The variator with the force transmission rollers on toroidal surfaces

 

(57) Abstract:

Usage: the machine mechanisms with changes in the transmitted torque. The inventive variable contains the input and output disks, interacting with them a set of rollers, each of which is connected with the piston double-acting installed inside the hydraulic cylinder. All hydraulic cylinders are on one side of the plane passing through the axis of the disks. 6 C. p. F.-ly, 4 Il.

This invention relates to a transmission with traction rolling doughnut-track type. It refers in particular to the components of the change gear ratio, or "progressive" for such transmission, the variator such that each of the sets of rollers that transmit thrust between the input disk and the output disk is connected with a hydraulic mechanism with which it is in the desired position, and the position of the roller is a key factor in establishing the gear ratio.

The variable-speed drives of this type are well known in the prior art and the patent publication GB-A-1395319, GB-B-2107009, EP-B-0078125 and EP-B-0133330

some of the many patents, in which the positioning system roller GU from rotating input drive to coaxially, rotating in the opposite direction to the output disk, and each roller is rotated relative to the other on the 120orelative to the common axis of the disks. In each of the four patents gear ratio from the input disk to the output on each of the rollers force is changed by changing the position of this spot is mainly in the direction of the tangent to the circle center General torus formed by the raceways of the input and output disks. In each of these four patents mechanism or messages such movement tangentially, at least some of the rollers includes pistons made at opposite ends of the caliper roller, i.e., structure, carrier bearings on which the roller rotates and the movable hydraulic cylinders.

It is clear that such a mechanism includes a lot of parts, because each of the two cylinders associated with each piston requires a sustainable mechanism for maintaining them in fixed position despite the movement of the piston within the cylinder and despite the changes in the interaction between the piston and the cylinder. In addition, each cylinder must be connected to the input and output hydraulic conclusions. These conclusions is which they will be subjected, and the symmetrical arrangement around the axis of the transmission, means that the findings will also be located around the circumference of the transfer, for example, sealed inside the gear or even, perhaps, to speak of him. This creates many difficulties. For example, the cost of the full formation of channels within the body molding, the difficulty of manufacturing sealed for high pressure connections with such channels, the need to maximize the diameter of all channels to minimize resistance to flow, protection against damage to these parts, if any of the channels displayed and the lock is available for the Assembly of the rollers and calipers.

It was also suggested, for example, in patent GB-A-1600972 and in more detail in our International patent N W 0 90/05860, to control the tangent position and angle relationships of each clip through only one piston-cylinder arrangement located only at one end of the support roller. For a typical set of three rollers clear that this will reduce the number of cylinders in two times, and therefore reduced the problem of protection from damage and access, which have already been mentioned, but none of the patents does not indicate that the three operating cylinder would respolice. The above-mentioned problems, therefore, are preserved.

The present invention is based on the position that if each roller is positioned only one hydraulic operating mechanism, as just described, it gives the opportunity to modify the location of the three mechanisms so that they in General are only on one side of the common axis of the disks, which gives the opportunity to solve some of the problems already mentioned above. The invention applies in particular to variable-speed drives, as shown in all the previous patent publications up to the present time indicated by corresponding numbers in which the configuration of the toroidal cross-country tracks, performed on the input and output discs is such that the radius from the axis of the disk to the point of contact between each of the tracks and the roller may vary across the range, including values larger and smaller than the distance from the disk axis to the center of the circle shared the Torah.

The invention is defined by the formula, the content of which shall be deemed to be included in the disclosure of this patent and the invention will now be described by example with reference to the accompanying drawings, in which: Fig. 1 depicts schematically the variator, partial rasme six operating cylinders of dvukhkontsevoi" infinitely variable transmission (PDU) with traction rolling doughnut-track type; Fig. 4 schematically options 6' and 6" cylinder, controlling the roller shown in Fig. 1, will be placed among the six cylinders is shown in Fig. 3.

