Automotive stepless transmission with belt drive and method of control thereof

FIELD: transport.

SUBSTANCE: proposed stepless transmission features reserve factor with respect to belt slippage caused by belt compression force applied to belt transmission 48 reduced to magnitude lower than or equal to 1.5 due to decreased pressure reception area of hydraulic cylinder 46c on its outlet side.

EFFECT: simplified design allowing belt compression force adjustment.

4 cl, 6 dwg, 1 tbl

 

The technical field

The invention relates to the construction of automobile continuously variable transmission with belt drive and method of controlling such a transmission. More specifically, the invention relates to the construction of automobile continuously variable transmission with belt drive and control, which eliminates the need for the camera to compensate for the centrifugal hydraulic pressure cylinder secondary side.

The level of technology

One known type of automobile transmission is a continuously variable transmission with a belt drive, which changes the speed smoothly and continuously without any gear. This continuously variable transmission driven by a belt formed of a continuously variable transmitting portion, which comprises mainly two rotating element mounted in parallel relation to each other, a primary pulley that is located on one of the rotating elements so that it is not able to rotate relative to this rotating element, a secondary pulley that is located on another rotating element in such a manner that it is not able to rotate relative to this rotating element, and a strap that wrapped around the two pulleys. The primary pulley and the secondary pulley, each includes a fixed part of the pulley and moving the art pulley, between which is formed a V-shaped groove forming the groove for a belt. Power is transmitted between the two pulleys with a belt. Here the cylinder primary side, which exerts an axial load to the movement of the movable side pulley of the primary pulley in the axial direction acts on the primary pulley, while the cylinder secondary side, which exerts an axial load to the movement of the movable side pulley of the secondary pulley in the axial direction acts on the secondary pulley. By individual control hydraulic pressure supplied to the cylinder primary side and a secondary cylinder side, the gear ratio continuously variable transmission with belt drive is changed by regulating the width of the groove of the primary pulley and change the diameter of the winding of the belt around the pulley while the belt tension is adjusted by changing the width of the groove of the secondary pulley.

Continuously variable transmission with belt drive of this type, when the rotation is specified by a source of power such as the engine, is transmitted continuously variable transmitting portion without reducing speed, while the vehicle moves forward, the rotation speed of the secondary pulley is increased, and when this happens, the secondary cylinder is relatively large centrifugal water is practical pressure. This centrifugal hydraulic pressure creates an axial load on the movable pulley of the secondary pulley in the direction that causes the compression of the belt so that the compression force of the belt becomes excessive. Because of this, one related stepless transmission with a belt drive is equipped with a camera to compensate for the centrifugal hydraulic pressure on the side of the secondary pulley to neutralize the centrifugal hydraulic pressure.

Figure 6 shows a view in cross section of the secondary pulley 200, representing an element of the above related variable transmission with belt drive. The secondary pulley 200 includes a fixed portion 204 of the pulley forming a single unit with the output shaft 202, the movable portion 206 of the pulley mounted on the output shaft 202 so that it can move axially but cannot rotate relative to the output shaft 202 and the cylinder 208 of the secondary side that is located adjacent to the movable part of the pulley 206. The cylinder 208 of the secondary side has a camera 212 hydraulic pressure generated by the mobile part of the pulley 206 and the partition 210, and the camera 214 compensation of the centrifugal hydraulic pressure formed between the partition wall 210 and a peripheral wall 213, which is attached to the movable part of the pulley 206. Thus, the camera 214 compens is the centrifugal hydraulic pressure is formed on the reverse side walls 210 relative to the camera 212 hydraulic pressure. Thanks to the use of the camera 214 compensation of the centrifugal hydraulic pressure generated centrifugal hydraulic pressure that is equal to the hydraulic pressure in the chamber 212 of the hydraulic pressure in the chamber 214 compensation centrifugal pressure counteracting the axial load on the movable portion 206 of the pulley in the direction of the fixed portion 204 of the pulley, which is called the centrifugal hydraulic pressure generated during the rotation of the camera 212 hydraulic pressure. Centrifugal hydraulic pressure generated in the chamber 214 compensation of the centrifugal hydraulic pressure, suppresses the action of the centrifugal hydraulic pressure in the chamber 212 of the hydraulic pressure, by application of an axial load to the movable part 206 of the pulley in the opposite direction relative to the axial load, the hydraulic pressure in the chamber 212 of the hydraulic pressure.

