made with the possibility of reciprocating movement along the path around the axis of the variator.

7. The device according to claim 6, characterized in that it comprises means for the application of controlled force to a Central toothed wheel and a toothed crown for displacement of the carrier along its trajectory.

8. The device according to claim 1, characterized in that the carrier comprises a gear wheel with an incomplete circular periphery, containing the inner and outer toothed area on a common circular position for engagement respectively with the Central toothed wheel and a toothed crown.

9. The device according to claim 1, characterized in that as the Central gear and the ring gear rotate around the axis of the variator.

10. The device according to claim 9, characterized in that the Central gear and the ring gear are connected so that the position of one depends on the position of the other.

11. The device according to claim 9, characterized in that it further comprises a carrier mounted for rotation around the axis of the variator and moving at least one satellite, which is in mesh with the Central gear and a ring gear.

12. The device according to claim 11,characterized in that the Central drive gear is carried out by means of the ring gear and planetary gear.

13. The device according to claim 1, characterized in that it further comprises a rack with linear movement, interacting with at least one of the Central gears and gear.

14. The device according to item 13, wherein the Central gear and the crown gear is made with the possibility of bringing one or more racks with linear movement.

15. The device according to claim 1, characterized in that it further comprises a linear actuator for the application of controlled forces and means to convert this force into torque applied to at least one of the Central gears and gear.

16. The device according to item 15, wherein the linear actuator is a hydraulic mechanism.



 

Same patents:

FIELD: machine building.

SUBSTANCE: invention relates to device for changing of transmission ratio, particularly to gears with rolling engagement in toroidal track. Variator contains input disk (18, 20), installed rotary; output disk (22), installed rotary co-axial with input disk (18, 20); rollers (30, 32), by means of which it is passed rotation between input disk and output disk; pistons (36, 38) of double-acting, each of which interacts on corresponding one of rollers. Variator also contains levers (44, 60), each of which is connected to corresponding one of rollers (30, 32) and connected to it positioner (36, 38), influencing on roller for control of transmission ratio of variator.

EFFECT: creation of considerabl more packaged design of variator.

40 cl, 9 dwg

FIELD: machine building.

SUBSTANCE: variable-speed drive unit comprises master and slave toroidal wheels (2, 3) and roller (6). Their generatrices are made in the form of convex and concave curved surfaces. Due to arrangement of generatrices of working surfaces in master and slave elements in accordance with a certain dependence, area of friction pairs contact is increased.

EFFECT: improved kinematic characteristics of variable-speed drive unit.

3 dwg, 1 tbl

FIELD: machine engineering, namely variable speed drives with continuously changing relation of revolution number of driven and driving shafts.

SUBSTANCE: friction tore ring type variable speed drive includes driving and driven discs made of set of rings 2, 3 forming together toroidal surface and joined with driving and driven shafts 1, 4 through tie rods 12, 16 at spring-loaded gap outside aid tie rods. Rings 2, 3 may move one relative to other and relative to driving and driven shafts along splines in parallel to main axis of variable speed drive. Ball 10 is used as frictional intermediate member between them; said ball transmits rotation of rings of driving disc to rings of driven disc and it rotates in holder 5 in direction set by means of rings and around main axis of variable speed drive. Actuating mechanism successively forces mutually opposite rings of driving and driven discs for providing their friction contact. Monitoring and control mechanism includes control gear wheel 8 working in pair with ring-like gear wheel 7 secured to holder 5; flat coiled spring whose one end is joined with housing and whose other end is joined with holder 5 or with control gear wheel 8.

EFFECT: improved design, simplified process for monitoring and controlling gear ratio.

5 cl, 7 dwg

FIELD: mechanical engineering.

SUBSTANCE: device comprises casing (160) mounted in the vicinity of roller (100) and pipeline for supplying fluid. Peripheral section (162) of the inner side of casing (160) is positioned close to the outer periphery of the roller. Two radial sections of the inner side are in the vicinity of appropriate side surfaces of roller (100). As a result, a chamber for supplying fluid is formed between roller (100) and casing (160). The pipeline for supplying fluid is mounted for permitting supply of fluid to the chamber for receiving fluid.

