Device for supplying fluid to continuously variable roller gearbox

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

 

Description

The present invention relates generally to continuously variable boxes transmission ("CVT") roller type, and more precisely to a device for supplying the fluid to the roller of such a variable.

The main components of the known roller variator 10 with a toroidal groove of the roller illustrated in figure 1. In this case, the two introductory (leading) of the disk 12, 14 mounted on the control shaft 16 for rotation with it, and have corresponding partially toroidal surfaces 18, 20, facing in the direction of the corresponding partially toroidal surfaces 22, 24 formed on the Central output (slave) disk 26. The output disk is mounted on axis with the possibility of its rotation independently of the shaft 16. The driving force from the engine or other primary propulsion is transmitted through the shaft 16 and the input disks 12, 14, is transmitted to the output disc 26 through a set of rollers arranged in a toroidal cavities. Illustrated one typical roller 28, but, typically, three such rollers are provided in both cavities. End load applied to the input disks 12, 14 through the hydraulic end of the device 15 for the application of the load, provides the contact forces between rollers and discs to enable transmission of the driving force. Driving the sludge (torque) is transmitted from the output disk additional parts of the transmission, typically, the epicycle mixer, as is well known in the art and described, for example, in the application 85308344.2 on European patent application (published as EP 0185463). Each roller is mounted on a respective support element 30, which is itself attached to the hydraulic power cylinder 32, resulting in an adjustable force, providing the progressive movement, can be applied to the combination of the roller and the bearing member along a direction essentially tangential to the main axis defined by the shaft 16. The power cylinder 32 contains a hydraulic piston 34, is able to turn within its corresponding cylinder 36. Such rotation of the piston is connected with a corresponding rotation (or "precession") axis of the roller around the so-called axis, such axis rotary wheel, which in the illustrated structure represents the axis of the piston 34. As obvious to the specialist, this precession of the axis of the roller leads to a change in the relative diameters of the trajectories, which rolls the roller 28 on the disks 12, 14 of the variator, resulting in a change gear ratio of the variator. Because the rollers are always striving oriented position in which their axes intersect the axis of the drive shaft 16, they automatically shift and precession in a position in which the so-called react wny torque is determined clamped force, the current from the power cylinder 32. Thus, the variator of figure 1 can be characterized as a regulator regulating a torque.

However, the present invention is potentially applicable to a roller of variable-speed drives of other types, including those known in the art as "partially" or "half" toroidal.

In known roller variable speed drives variable not included in direct contact with the rollers. Instead supported the presence of a film of fluid, called "fluid medium for transmitting traction (traction fluid)", between the surfaces of these elements, and the driving force is transmitted between them due to the shift of this film. Maintaining the film is of the utmost importance, since direct contact of the rollers with the disks causes excessive wear.

Fluid also performs the important function of cooling the parts of the variator, in particular rollers. In variable-speed drives, which represents the closest analogues of the invention, the working temperature of the rollers is an important factor in determining the power of the variator. The shearing forces in the contact area between the disk of the variator and rollers lead to heat, causing an increase in the temperature of the rollers (and to a lesser extent disks). Excessive temperatures can (1) cause is the damaged themselves rollers (steel, from which they are made, subject to change with long-lasting high temperatures); and (2) adversely affect the operating characteristics of a fluid medium for the transmission of tractive effort, because high temperatures and the resulting low viscosity fluid lead to the formation of more than a thin layer of fluid between the disk and the roller and stronger slippage between these parts. Long lasting high temperature with time can lead to changes in the properties of the fluid undesirable way.

In practice, it is established that the power of the variator is limited by the speed of heat dissipation from the rollers, making improvements in this direction are very important.

Device for supplying a fluid medium to transmit traction to the variator rollers owned disclosed in the applicant's European patent 890044 and its equivalent U.S. patent 5971885. In this device the flow of fluid to transmit traction passes through a node, consisting of a power cylinder and a bearing element, to the number of nozzles located near the outer periphery of the roller. Thus, the sprayed fluid is supplied to the periphery of the roller.

