The site of the variator, the valve

 

(57) Abstract:

The invention relates to a control system variable speed drive designed, for example, for use in the infinitely-variable transmission. The host variable contains a variable of this type in which the clutch is carried out by rolling on the toroidal surface of the rolling elements and uses double-acting pistons to control the rollers and the pressure drop created by the mechanical load for the loading of the variator, and a management tool designed to change the pressure differential created by the mechanical load, in accordance with the changes of the resulting pressure acting on the part of governors of the rollers of the pistons. Control rollers pistons pistons are double acting, guided by the pressure difference in the hydraulic tool control valves associated with the first and second hydraulic circuits. The first valve is used to supply fluid to the greater of the two pressures in the circuits leading to the chamber of higher pressure means for creating a mechanical load. A second valve is used to supply fluid at the lower of the two pressures in the circuits leading to the compensating chamber means DL is between the roller and the disk is constantly below the limit value, when grip is lost. 12 C.p. f-crystals, 9 Il.

The invention relates to a control system variable speed drive designed, for example, for use in a stepless variable transmission (CVT).

It is well known that in the known variable-speed drives of this type in which the clutch is carried out by rolling on the toroidal surface of the roller, each roller is mounted in raichoor, and this raichoor attached to the cylinder exposed to an adjustable hydraulic forces, which creates oppositely directed tangential forces (due to shear the oil film on the contact surfaces between the roller and the other drives.

Dual mode is steplessly adjustable transmission, which uses this type of variator, in detail, for example, in the descriptions of applications for patents great Britain GB-A-2023753 and GB-A-1078791. In this case the variable contains two input disc or rotor that both rotate together with the input shaft driven by the primary engine. One of these two disks rigidly mounted on the shaft, while the other is mounted on the shaft with the spline so that the disk has some freedom to agronomy sets of rollers, providing rolling contact between the partially toroidal surfaces of the rolling elements (raceways) formed on adjacent surfaces of the input disk and output disk.

In addition to its function of an input element mounted with a possibility of displacement in the axial direction end plate also serves as a piston operating for the application of mechanical load to the CVT. This is required to create the necessary contact forces between rollers and discs for the transmission of drive force. If the variator is subjected to excessive mechanical load, its efficiency will be low, and the element life is short, whereas, if this effort is inadequate on the surface of contact between the roller and the disk may be unacceptable slippage, which will lead to loss of adhesion, which is definitely undesirable.

In the application to the United Kingdom patent GB-A-1600974 disclosed variable of this type in which the clutch is carried out by rolling on the toroidal surface of the roller and in which an attempt was made to compensate for excessive mechanical load, when the elements of the variator work on speed. This is the spacecraft carries a cylindrical housing, divided internally into two chambers, and in each of these chambers placed one of the two annular pistons arranged in series on the shaft of the variator. Each piston divides the respective chamber into two cavities, one on each side of the piston, and when the variator in a pair of cavities on the rotor side of the pistons is supplied fluid under high pressure, while in a pair of cavities on the other side of the piston is served low pressure to produce a resulting mechanical load acting on the variator, as described above. Thus, by increasing the pressure on both sides of the pistons, designed to create a mechanical load, a large radial gradient of the pressure increasing due to the fluid in the cavity of the high pressure, when the elements of the variator rotate speed will be largely compensated by the almost identical pressure gradients formed in the fluid found in the cavities of low pressure. This provides the possibility of forming essentially as effective mechanical loads that would be applied in the absence of the centrifugal force, i.e. in the case, if the end plate and the housing does not rotate the panorama of power."

The node with end load, described in the patent application in the UK of GB-A-1600974, fluid under low pressure, for cavities that are used to create mechanical load comes from the schema lubrication of rotors/rollers, while fluid under high pressure is supplied from the same source that is used for piston single acting, control rollers. Therefore, except in those cases when the supply pressure is extremely low, the differential value of the mechanical load may be less than required to maintain the clutch.