EFFECT: enhanced reliability.

14 cl, 10 dwg

FIELD: mechanical engineering.

SUBSTANCE: friction toroidal variator comprises inlet disk (2) and outlet disk (3) provided with toroidal surfaces, friction roller (5), spider whose one axle is provided with roller (5), holder (8) of friction roller, control mechanism, and mechanism for control of gear ratio. The second axle of the spider is fit in holder (8) of the friction roller that can rotate around the main axle of the variator. The control mechanism and mechanism for control of gear ration are made of gear sector (9) that rotates on the second axle of the spider secured to the first axle of the spider and housing (12) by means of worm gearing and spring (15) secured in housing (12) and connected with holder (8) directly or through the reduction gear.

EFFECT: simplified control and control of gear ratio.

8 dwg

Roller device // 2226631
The invention relates to rollers and cooling during use, in particular to the rollers used in variable-speed drives with toroidal raceway

The invention relates to mechanical engineering, in particular to a device transmission with stepless gear ratio

The invention relates to a control system variable speed drive designed, for example, for use in the infinitely-variable transmission

The invention relates to a positional servo system, in which the definition of the error between the desired relative positions resulting in action t

FIELD: mechanical engineering.

SUBSTANCE: friction toroidal variator comprises inlet disk (2) and outlet disk (3) provided with toroidal surfaces, friction roller (5), spider whose one axle is provided with roller (5), holder (8) of friction roller, control mechanism, and mechanism for control of gear ratio. The second axle of the spider is fit in holder (8) of the friction roller that can rotate around the main axle of the variator. The control mechanism and mechanism for control of gear ration are made of gear sector (9) that rotates on the second axle of the spider secured to the first axle of the spider and housing (12) by means of worm gearing and spring (15) secured in housing (12) and connected with holder (8) directly or through the reduction gear.

EFFECT: simplified control and control of gear ratio.

8 dwg

FIELD: mechanical engineering.

SUBSTANCE: device comprises casing (160) mounted in the vicinity of roller (100) and pipeline for supplying fluid. Peripheral section (162) of the inner side of casing (160) is positioned close to the outer periphery of the roller. Two radial sections of the inner side are in the vicinity of appropriate side surfaces of roller (100). As a result, a chamber for supplying fluid is formed between roller (100) and casing (160). The pipeline for supplying fluid is mounted for permitting supply of fluid to the chamber for receiving fluid.

EFFECT: enhanced reliability.

14 cl, 10 dwg

FIELD: machine engineering, namely variable speed drives with continuously changing relation of revolution number of driven and driving shafts.

SUBSTANCE: friction tore ring type variable speed drive includes driving and driven discs made of set of rings 2, 3 forming together toroidal surface and joined with driving and driven shafts 1, 4 through tie rods 12, 16 at spring-loaded gap outside aid tie rods. Rings 2, 3 may move one relative to other and relative to driving and driven shafts along splines in parallel to main axis of variable speed drive. Ball 10 is used as frictional intermediate member between them; said ball transmits rotation of rings of driving disc to rings of driven disc and it rotates in holder 5 in direction set by means of rings and around main axis of variable speed drive. Actuating mechanism successively forces mutually opposite rings of driving and driven discs for providing their friction contact. Monitoring and control mechanism includes control gear wheel 8 working in pair with ring-like gear wheel 7 secured to holder 5; flat coiled spring whose one end is joined with housing and whose other end is joined with holder 5 or with control gear wheel 8.

EFFECT: improved design, simplified process for monitoring and controlling gear ratio.

5 cl, 7 dwg

FIELD: machine building.

SUBSTANCE: variable-speed drive unit comprises master and slave toroidal wheels (2, 3) and roller (6). Their generatrices are made in the form of convex and concave curved surfaces. Due to arrangement of generatrices of working surfaces in master and slave elements in accordance with a certain dependence, area of friction pairs contact is increased.