There are important business drivers for improving the efficiency of fluid for PE is Adachi traction. Create the desired fluid flow requires energy and thus reduces the overall efficiency of the gearbox; improvements in the use of the fluid creates the possibility of reducing the volume flow and, consequently, the corresponding energy needs. In addition, studies have shown that the residence time of the fluid on the roller surface, usually less than desirable from the point of view of maximizing the heat from the rollers. Increasing this time also creates the possibility of reducing the volume of flow, but, in addition, or alternatively leads to increased cooling effect of the rollers and thereby potentially creates the possibility of increasing the ability of the regulator to transmit power and/or reduce the temperature of the rollers, which can lead to increased service life of the rollers.

The condition for the existence of the casing in the vicinity of the roller was proposed in 1938 W.T.Murden (U.S. patent 2132751), but as far as known to the applicant, the idea was not accepted in the art, and presumably, due to the shape of the casing - it contains only partly round the rim near the outer edge of the roller - its effectiveness would be limited.

In accordance with the present invention a device for supplying a fluid medium, designed for roller best penati transmission, in which the driving force is transmitted from one groove rolling to another using at least one rotating roller, the outer circumferential periphery of which is in rolling grooves, the device for supplying a fluid medium includes a casing installed in the vicinity of the roller, and the line for supplying the fluid and differs in that the casing has an inner surface having a circumferential peripheral portion, which is adjacent to the outer circumferential periphery of the roller, and two passes in the radial direction of the part that are close to the corresponding side surfaces of the roller, causing the roller casing forms a chamber for receiving the fluid, and the line for supplying the fluid placed with a possibility of the fluid in the chamber for receiving a fluid medium.

The preferred implementation of the present invention is intended for use in the gearbox with toroidal grooves of the roller, while the roller is mounted so that there is the possibility of changing its inclination relative to the toroidal grooves rolling, to thereby change the gear ratio of the gearbox, with the cover attached to the support roller so as to maintain constant the position of the casing relative to the roller.

Further specific options done by the means of the present invention will be described only as an example with reference to the accompanying drawings, in which:

figure 1 is a schematic illustration of the basic components of the variator known conventional type;

figure 2 is a perspective representation of a node consisting of a roller, a bearing element and a power cylinder and designed for variable-speed drive in which the present invention is implemented, and half of the roller and its associated supporting structure and the supporting element, not shown, to show the cross-section data components;

figure 3 is carried out along the direction of the main axis of the variator image of the main components of the variator Assembly, which implements the present invention, when one of the disks of the variator is not shown, so that you can see the nodes, consisting of a roller, a bearing element and a power cylinder;

figure 4 is a perspective representation of a node consisting of a roller, a bearing element and a power cylinder and intended for progressive transmission, in accordance with the second embodiment of the present invention;

figure 5 is a perspective representation of a node consisting of a roller, a bearing element and a power cylinder and intended for progressive transmission, in accordance with the third embodiment of the present invention;

6 is carried out with a spatial separation e the cops perspective representation of the node, consisting of a roller, a bearing element and a power cylinder and intended for progressive transmission, in accordance with the fourth embodiment of the present invention;

Fig.7 is a view in plan site 6;

Fig and 9 are performed in axial section planes, respectively, by the arrows a-a and Y-Y 7;

figure 10 is a cross-section of the power cylinder, suitable for embedding in a variable-speed drive in which the present invention is implemented.