However, the use of this camera compensation of the centrifugal hydraulic pressure makes a continuously variable transmitting portion of the heavier, less efficient and more costly. Thus, publication of the patent application of Japan No. JP 2005-90719 describes a technique that avoids the use of the camera to compensate for the centrifugal hydraulic pressure by approx is in cylinder secondary side with two hydraulic pressure chambers, that is, the hydraulic pressure chamber of the outer diameter, and the hydraulic pressure chamber side of the inner diameter, and a corresponding switch of the areas receiving the pressure of the cylinder.

However, when the technology described in the publication JP 2005-90719, you must have design for switching between the mode in which hydraulic pressure is supplied to the hydraulic pressure chamber side of the inner diameter and the hydraulic pressure is discharged into the hydraulic pressure chamber of the outer diameter, and a mode in which hydraulic pressure is supplied to the hydraulic pressure chamber side of the inner diameter, and also the hydraulic pressure supplied to the hydraulic pressure chamber of the outer diameter. However, the required design is quite complex. In addition, the compression force of the belt does not change smoothly when switching the receiving area of the pressure cylinder, which refers to the switching of the modes.

Brief description of the invention

The present invention thus relates to an automotive continuously variable transmission with a belt drive, which is capable of appropriately adjusting the compression force of the belt, while having a simplified structure by eliminating the camera compensate for the centrifugal hydraulic is anyone pressure on the side of the secondary pulley.

The first object of the invention relates to an automotive continuously variable transmission with a belt drive, which includes: (a) continuously variable transmitting portion, which rotation is transmitted from the source of power without sacrificing speed, while the vehicle moves forward, and applied to one chamber of the hydraulic pressure to the secondary pulley, and b) the device controlling the hydraulic pressure, which switches the continuously variable transmitting portion by controlling one of: (i) the supply and release of fluid and (ii) the pressure of the working fluid relative to the cylinder primary side, is applied to the primary pulley and the regulatory force of the compression belt wrapped around the primary pulley and the secondary pulley by regulating the pressure supplied to the cylinder secondary side formed by a single hydraulic pressure chamber, C) a control unit of the hydraulic pressure with a design for independent adjustment of pressure in the pipeline and the pressure supplied to the cylinder secondary side.

In addition, according to the first object receiving the pressure cylinder area of the secondary side can be set so that the factor of safety relative slippage of the belt, the pressing force of the belt is obtained when the pressure supplied to the cylinder the secondary the hand, installed on the lowest level of the specified adjustable pressure when the vehicle is moving at maximum speed on a flat road, is a value less than or equal to 1.5.