In the variator of the type indicated above, the ratio between the tangential force (grip force) TF and the normal (perpendicular) force NF on the surface of contact between the roller and the disk is known as the coefficient of coupling. When exceeding a certain value, called the limiting friction, the roller will slide and grip will be lost. This means that in the system in the form of the United Kingdom patent GB-A-1600974 full pressure compensation of the centrifugal force can be used only in the case when the source of low pressure is very low, Yes the containing variable of this type, in which the coupling is carried out by rolling on the toroidal surface of the roller, which has an input and output disks, rollers, driven by a hydraulic piston located between the said disks and functioning to transfer clutch between them, and means for creating a mechanical load, depending on the deviation of the disc toward the other disc, in which the hydraulic tool control is designed to change the face of the load in accordance with the changes (resultant) force acting from the side of the control roller of the piston, in order to maintain the friction on the contact surface between the roller and the disk is constantly below the limit value, when grip is lost.

Preferably the tool contains a control means for changing the mechanical load in accordance with a predetermined function of the force acting from the side of the control rollers of the pistons.

In a particularly rational design specified management tool provides a means for changing the mechanical load is proportional to the pressure created by the piston, the control rollers.

Preferably, crystals, adjustable due to the difference between the pressures in the management tool, and a tool for creating end-load provides a means for the application of the mechanical load, proportional to the force acting from the side of the control roller of the piston.

Preferably double-acting pistons designed to control rollers, contain the head of the piston sliding within a single coaxial cylindrical caps, in each of which the working fluid is supplied from a separate source of working fluid.

Alternatively, double-acting pistons, designed to control the rollers contain pistons with one head located inside the cylindrical chamber, and the opposite surface of each of the specified piston are open to influence from the separate sources of working fluid, the working fluid pressure in each of which can be adjusted independently of the other.

Rationally, if the tool for creating end load includes a high pressure chamber and the chamber pressure compensating, the last of which is supplied with working fluid from a pressure equal to the lower of the two pressures acting on the charge of the burden is supplied with working fluid pressure, equal to the higher of the two pressures acting on the control rollers pistons.

Preferably the tool includes parallel first and second hydraulic circuits, each of which is served by its own working fluid from one or the other of these sources using its own pump and each of which is arranged with its discharge valve (pressure valve) to create the desired pressure within the scheme.

Preferably, the regulator includes a valve which releases the fluid with higher pressure and which is installed between the first and second hydraulic circuits and attached to the fluid with the higher of the two pressures in the circuits in the high-pressure chamber, means for creating a mechanical load.

Preferably, the regulator includes a valve which releases the fluid from the lower pressure and which is installed between the first and second hydraulic circuits and attached to the fluid with the lower of these two pressures in the compensation chamber means for creating a mechanical load.

In one embodiment, vatore the specified lubrication chart attached to the fluid supply with adjustable pressure in the compensation chamber means for creating a mechanical load.

The valve, which releases the fluid from the lower pressure and which is suitable for use in CVT as described above, may include first and second inlets for receiving fluid from the first and second pressures, the outlet for the liquid having the lower of the two pressures, at which the liquid is supplied to the valve, and the obturator, responsive to the specified first and second pressure in order to facilitate the passage of only the fluid of lower pressure to the specified output hole.

In a specific structural embodiment of the valve, which releases the fluid of lower pressure, the obturator includes a channel, the first end of which communicates via a fluid from a source of high-pressure fluid, the second end of which communicates via a fluid from a source of fluid to the low pressure and intermediate point of which is communicated with the specified outlet, and each end of a specified channel has a contact area of the seal that is designed to interact with one or the other of the pair of sealing elements, the sealing elements are separated from each other by a distance greater than the distance between the specified contact is bots liquid, being at a higher pressure causes a displacement of the sealing elements with the aim of closing (seals) end communicating with the high pressure fluid, and open (unzip) the end that communicates with the fluid of low pressure to thereby force the fluid of low pressure passing to the outlet.

In accordance with the present invention is also designed valve containing the first and second chambers and a piston with two heads, the first head of which is located within the first chamber and the second cylinder, which is located inside the second chamber, and the specified first head serves to divide the first chamber into two parts, the first of which has an inlet for receiving working fluid from the first source, and the second part has a second inlet for receiving working fluid from a second source, moreover, the specified second cylinder and configured to connect it in the first cylinder by means of a connecting element and with the possibility of displacement along with it. The second chamber has a first inlet for receiving fluid from a source, an outlet for the working fluid in the other strukcija done so, that the pressure of the working fluid in the second chamber is proportional to the difference between pressure in the first chamber.