The design of the variator, illustrated in figure 2 and 3, is slightly different from the design of the variator of figure 1, and its construction and operation will be briefly explained before considering the device for supplying a fluid medium. Each of the three rollers 100 in the cavity of the variator 102 formed between the disc 104 of the variator and interacting with the disk (not shown in figure 3), is mounted on a respective support element 106, which is affected by two hydraulic power cylinder 108, 110. Bearing elements cannot freely rotatable for adjusting oneself to the desired precession of the axis of the roller. Instead, the orientation of the bearing elements is limited. To understand why this is the case, you should first pay attention to the fact that due to the geometry of the variator center of each roller is always n the circumference 112, which represents the Central circumference of the toroidal cavity formed by the disks, as is well known to specialists in this field of technology. Any rotation of the bearing member can occur only around the axis 114 of the bearing member (see figure 3)connecting the centers of power cylinders 108, 110, since it is around these centers can be rotated pistons (one of which is denoted by reference number 116 and can be seen in figure 2)provided on both ends of the bearing member 106, while the pistons are rotated in their respective cylinders, such as indicated by reference number 118. However, the axis 114 of the bearing member is displaced in the radial direction from the Central circumference of the cavity 112, as seen in figure 3. The axis 114 of the bearing member is located closer to the main axis of the variator (as defined by the main shaft 120)than the Central circumference of the cavity 112. The consequence of this bias is to limit the orientation of the bearing member, which therefore changes only when the disks, such as indicated by reference number 104, is slightly shifted along the major axis due to the pliability and significant mechanical loads, the effects of which they are exposed.

To allow the precession of the rollers 100, required for changing the gear ratio of the gearbox, each n is x is mounted on a corresponding support element 106 by means of a support device, includes rotating the support 122, which enables the rotation of the roller around its own axis for transmission of the driving force, and the ball joint that has inner ring 126 rotating bearing 122. The protrusion 124, which can be seen in figure 3, acts on the spherical part 126 of this hinge and enters a corresponding groove in the socket, which is made in the form of a hub 128 to form the axis 130 of the rotary wheel (castor axis)around which the roller 100 precessive.

Considering next the elements of the node associated with the supply of the fluid to transmit traction to the roller 100, it is necessary to indicate that the source of the fluid flow, such as a pump (not shown), is connected to the hollow rod 152, which passes along the axis of the cylinder 118 and is included in a corresponding axial hole 154 in the piston 116, forming a seal with him. The hole 154 extends along the lead 156 of the bearing member to Solovay hole 158, from which fluid is supplied to the roller 100.

The cover 160 is located near the roller 100. In the illustrated embodiment, the roller 100 for the most part surrounded by a casing 160. The cover 160 is mounted on the hub 128, so that it remains in a fixed position relative to the roller 100, despite the precession of the roller about the axis 130 of the rotary wheel. That is, the cover moves along the roller. The casing is not in contact with the roller 100. In the illustrated embodiment, between the roller 100 and the casing 160 is supported by a gap of approximately 1 mm, Thus, between the facing to each other surfaces of the roller and the casing 160 is formed zone 161 receiving the fluid. The cover 160 has a curved circumferential peripheral wall 162, passing around the greater part of the circumferential periphery of the roller 100. Thus, part of the reception area of the fluid is formed in the place designated by the reference number 163, between the outer circumferential peripheral surface of the roller 165 and a circumferential peripheral wall 162. However, in those areas 164, where the video should be in contact with the disk of the variator, the wall has gaps. Circumferential peripheral wall 162 is connected to the hub 128 by using the upper and lower walls 166, 168, located in a substantially radial planes (relative to the axis of the roller 100 with the opposite end of the roller 100. In the illustrated embodiment, they are cut in areas 170, but without such a cut can be dispensed.

The cover 160 has two holes for inserting the fluid, one of which is denoted by reference number 172 and can be seen in figure 2, while the edge of another hole is visible in the area denoted by reference number 174. These openings are located on opposite sides of the roller. About the holes 172, 174 located on the axis 130 swivel wheels so that their displacement is minimized when the precession of the roller 100.

In addition, both openings 172, 174 are along the axis 130 of the rotary wheel for receiving the fluid from the respective nozzle openings located in alignment with them. In the hole 172 receives fluid from the above-mentioned nozzle 158. Similarly executed nozzle supply to the hole 174, but this hole cannot be seen in the drawings.