In Fig. 1 roller 1 for use in the variator of the toroidal-track PDU is installed through the bearing 2 on the support 3, one end of which tapers and becomes the core 4, at the far end of which is formed by the piston 5 double action, which moves inside the cavity of the cylinder 6, the controlling roller is formed in the cylinder block 7. Rounded end edges 8 of the piston 5 allow the piston 5 is slightly tilted inside the cylinder 6, and move the reciprocating along the axis 9 of the cylinder so that the center 10 of the roller 1 is able to move not only up and down on the same axis, but deviate from it, although the distance from the center 10 of the roller to the center 11 of the piston 5 remains fixed. The front end of the cylinder 6 is closed by the gasket 12, held in place with the lock spring ring 13, and the Central element 14 of the strip 12 is capable of limited radial movement relative to the axis 9 of the cylinder so as to allow the center 10 of the roller 1 to make just described movement. The piston 5 divides the cylinder 6 into two chambers 15 and 16. For cylinder 6 in Fig. 1 I is below the axis 9 of the cylinder. In both of these embodiments, the camera 15 is formed with an annular groove 17, and the camera 16 with a similar groove 18. Position 19 schematically shows a suitable annular element attached to the left side of the piston 5 in both cases (6' and 6") cylinder 6, and to the right side of the piston only in version 6'. Where there is such a connection element 19 prevents direct contact between the piston and the inner wall 20 of the strip 12, as soon as the piston 1 is outside the specified left-hand limit of its movement within the cylinder and between the piston and the end wall 21 of the cylinder when the piston 1 is outside the specified right of its motion.

A typical variable-speed drive, such as PDUs, will include a set of three such rollers 1, and each roller is controlled by the combination of a piston-cylinder 5/6, with three cylinder included in the total hydraulic control circuit. And yet, more typical, as shown in Fig. 3, 4, is the case when two such set, which together constitute the six rollers are controlled by a common hydraulic circuit. This circuit, which in General type described in detail in patent N W 0 90002277 contains two pumps 25 and 26, two valve pressure 27 and 28 and the output 29. The relative setting of the valves electronnogo control device 30, which receives the input signal to start the drive, engine speed, road speed and all other required parameters. Through one of the chambers 15 or 16 of each of the cylinders 6 pump 25 communicates with the valve 27, the pressure and the output 29. Through the other of the chambers 16 or 15 of each of the cylinders 6 other pump 26 communicates with another pressure valve 28 and also with the output 29. In Fig. 1 in one example, the camera 15, attached to the pump 25, the camera 16 to the pump 26 and valve 28 and the output 28. However, the way in which all the chambers 15 and 16 are combined in groups between the pumps 25 and 26 and their respective valves pressure 27 and 28 so as to provide proper and consistent operation of all six rollers in the traditional "dvukhkontsevoi" system, as shown in Fig. 3, 4, will be described hereinafter with reference to these figures. In each cylinder 6 mounted in accordance with option 6', the chamber 15 of the cylinder connected with one of the pumps (as shown, the pump 26) with the grooves 18 and the valve 32. However, option 6" cylinder thickening 33 on the end of rod 4 is made to approach the edge 34 with the removed facet of the cavity 35, is made in the far wall 21 of the cylinder. The camera 15 is also connected to one of the pumps 25 and 26 through ditches the spine of 35 and channel 37 with the respective pressure valve (27 or 28) and thus, with the output 29. When the piston 5 is in the normal limits of its travel within the cylinder 6, the cavity 35 is not closed, and the amount of liquid, the current through the chamber 16, is determined by submission of the attached pump (25 or 26), and by setting the appropriate pressure sensor (27 or 28). The piston 5 would have to go beyond the normal size of its stroke when moving to the right in the cylinder 6", however, the approximation thickening 33 to the edge 34 restricts fluid flow in the channel 37 and, thus, increases the fluid pressure in the chamber 16, providing the effect of the hydraulic stop trying to resist further movement of the piston 5 to the right. If you are unable therefore to control excessive movement of the piston, the thickening 33 encounters an edge 34 that provides a physical stop.

Fig. 1 also shows partially (reference 38) fragment toroidal treadmill one of the drives (40, see Fig. 2 and 3), between which the roller 1 will transmit thrust.