Further embodiments of the present invention will be described in more detail exclusively by means of example with reference to the accompanying drawings, in which:

Fig.1 is a cross-section of the variator, which includes a simple mechanism for creating a differential mechanical load,

Fig. 2 is a schematic depiction of a control system for a variable-speed drive, in which the coupling is carried out by rolling on the toroidal surface of the rolling element with the specified image illustrates the various aspects of the present invention;

Fig.3 and 4 show first and second nodes to generate the mechanical load of the variator;

Fig. 5 is a broken-out section side of the variator and shows the relationship between the normal force (NF) and the forces of adhesion (TF), discussed in text;

Fig. 6 is a schematic depiction of a device for regulating the pressure, suitable for a pressure end load, which varies in accordance with changes of the resulting pressure acting on the side of upreit pre-loaded spring on the end load and how this impact can be lifted hydraulically; and

Fig.9 is a magnified image of the valve according to Fig.2, which produces a liquid with a lower pressure.

As is shown in Fig.1, the CVT 2 comprises a pair of input rotary disks 78, 79, the output of the rotary disc 4 and the set of rollers 12 arranged between, and designed to transmit torque in a way that is well known to specialists in this field and therefore not described in detail here. At the end of the variator 2 is provided node 5 to create a mechanical load, which in its most simple form contains simple hydraulic chamber 6, which is supplied working fluid under pressure. The pressure in the chamber 6, is used for loading the disc 78 in the axial direction in such a way that it provides a reliable clamping of the rollers between the disks 78, 79 and ensures effective transmission of torque in the variator. As stated previously, the magnitude of this end of the load must not fall below the value at which the clutch will be lost, or to be so high that it leads to reduced efficiency and service life of the transmission. In this application the following describes the way the reg is ateneu, at this rationally that the axis 10 of the main roller 12 of the variator installed in the cavity 14 of the hollow piston rod 16 of the piston 18 double action. This piston is made with opposite heads 20, 21 of the piston that slide under the action of hydraulic load inside coaxial cylindrical caps 23, 24 and which can freely rotate around the axis of shaft 16. It is also possible the same piston single acting, in which both opposite surfaces only head exposed to the liquid.

On the end and side walls of the covers 23, 24 respectively performed inlets 26, 27 and outlet openings 29, 30 for the working fluid, and using many of the same pickup routes 25, 25A also is used to supply the working fluid in the auxiliary end caps of the cylinder. Pressure in the respective auxiliary cylinders other videos (1-5) refer to the pressure in the caps 23, 24 that the adhesion forces are equal.

In the art (as described, for example, in the patent application in the UK of GB-A-979062) is well known for setting the first roller on the inside of the covers 23, 24 and placing the axes of the caps so that they essentially pass the rolling rotor, but they are at a slight angle, known as the camber angle of the front wheels or caster angle of the swivel bolt (DM). With this design is the use of hydraulic end stop is facilitated because each axial position of the retainer corresponds to the angle of equilibrium ratios.

Hydraulic control circuit for a transmission contains two sources of working fluid supplied from the oil pumps 32, 33, capable of feeding the working fluid from the reservoir to the sump 35, for example, at a pressure of from 30 to 50 bar in the left and right of the highway 37, 38 located above the flow direction, and these highways provide fluid flow respectively to the input holes 26 and 27 of the cylinder. However, these pumps will not be served the working fluid under pressure when the valves (58, 59) management or corresponding hydraulic outlet openings (29, 30) will not be sufficiently throttled. Cross-connection 43 between lines 37 and 38 is communicated through the design of the check valves 45, 46, which ensures the production of a fluid with a higher pressure, and through the line 48 with the main chamber of the high level is 4. This ensures that in the chamber 50 will always be liquid under pressure, equal to the higher of the two pressures in lines 37 and 38.

Outlet openings 29 and 30 from the covers 23 and 24 are using below along the flow of the left and right of highways 55 and 56 to the inputs of two electro-hydraulic valves 58 and 59 pressure ratio (proportional valves), which will be described below.