It should be noted that there is not hermetically sealed connection between the nozzle 158 and the corresponding hole 172 to enter the fluid. The provision of such connection would lead to the complexity of the design. In the illustrated embodiment, there is a small distance from the nozzle 158 to the housing 160. A jet of fluid from the nozzle 158 passes through the space between the nozzle and the casing and is thus in an area of 161 admission of fluid between the roller 100 and the casing 160. Within this space provides for the circulation of the fluid due to the impact of the rotating roller. Thus, the circumferential peripheral surface 165 of the clip will be securely covered with a fluid medium for the transmission of tractive effort, which will be supported by the availability of the necessary film of fluid between the roller 100 and the disk vari the Torah. There is a constant flow of fluid into the casing 160 and the casing 160, but the casing serves to increase the residence time of the fluid in the vicinity of the casing, and found that it can significantly improve the cooling roller. Within the zone 161 receiving the fluid prevailing conditions characteristic of turbulent flow, and the resulting circulation of the fluid also contributes to the cooling roller. Some resistance force will inevitably act on the roller side of the fluid, but found that this loss of energy is small.

Fluid must be released from the nozzle 158 with sufficient speed to ensure its entry in the casing 160, despite the centrifugal effects which cause displacement of fluid through the inlet hole 172.

It should be understood that the pressure of the fluid to transmit traction inside the holes 154 in the piston 116 creates a bias efforts, acting on the piston and, consequently, the suspension element roller 106. However, this force is balanced by the opposite and substantially equal to the force applied by the relevant device to supply the fluid to the opposite power cylinder 110 at the opposite end of the bearing member, so that there is no significant result is about the efforts acting on the element.

However, the design in some respects can be simplified by supplying a fluid medium to transmit traction to the node consisting of a roller and the casing, through the nozzle, which is not mounted on the load carrying element 106 of the rotor, but instead is attached to the casing of the variator. Figure 4 and 5 illustrates two such alternative devices. Many of the elements are common to 2, 3, 4 and 5, and the same reference numbers used for the data elements in all figures. In particular, each device has a casing 160 surrounding the roller 100.

In the embodiment of figure 4, the nozzle is formed on the end 200 of a bent pipe 202, which is attached to the housing 206 of the variator, as shown in the figure, in the area denoted by reference number 204. The hole 208 in the housing 206 allows flow of fluid from the pump, which is schematically indicated by the reference number 210. The pipe 202 attached to this form and it is located so that it does not cause pollution of the roller 100, the bearing member 106 or casing 160 when moving data elements. An inlet through which fluid enters the environment, coming under pressure from the nozzle 200, the diagram denoted by reference number 212, and it goes along and facing in the direction of the axis, such axis of the caster wheel. The nozzle 200 also passes the Dole to the axis, consequently, there is coaxially relative to the inlet, despite the movement of the roller, although, needless to say, the displacement of the support member 106 back and forth the distance between the nozzle 200 and the inlet 212 is changed accordingly. On the opposite side of the roller relative to the nozzle 200 has an additional pipe 220 with additional nozzle 222.

Figure 5 illustrates a construction in which the direction along which fluid is released under pressure into the casing 160, runs essentially transversely to the axis, such axis of the caster wheel. In this case, the inlet 250 in the casing 160 is made in the form of slits in the top wall 166 of the casing. The slot is located as close as possible to the axis of the rotary wheel, despite the fact that the wall 166 is slightly offset from this axis. The slot runs essentially along the direction of movement of the bearing member 106. Tube 252 in this embodiment, ends of the nozzle 254, directed transversely to the axis, such axis of the caster wheel, and turned in the direction of the inlet 250. Due to the location of the inlet nozzle 250 254 remains exposed with regard to him, despite the movement of the node, consisting of a roller and casing. In a possible napsoluciones.com version of this device con is Moreno, which one of the nozzles formed like a nozzle 200 in figure 4, is intended for input of fluid under pressure through the hole similar to hole 212 on the circumferential peripheral surface of the roller, while the other nozzle located on the opposite side of the roller, made like nozzle 254 figure 5 and is intended for supplying fluid under pressure to the end surface of the roller. It is considered preferable from the viewpoint of the cooling roller.