EFFECT: improved kinematic characteristics of variable-speed drive unit.

3 dwg, 1 tbl

FIELD: machine building.

SUBSTANCE: invention relates to device for changing of transmission ratio, particularly to gears with rolling engagement in toroidal track. Variator contains input disk (18, 20), installed rotary; output disk (22), installed rotary co-axial with input disk (18, 20); rollers (30, 32), by means of which it is passed rotation between input disk and output disk; pistons (36, 38) of double-acting, each of which interacts on corresponding one of rollers. Variator also contains levers (44, 60), each of which is connected to corresponding one of rollers (30, 32) and connected to it positioner (36, 38), influencing on roller for control of transmission ratio of variator.

EFFECT: creation of considerabl more packaged design of variator.

40 cl, 9 dwg

FIELD: machine building.

SUBSTANCE: invention relates to rolling variator, particularly to control mechanism by roller orientation. Device of infinitely variable control of reduction ratio (variator) contains couple of rotating rolling path, installed for rotation around its common axis (218) of variator. Drive force is passed from one rolling path to the other by means of at least one roll (200), running by it. Connection between roll (200) and its carrier (214) provides roller precession relative to around axis (228) of precession, where it is defined relative to axis of precession and non-parallel to roller axis. Precession leads to changing of angle between axis (222) of roller and axis (218) of variator and corresponding to changing of reduction ratio. Carrier itself allows toothing (206), by means of which it is engaged with central tooth gear (212) and gear rim (214). Rotation of carrier (204) around axis of carrier serves to changing of axle orientation (228) of precession and accompanied by changing of reduction ratio of variator.

EFFECT: invention provides by means of control of displacement of carrier to change reduction ratio of variator.

16 cl, 21 dwg

FIELD: machine building.

SUBSTANCE: variator transmission consists of input shaft (18), input disk (10) installed on input shaft and rotating with it and output disk (12) facing input disk and coaxially rotating with it. Input and output disks (10, 12) form a toroid cavity between them. In the toroid cavity there are positioned only two rollers; also the first and the second rotating rollers are arranged on the first and the second roller carriages. Facility (34, 36) of end load holds rollers down to contact with the input and output disks for motion transfer. Two roller carriages are mounted on opposite sides from the axis of lever pivot. Pivot axis of the lever travels in one, preset radial direction relative to rotation axis of input and output disks.

EFFECT: simplified and inexpensive variator.

27 cl, 3 dwg

Variator // 2413888

FIELD: machine building.

SUBSTANCE: variator consists of two races made for rotation around common axis. Opposite profiled surfaces of races restrict circular space containing at least one roller (38) transferring driving force between races. The roller is installed on the carrier (42) so, that its incline to common axis can vary to facilitate changes of variator ratio. The rollers and their carriers are controlled by means of a mechanism consisting of solar (46) and circular (50) gears interacting with the carrier. Relative rotation of the solar and circular gears causes an incline of carrier (42) so, that rollers turn to a new incline. There is disclosed satellite (100) controlling solar and circular gears and interacting with both. Rotary position of the carrier is controlled independently from its interaction with solar and circular gears.

EFFECT: improved control of rollers orientation.

16 cl, 11 dwg

FIELD: machine building.

SUBSTANCE: device consists of control part actuated by user for control of ratio (lever (50) and of device of working connection (rollers (18) of control part for regulation of ratio with movable part for transfer of variator torque. The connecting device corresponds to a hydro-mechanical arrangement. When a user actuates control part (50) for regulation of ratio there is regulated ratio of variator. The device also has the appliance for turning torque off (valve (60) actuated by a user for disconnection of the part for regulation of the ratio from the movable part for transfer of torque.

EFFECT: simplification of design.

17 cl, 3 dwg

FIELD: transport.

SUBSTANCE: invention discloses planetary variator, combination of reverse variable transmission system comprising these planetary variators, hydraulic system for reverse variable transmission control and method for this hydraulic system regulation.

EFFECT: higher engine efficiency due to lower specific fuel consumption.

12 cl, 13 dwg

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