Cross-connection 61 between the left and right lines 55 and 56 formed by the construction of the valves 63 and 64, which ensures the production of a fluid of lower pressure, and the connecting line 66 creates a connection with the compensation chamber of the transfer mechanism designed to create a mechanical load, i.e. with the chamber 89 in Fig. 3 or 99 in Fig.4. The valves 63, 64, located between them, ensure that the compensating pressure in design, creating a mechanical load is always lower pressure in the cylinders 23, 24 of the control rollers. Alternatively, the elements 61-66 can be moved into the area next to the items 43-46.

For valves 58 and 59 control the flow direction left and p which may be used for fluid supply for General lubrication of the transmission. The proper pressure is maintained in the line with a backslash (bypass) valve 72. POS. 74 indicates alternative connections (back-pressure) for a node, which is used to compensate for end load (instead of the connection 66).

As is shown in Fig. 3, the appropriate mechanism for creating the mechanical load of the variator includes a hollow Cabinet element 76 attached to the input rotor 78 of the variator, and the main and auxiliary pistons 80, 81, placed inside the body element. POS. 83 indicates the end stop for the piston 80. The rotor 78, the piston 80 and separating the node 91 is installed using a flat-blade connection, either directly or not directly on the shaft 85 of the variator, and the o-ring seals shown in the figure, are hydraulically isolated from each other the main camera 50 to create a mechanical load between the rotor 78 and piston 80, 81), the camera 87 pre-loading between the piston 80 and piston 81) and the so-called compensation chamber 89 between the piston 80 and the front wall of the body element 76). Dividing the node 91 limits the distance that the piston 81 and the rotor 78 can be close to each other.

And in conclusion, the mechanism is Sedna stepped surface of the main piston 80, and in the mechanism provided by the channels 95, 98, 97 connecting the camera 89, 50, and 87, respectively, with hydraulic lines 86 and 48 and the atmosphere. In an alternative embodiment, the channel 95 may be located so that it will connect the camera 89 source of backpressure in the system.

In the operation of the mechanism for creating the mechanical load it is filled with oil and rotates with the input rotational speed of the variator. However, the initial variable must counteract the final inertial loads during large accelerations experienced by the transmission during engine start-up. Because hydraulic pumps are also provided from the engine, and hydraulic end load is not available, must be provided by an alternative device to create a mechanical load, and it is formed by the Belleville spring installed between the two pistons 80, 81. Thus, it should be understood that the design allows the application of mechanical load when the engine is running, but that this pre-load can be lifted hydraulically to any extent depending on the physical dimensions of the site and applied pressure. The work of the Belleville springs can better serously, represents the output load IL generated by the Belleville spring, pressure (CF) in the high-pressure chamber and pressure (TP) in the compensation chamber. The original load IL spring will be overcome only when the differential pressure (CP-TP) will become more IL, and then the pressure end load increases in proportion to a pressure differential, and the nature of this growth largely depends on the dimensional ratios of the piston between the high pressure chamber and the compensating chamber. In Fig.8 shows that the effect of load IL spring can be lifted hydraulically by raising the pressure in the high pressure chamber and the compensation chamber adjustable manner in order to eliminate the influence of the load of the spring. It accordingly can be illustrated by reference to the lower part of Fig.8, which shows that the influence of the spring may be eliminated so that the line end load will pass through zero when removing the load. However, other variants are obvious to a person skilled in this field.

Applying in compensation the camera supports pressure (TP) means that it loads the variator.

During operation of the electrohydraulic proportional valves 52, 59 is a well-known manner to create the desired back pressure in lines 55, 56 and to the end caps 23, 24, to cause movement of the main rollers 12 in the desired position. In fact, it is the difference between the higher pressure in the main line (which controls the pressure and lower pressure in the main line (supporting pressure) determines the torque in the transmission. Thus, it is argued that the rollers shall be under the control of the differential pressure". As described above, in the design to create a mechanical load also used the difference between the higher and lower of the two pressures in the hydraulic circuit, and, therefore, this construction is also under control of the difference".

The basic hydraulics of the new system ensures that the tangential adhesive force (TF) is equal to half of the resulting force created by the governing pressure (CF) acting on the control rollers piston double-acting, less supportive pressure (TP) in the transverse plane of the variator. This is illustrated in Fig.5, where NCF and TF respectively hereafter the abuser pressure and control pressure, and SA denotes the angle of longitudinal inclination of the swivel pin.