In all the above variants of implementation, the nozzle is used to release fluid under pressure and feed it through the hole in the wall of the casing, and when this does not occur the need to create a sealed connection between the line for supplying the fluid and casing. It is very convenient from the constructive point of view. However, tests conducted by the inventors showed that at a given speed of the fluid flow, the cooling efficiency is increased when the connection line for supplying the fluid from the casing so that the line for supplying the fluid communicates with the internal space of the casing through its nozzle holes. A node of this type, consisting of a roller and a bearing element, is illustrated in Fig.6-9, and the position and relationship of the major elements of the site are best shown in the implementation of the EBM with a spatial separation of the elements of the image of figure 6. The movie denoted by reference number 300 and rotates on the shaft 302 that is installed rotatably in two sealed roller bearings 304, 306, which are installed in the holes 308, 310 of the respective halves 312, 314 lifting body. The two halves of the casing are connected together by bolts (bolts not shown in the drawings for simplicity)that pass through the near and far intermediate portion 316, 318 lifting body.

In this embodiment, the casing is formed in two halves 320, 322 of the casing, which both have corresponding radial wall 324, 326 essentially round shape and vertical, circular peripheral wall 328, 329. In the assembled casing two peripheral walls rest against each other, resulting inside the casing forms the inner space to accommodate the roller.

The shape of the internal space of the casing is important for its function and is best visible on Fig. The inner surface of the casing has a circumferential peripheral facing radially inward portion 330 near the outer circumferential periphery of the roller, which serves to limit the "repulsion" of fluid from the roller under the action of centrifugal force. The distance between the roller and the housing in this area is in the illustrated embodiment, approximately 1 mm In this place m which may be used is increased clearances, up to 4-5 mm of the Inner surface of the casing also has the appropriate passing essentially in the radial direction, part 334, 336, located close to both side surfaces 338, 340 roller. In the illustrated embodiment, these radial parts are in radial planes. However, these parts can be made with several different forms - for example, they can be made with the shape of a truncated cone, if it is determined that it enables you to improve flow characteristics.

Passing in the radial direction, part 334, 336 casing form a radial mixing chamber along the side surfaces of the roller.

In General, the casing serves to form a chamber for receiving the fluid passing around the outer circumferential periphery of the roller and, at least along part of the side surfaces of the roller. It was thus established that the residence time of the fluid in the vicinity of the roller increases significantly, which provides improved heat transfer from the roller to the fluid and thereby improved the cooling roller. It should be noted that in this respect the housings illustrated in the previous drawings, the same.

You can see that the peripheral wall 328, 329 of the housing has a cut in places 342, 344, where the roller comes in contact with the disc and the variator.

Line for supplying a cooling fluid is formed through the radial holes 346 and connected with him axial hole 348 in the near intermediate portion 316 of the chassis (see Fig.9). Axial hole leads to (1) the first radial Solovay the hole 350 in the intermediate portion 316 of the housing, which communicates with intended for reception of the fluid chamber formed between the housing and the roller, with the first coplowe hole 350 is located with the possibility of release of fluid on the outer circumferential periphery of the roller, and (2) a pair of channels 352, 354 for the passage of fluid (see 6 and 8)formed by grooves on the inner end sides of the respective halves 312, 314 lifting body. Fluid passes through the channels 352, 354 to passing in the axial direction of the channel 356 formed in the inner radial direction of the surface far intermediate portion 316 of the housing, and thus, the second radial Solovay opening 358 formed in the wall of the casing. Second coplowe hole communicates with the chamber for receiving the fluid and produces a fluid medium on the circumferential periphery of the roller. Thus, the device serves for production of cooling fluid into two zones of the outer surface of the roller, one of which is located diametrically protivopul is tenderly another.