Combination roller, support and operating mechanism of the double-acting piston-cylinder just described with reference to Fig. 1, is very similar to the dual-action mechanism, described in patent N 0 90/05860. ACC is x traction between the input disk (not shown in the drawings) and the input disk 40, mounted on a single stable carrier structure 41, generally rectangular shape and having a flat upper surface 42 so that the three blocks (marked in Fig. 3 as 7a, 7b, and 7c) lie on the same side of the common plane 43a containing the common axis 43 drives, and they all crossed another common plane (as shown, which is the transverse plane 43b to the section line 1-1), which is essentially parallel to the axis 43 and offset from it. As shown in Fig. 1, block 7 of Fig. 2 will also be connected to the pumps 25 and 26 and with pressure sensors 27 and 28 through channels 31, 32 and 37, but now these channels are mostly contained in the structure 41, as shown schematically in example 31a, 32a and 37a. If these structures are solid, the channels can be formed by drilling in the structure, one of such holes 44 shown in Fig. 2. The pumps 25 and 26 and the pressure sensors 27 and 28 can be placed within the structure, as shown schematically in Fig. 2, this further simplifies hydraulic connection that needs to be done.

Another advantage of the invention is shown in Fig. 2. If the arrow 45 indicates the direction of rotation of the output disk 40, then, obviously, the roller 1a follows the cylinder relative to this direction and the order reversed: the cylinder 6c followed his roller 1c relative to the direction 45. This, however, does not pose a special problem for rollers with hydraulic operating mechanism double action, which is shown in Fig. 1; all that is required is that the camera 15 16 cylinder 6c were connected with the same pumps that camera 16 15 cylinders 6a and 6b. In Fig. 2 lines 46 and 47 show the inner and outer radial extremity of the partially toroidal treadmill 48 formed on the output disc 49 on which the rollers 1a, b, c will roll, and line 49 shows the line paaradise, i.e. the radius of (49a) is equal to the common radius of the torus. This is the radius at which each of the rollers will roll when it is in the position of the roller 1a, when the axis of rotation of the roller intersects the axis 43 of the disk and the roller passes the rod with gear ratio 1, so that the output disk 40 rotates with the same speed as the corresponding input disk (51, Fig. 3), but in the opposite direction.

Fig. 3 shows the cylinders 6a, b and c, and the cylinder 6d, e and f for the second set of rollers of dvukhkontsevoi" toroidal-track PDU, and a contour line shows the input and output disks. As is customary in such two-sided blocks, the input disk 50 at one end of the variator connected to the input shaft 53 to I is that it can freely rotate around the shaft 53. Slip joint 39 between the shaft 53 and the disk 51 permits axial movement between the shaft and the disk that meets the end of the heating power, as is clear from the previous level of technology. The rollers 1a, b and c (Fig. 2) transmit thrust between the treadmill 55 on the disk 51 and the treadmill 48 on one side of the output disk 40, and three roller (not shown, but which is referred to as 1d, e and f) to another set (controlled cylinders 6d, e and f) transmit thrust between the input disk 50 and a treadmill on the opposite side of the output disk 40. The efficiency of such dvukhkontsevoi toroidal-track PDU requires among other achievements, three special purposes. First, of course, each of the rollers from 1a to 1f must pass the same ratio between their respective input and output disks, which require that the corresponding piston 5 was exposed to the same purely hydraulic power through the volume of fluid inside the chambers 15 and 16, and its corresponding cylinder 6. Secondly, since connections between the chambers 15, 16 and pumps 25, 26 in Fig. 2 reversed for the cylinder 6c in comparison with the cylinders 6a and 6b, one of the cylinders 6d, e, f must be similarly reversed otnositelnaya option 6", the latter of the above cylinders are reversed relative to each other so that the first of them produces hydraulic stop if the rollers are striving to overcome one of the permissible limits of their range of gear ratio, and the second produces a similar effect on other allowable limit. This embodiment is shown in Fig. 4. As shown in Fig. 2, one of the cylinders (6c) of the first set of three rollers reversed in direction with respect to the other two cylinders 6a and 6b. Similarly for the second set of rollers cylinder 6f reversed in direction with respect to the cylinder 6d and 6e. Therefore, the cylinders 6a, 6b, 6d and 6e are directed in the same direction (relative to the direction of rotation of the arrow 45 of the output disc 40), and cylinders 6c and 6f are directed in the opposite direction. The common manifold 52 is connected to the feed pump 25 and, therefore, is connected with the chambers 15 of the cylinder 6a, b, d, c, and cameras 16 cylinder 6c and f, thus providing equal pressure in all of these six chambers. Similarly, the collector 56, connected to a pump 26, is connected also with cameras 16 cylinders 6a, b, d, e and chambers 15 of the cylinder 6c and f. In order to make two hydraulic circuit pumps 25 and 26, it is only necessary that two of the six cylinder hydraulic stop, when the rollers can go beyond the limits of normal values of the gear ratio, two cylinder options 6" can be reversed in direction. In Fig. 4 two such cylinders are cylinders 6c and 6e. The chamber 16 of the cylinder 6c completes the circuit between the pump 25 and the corresponding pressure sensor 27, the camera 16 cylinder 6E completes the circuit between the pump 26 and the respective sensor 28. If the pistons are aiming to go beyond the left margin of normal values of their course, the restriction of flow in the channel 37 from the chamber 16 of the cylinder 6c will effect the hydraulic stop and thus increase the pressure in the reservoir 52 and, if the pistons are aiming to go beyond the right margin of normal values of their stroke, the effect of hydraulic stop will occur in the chamber 16 of the cylinder 6e, thereby increasing the pressure in the reservoir 56.