Rationally, that by providing a control pressure difference as for the rollers, and for structures that are designed to create a mechanical load, it is possible to ensure that the total end load NF (the CF-TR) is changed in accordance with the result of pressure (CP-TP), is applied to the control rollers pistons. Therefore, the value of the total end load NF is directly related to the magnitude of the adhesion forces TF, and therefore the adhesion factor (the ratio TF/NF) will remain constant during the entire operation of the variator. Therefore, maintaining the grip below a certain pre-determined value, which usually occurs slippage, is achieved automatically.

In Fig.4 shows an alternative design for the creation of end load, which shows that the constant and close to the optimum coefficient of coupling is achieved through the use of the cylinder to create a mechanical load with two cameras 50, 99 equal size, with one camera (50) is under the managing pressure plus the pressure of centrifugal force in it) in contrast, the button as accurately as possible to agree on changes related to the power roller clutch on the surface of the contact roller/disk with changes in the perpendicular forces due to mechanical load. This figure uses the same number of positions as in Fig.3, to indicate structurally or functionally identical elements. In modifications (as shown in Fig.3) node to create a mechanical load, the compensation chamber and the high pressure chamber, if desired, may vary with the purpose of providing partial compensation of pressure from centrifugal force, so that the clutch coefficients decreased with the velocity (speed).

It should be noted that the control system of the CVT according to the present invention in comparison with the system in the form of the United Kingdom patent GB-A-1600974 has a very significant advantage, as in the construction according to the preceding technical level there is no effective support pressure acting on the control rollers pistons, and because of this, any low pressure applied to them to compensate for end load, will lead to the increase of the working friction, which causes the risk is amplified embodiment of the present invention the compensating pressure is provided rather from a point 70 lubrication circuit of Fig.1 (backpressure), instead of highway 66 (supporting pressure). However, it should be noted that the back pressure, but does not require, valve design, which produces a liquid with a lower pressure, still does not fully compensate for supporting the pressure due to pressure drops (loss of flow) in the system.

From the foregoing it is obvious that the main function of the present invention is to change the face of the load in accordance with changes resulting force acting from the side of the control rollers of the pistons, in order to maintain the coefficient of adhesion (ARTICLE) on the surface of the contact roller-drive continuously below the limit value at which the clutch will be lost. Although in the above described device is one possible way to achieve this effect, it is obvious that you can use any of a number of different ways. For example, you can use the valve device 150 shown in Fig.6, which contains the first and second chambers, indicated respectively 152 and 154, and a piston with two heads, indicated generally poses. 156. The first piston a contained within the first chamber 152 and serves to divide it into two parts 152a, 152b, to the high output pressure, and valve design, which produces fluid under low pressure. The second piston 156b is contained within the second chamber and operable connected via a connecting element 158 with the first piston a to shift with him. On the side remote from the coupling element 158, the second chamber has an inlet opening 159 for receiving the working fluid from the independently driven pump 160 controlled by a controller 162. The first outlet 164 of the second chamber provides a flow of the working fluid in order to create a mechanical load and can supply the working fluid in a simple single-chamber design to create a mechanical load, such as shown in Fig.1. Rationally that this outlet may be replaced by a single bleed hole (not shown) in the inlet opening 159. The second outlet 166 is located under the piston 156b and serves to return the hydraulic fluid reservoir 35 (Fig.2). The piston 156b and the exhaust port 166 are located relative to each other so that the piston is used to control the flow through the outlet 166 and, therefore, to regulate the pressure P1 and the magnitude of the mechanical force. If the tertia and restore proper pressure. Conversely, if necessary, the piston 156b may move to close the outlet 166 (partly or fully) and to restore the pressure. Additional outlet 167 to drain from the area behind the piston 156b and allow the exit of air trapped behind the piston 156b. If desired, the outlet 167 may be positioned in such a way that it also provides pressure relief in case of excessive rise of pressure. Alternatively, you can use the controller 162 to change the performance of the pump 160 and, therefore, the pressure P1 in such a way that it will never exceed a predetermined value. This situation may, for example, occur at high speeds, when the centrifugal pressure on the hydraulics in the mechanism designed to create a mechanical load significantly and negatively affects the total end load.