The site, consisting of a roller and a bearing element and is shown in Fig.6-9 must be connected with the driving mechanism of the linear displacement, in which means are provided for supplying cooling fluid through the piston drive mechanism. An appropriate drive mechanism (power cylinder) is illustrated in figure 10. The design of the power cylinder was actually owned disclosed in the applicant's earlier U.S. patent 5971885, the content of which is hereby incorporated in this application by reference, and additional details can be found in this document.

Inside the cylinder 400 has a working camera 402, 404, which receives fluid under appropriate pressure to ensure its impact on the enlarged head 408 of the piston 406. On both sides of the enlarged head 408 piston is tubular elements 410, 412, which pass through the respective end walls 414, 416 cylinder with security seals on them. One of the ends of the rod 418 is attached to the piston via a ball joint 420. The other end 422 of the rod leads to the parts 316, 318 bearing element attached to it, but the element is not shown in figure 10 for simplicity. Fluid medium for transmitting the tractive effort from the pump 424 is fed through the hole 426, passing right through the piston throughout its length, is, thus, enters the hole 346, which can be seen in Fig.9.

1. Device for feeding a fluid medium, designed for roller continuously variable transmission in which the driving force is transmitted from one groove rolling to another using at least one rotating roller, the outer circumferential periphery of which is in rolling grooves, the device for supplying a fluid medium includes a casing installed in the vicinity of the roller, and a line for supplying a fluid medium, characterized in that the casing has an inner surface having a circumferential peripheral portion, which is adjacent to the outer circumferential periphery of the roller, and two passes in the radial direction of the part that are close with the corresponding side surfaces of the roller, causing the roller casing forms a chamber for receiving the fluid, and the line for supplying the fluid placed with a possibility of the fluid in the chamber for receiving a fluid medium.

2. The device according to claim 1, characterized in that the circumferential peripheral portion of the inner surface of the casing passes around the greater part of the circumferential periphery of the roller, with a specified part of the inner surface of the housing are made with cut-outs in two diametrically opposite zones, in which the roller is in appropriate to the skill sets of rolling elements.

3. The device according to claim 1 or 2, characterized in that the line for supplying the fluid communicates with the chamber for receiving the fluid through at least one nozzle that is installed with the possibility of release fluid to the surface of the roller.

4. The device according to claim 3, characterized in that the nozzle is installed with the possibility of release of fluid on the outer circumferential periphery of the roller.

5. The device according to claim 4, characterized in that it contains at least two nozzles that are installed with the possibility of release of fluid at spaced from each other in the circumferential direction of the area of the outer circumferential periphery of the roller.

6. The device according to claim 4, characterized in that it comprises two nozzles located on diametrically opposite sides of the roller.

7. Device according to any one of claims 4 to 6, characterized in that at least one of the nozzles is installed with the possibility of release fluid to one of the side surfaces of the roller.

8. The device according to claim 1, characterized in that the casing contains two parts, each of which has an essentially circular radial wall and gathered together around the roller.

9. The device according to claim 8, characterized in that at least one of the two parts of the casing has a vertical peripheral wall, which comes in contact with the other of the two parts.

10. Device is istwo according to claim 1, characterized in that the casing forms a chamber that contains the flash movie.

11. The device according to claim 1, characterized in that it is intended for transmission with toroidal grooves of the roller, and the roller is mounted so that there is the possibility of changing its inclination relative to the toroidal grooves rolling, to thereby change the gear ratio of the gearbox, with the cover attached to the support roller so as to maintain a constant position relative to the roller.

12. The device according to claim 11, characterized in that the roller is configured to precession around the axis of the swivel wheels.

13. The device according to claim 1, characterized in that the line for supplying the fluid ends of the nozzle, positioned and displayed with the possibility of release of fluid through the opening in the wall of the casing, the nozzle is separated from the shell.

14. Roller continuously variable transmission that contains a device for feeding fluid according to any one of claims 1 to 13.



 

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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

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