Fig. 3 shows the best way that the axis 9 of the cylinder 6 are floor angle relative to the transverse planes 57, which include the total circumference of the torus discs, between which the rollers are positioned with their cylinders, transmit thrust. The angle is known in the prior art as casting angle, will con the formation (MRF). The presence of a casting angle helps to make possible the mounting blocks 7 cylinders 6a, 6c and 6d, 6f close one along the other, as shown in Fig. 3; if the angle is very small or equal to zero, it would be obvious that the cylinder blocks were faced one another, if you try, as in Fig. 3, to mount three blocks in a single common plane on the surface 42 of the structure 41. With small or zero casting angles, therefore, an alternative arrangement of these cylinders would have to be found to avoid their collision with each other. The cutout 58, made at the corner of each block 7 of the cylinder shown in Fig. 2 and 3, gives space to the outer edge of the disc 50, 51 and 40. Although there has been described a solid or porous, and in General a rectangular design for patterns 41, alternatives are possible within the invention. For example, more open frame comprising two parallel and joined beams, one of which supports the cylinder blocks 6a, 6c, 6d and 6f (Fig. 3), and the other cylinder blocks 6b and 6e. This design again would have the effect of location of all six cylinders and blocks on one side of the axis 43 rather than the symmetrical arrangement of the cylinders around her and offered E-force transmission rollers on toroidal surfaces, contains the input and output disks, interacting with them a set of rollers, each of which is connected with the piston double acting installed inside the hydraulic cylinder, wherein all hydraulic cylinders lie on one side of the plane passing through the axis of the disks.

2. The variator under item 1, characterized in that all the hydraulic cylinders are located on a common ground.

3. The variator under item 1, characterized in that all hydraulic cylinders are intersected by a single plane that is parallel to the axis of the variator.

4. The variator under item 1, characterized in that the set of rollers comprises three rollers are equally spaced from each other in the circumferential direction, and the direction of the line connecting the piston with the center of one of the rollers relative to the direction of rotation of one of the disk opposite to the direction corresponding to the other two videos of this set.

5. The variator on p. 4, characterized in that all the hydraulic cylinders of the three rollers is offset from the plane that includes the Central circle of the General torus two disks, and installed it at an angle.

6. The variator under item 5, wherein the two hydraulic cylinders of the three Liski cylinder on the other side.

7. The variator under item 1, characterized in that a common basis has the form of a rectangular block located in the hydraulic channels connected to the hydraulic cylinders.

 

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