In the process, the hydraulic pump 160 is actuated and generates a pressure P1 in the second chamber 154, which acts on the second piston 156b, and supplies the hydraulic pressure to create the mechanical load. Pressure P2, P3, action is asnote between P2 and P3 is used to counteract P1, so the piston 156b shifts in the direction of one or the other of the arrows W, depending on the magnitude of the difference between P1 and P2-P3 in order to increase or decrease the resistance in the outlet 166. Rationally, this design allows you to vary the amount of pressure from the mechanical load and, consequently, the force of the mechanical load in accordance with the resulting pressure acting on the control rollers pistons (P2-P3), since P2 and P3 are the control pressure CP and the supporting pressure of the TR control rollers of the pistons. Therefore, with this simple design double chamber device to create a mechanical load is not absolutely necessary, and the design can be somewhat simplified. The exact ratio between the pressures P1, P2 and P3 depends on the relative sizes of the pistons a, 156b, which can be changed to obtain any desired ratio. For example, the pistons of the same size will cause a change in pressure P1 is exactly proportional to the difference between P2 and P3, while the other sizes will lead to modification of the nature of this change. In the case when P1 barely reaches the pressure at which the mechanical load will be the same cterm he closes the outlet 166, and the pressure is restored.

For the sake of completeness it should be added that two factors lead to changes in the above-described relationship between mechanical load and the normal force on the contact surface of the roller/drive. First, for a given mechanical load (normal) power will increase inversely proportional to the cosine of the angle gear ratio of the rollers (0owhen 1:1). Secondly, there will be a difference between the normal forces on the terminal and the Central disk, which occurs due to the axial component of the resultant control force acting on the roller, it will be equal to the resultant force, multiplied by the sine of the angle of longitudinal inclination of the swivel pin. Since both of these effects are comparatively small, the above interpretation, they are ignored.

The valve, which releases the liquid with the lowest pressure, in Fig.2 and Fig. 9 may be used in some cases other than the above application, and, therefore, this valve is described now in more detail. In particular, the valve 200 includes first and second inlets 202, 204, designed to receive fluid from the first and second pressure P6, P7, outlet port 206 for receiving W is different pressures in order to facilitate the passage of only the liquid from the low pressure to the specified output hole 206. The valve includes two cameras 210, 212, each associated with a respective inlet and a channel 214 which is connected by fluid at the first end a camera 210 and at its other relations of the free second end 214b with camera 212. Mid-point of the channel 214 is connected with the outlet 206 of the valve for passage of fluid as described below. Each end of the channel has a contact pad 216, 218 of the seal. Additional signs of valve is that it contains a pair of sealing elements shown, for example, in the form of balls 220, 222 (63, 64 in Fig.2), each of which can move freely within the borders of their respective chambers 210, 212 and/or to close or open the respective ends of the channel 214. Two sealing element 220, 222 are separated from each other by a distance greater than the distance between pads seal, with the spacer element 224 passing between them, so that in the process of working fluid at a higher pressure causes a displacement of the sealing elements with the aim of closing the end (channel) associated with the fluid under higher pressure, and maintain a set distance or gap G designs passage in the channel 214 remains unclosed, and the fluid of lower pressure is free to pass to the outlet 26, thereby providing a flow of fluid from the lower of the two pressures for later use.

1. Host variable that contains a variable of this type in which the clutch is carried out by rolling on the toroidal surface of the roller, which has an input and output discs (78, 79), the rollers (12) driven by a hydraulic piston located between the said disks and functioning to transfer clutch between them, and means (89, 50) to create a mechanical load, which serves to bias the discs toward each other, means (58, 59) hydraulic control, designed to change the face of the load in accordance with the changes of force, the acting on the part of governors of the rollers of the pistons (20, 21), to maintain friction on the contact surface of the roller - disk is permanently below the limit value at which the clutch will be lost, characterized in that the control rollers pistons (20, 21) are double-acting pistons, driven by the pressure difference in the means (58, 59) of the hydraulic control and the first valve (45, 46) associated with properties larger of the two pressures in the schema, leading to the chamber (50) higher pressure means for creating a mechanical load, and a second valve (63, 64) connected with the first and second hydraulic circuits (37, 38) for the fluid at the lower of the two pressures in the circuits leading to the compensation chamber (89) means for creating a mechanical load.

2. The site of the variator under item 1, characterized in that the first valve (45, 46) is a valve, releasing the fluid from the higher pressure and the second valve (63, 64) is a valve, releasing the fluid of lower pressure.

3. The node variable in one of the p. 1 or 2, characterized in that the tool contains a control means (58, 59) for changing the mechanical load in accordance with a predefined function of the force acting from the side of the control rollers of the pistons (20, 21).

4. The node variable in one of the paragraphs.1-3, characterized in that the tool contains a control means (58, 59) for changing the mechanical load is proportional to the force acting from the side of the control rollers of the pistons (20, 21).

5. The node variable in one of the paragraphs.1-4, characterized in that the means for creating a mechanical load (50, 89, 50, 99) provides a means for application of force t>6. The site of the variator on p. 5, characterized in that the control rollers double-acting pistons contain opposite heads of the pistons sliding within a coaxial cylindrical caps (23, 24), in each of which the working fluid is supplied from a separate source of working fluid.

7. The site of the variator on p. 5, characterized in that the control rollers pistons (20, 21) double action contain pistons with one head located inside the cylindrical chamber, and the opposite surface of each of the specified piston are open to influence from the separate sources of working fluid, the working fluid pressure in each of which can be adjusted independently of the other.

8. The node variable in one of the paragraphs.5-7, characterized in that the means for creating a mechanical load (50, 89, 50, 99) includes a chamber (50) and high pressure chamber (89, 99) compensating pressure, the latter of which is supplied with working fluid from a pressure equal to the lower of the two pressures acting on the control rollers pistons (20, 21).

9. The site of the variator under item 8, characterized in that the camera (50) high pressure means for creating a mechanical load is supplied to the working liquid is SS="ptx2">

10. The site of the variator according to any one of paragraphs.5-9, characterized in that the means (58, 59) management includes parallel first and second hydraulic circuits(37, 55, 38, 56), each of which is served by its own working fluid from one or the other of these sources using its own injection pump (32, 33) and each of which is arranged with its discharge control valves (58, 59) to create the desired pressure within the scheme.

11. The site of the variator under item 10, characterized in that it comprises a circuit (74) lubrication with means (72) for regulating the pressure in the circuit, and in which the specified lubrication chart attached to the fluid supply with adjustable pressure in the compensation chamber (89, 99) means for creating a mechanical load.

12. The site of the variator according to any one of paragraphs.1-11, characterized in that it includes a valve, which produces a liquid with a lower pressure containing first and second input apertures (202, 204) for receiving fluid from the first and second pressure outlet port (206) for the liquid having the lower of the two pressures, at which the liquid is supplied to the valve, and seal (220, 222, 224), responsive to the first and second pressure relief p. p. 12, characterized in that the seal (220, 222, 224) includes a channel (214), the first end of which communicates via a fluid from a source of high-pressure fluid, the second end of which communicates via a liquid with a liquid source of low pressure, and the intermediate point, which communicates with the outlet (206), and each end of the channel has a contact area of the seal that is designed to interact with one or the other of the pair of sealing elements, thus sealing elements are separated from each other by a distance greater than the distance between pads (a, b) seal, using the spacer element (224) passing between them so that in the process of working fluid at a higher pressure causes a displacement of the sealing elements (220, 222) with the aim of closing the end that communicates with the high pressure fluid, and an open end communicating with the fluid of low pressure to thereby force the fluid of low pressure passing to the outlet (206).

 

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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

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

FIELD: transport.

SUBSTANCE: proposed system comprises first source of pressurised hydraulic fluid source to produce first fluid flow and second source of pressurised hydraulic fluid source to produce second fluid flow, and torque converter control subsystem to control said converter and its coupling. Said subsystem comprises torque converter control valve and solenoid. Said solenoid is multiplexed to aforesaid control vale and coupling. Said control valve controls hydraulic fluid flow to torque converter and other subsystems in hydraulic control system.

EFFECT: higher efficiency and response in control, smooth control.

10 cl, 6 dwg

FIELD: transport.

SUBSTANCE: proposed system comprises compressed hydro fluid source communicated with transmission range selection subsystem (ETRS). ETRS subsystem comprises ETRS valve, packing mechanism, first and second mode valves, retention valve assembly and multiple solenoids. ETRS subsystem allows multiple operating conditions in multiple potential faulty states.

EFFECT: higher efficiency and response in control.

10 cl, 4 dwg

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