Accordingly, despite the fact that the compression force of the belt at maximum speed may be excessive due to the increase of the axial load produced by the centrifugal hydraulic pressure, pushing the movable portion of the pulley in the direction that increases the compression force of the belt, due to the lack of camera to compensate for the centrifugal hydraulic pressure that provides suppression of axial force, the transformation of this power compression belt in excessive can be limited by reducing the receiving area of the pressure cylinder secondary side. In this case, it is also necessary to reduce the pressure supplied to the cylinder of the secondary side. Regarding this point, the control pressure in the pipeline and the pressure supplied to the cylinder secondary side, independently makes it possible exception of the problems lies in the fact that the pressure in the pipeline together with the pressure supplied to the cylinder of the secondary side becomes too low or is unable to switch to increase speed due to the fact that the hydraulic pressure required for switching is not fed into the cylinder p is Rechnoy side or a similar tool. In addition, when receiving area of the pressure cylinder secondary side decreases, the pressure in the pipeline must be increased to increase the hydraulic pressure supplied to the cylinder of the secondary side at low speeds. However, if the pipeline pressure can be adjusted independently of the pressure supplied to the cylinder of the secondary side, the increase in pressure in the pipeline may be limited, to avoid sharp impact on the gear side (γ>1), which adversely affects fuel consumption. In addition, the receiving area of the pressure cylinder secondary side decreases, while the factor relative slippage of the belt, the force of the compression belt is taken when the pressure supplied to the cylinder secondary side, set at the lowest pressure during the movement of the vehicle with a maximum speed on a level road, when the vehicle moves with a maximum speed on a level road, it becomes a value less than or equal to 1.5, which makes it possible to maintain a long service life of the belt without deterioration of its qualities. The result is possible to obtain automotive continuously variable transmission with a belt drive having a simple design and allows you to eliminate for all practical purposes the camera compensation cent is obingo hydraulic pressure.

The second object of the invention relates to a method for control of automotive continuously variable transmission with a belt drive, which includes a continuously variable transmitting portion, which receives rotation from a source of power without reduction in speed, while the vehicle moves forward, and one chamber of the hydraulic pressure applied to the secondary pulley. This method of control is characterized by the fact that it includes a) the switching part of the continuously variable transmission part by controlling one of: (i) the supply and release of fluid and (ii) the pressure of the working fluid relative to the cylinder primary side, is applied to the primary pulley; and regulating the pressing force of the belt that connects the primary and secondary pulleys, by regulating the pressure supplied to the cylinder of the secondary side, which is formed in one chamber of the hydraulic pressure independently perform one of: (i) control the inlet and outlet of the working fluid and (ii) control for regulating the pressure of the working fluid relative to the cylinder primary side where the receiving area of the pressure cylinder secondary side is set so that the factor of safety relative slippage of the belt, the pressing force of the belt is obtained when the pressure supplied to the cylinder of the secondary side, is installed on C is given the lowest manageable level pressure, when the vehicle moves with a maximum speed on a level road, could have a value less than or equal to 1.5.

Accordingly, the camera centrifugal pressure can be eliminated for all practical purposes, it is possible to obtain automotive continuously variable transmission with belt drive with a simplified design.

Brief description of drawings

These and further aims, characteristics and advantages of the invention will be better understood from the following description of typical embodiments of the invention with reference to the accompanying drawings, in which similar reference positions indicated similar items. In the drawings:

figure 1 - schematic view of the power transmission of the vehicle corresponding to one example of a variant embodiment of the invention;

figure 2 - table of application of the clutch and brake, showing the operating States of the power transmission of the vehicle shown in figure 1;

figure 3 is a view in cross section the construction of the pulley continuously variable transmission output side, which is the element variable transmission with belt drive shown in figure 1;

4 is a schematic diagram of the hydraulic circuit pressure, which forms the control unit of the hydraulic pressure is, which delivers the working fluid in the transmission device powered vehicle shown in figure 1;

5 is a table which gives results of calculations of the factor relative to the vehicle, which was applied to a typical embodiment of the invention, and the various parameters used in this calculation;

6 is a sectional view of the secondary pulley, which forms an element related variable transmission with a belt drive; and

7 is a schematic diagram of the hydraulic circuit pressure, which forms the control unit of the hydraulic pressure according to another variant example of implementation of the invention.

Detailed description of preferred embodiments of the invention

Figure 1 shows a schematic view of the device 10 of the power transmission in the vehicle corresponding to one example of a variant embodiment of the invention. The device 10 of the power transmission in the vehicle is an automatic transmission for a motor with a transverse, and which can be used in a vehicle with a front engine layout and front drive. Automotive device 10 of the power transmission includes an engine 12, which serves as a source of power for movement. Exposure is the amount of force of the engine, which is an internal combustion engine, is transmitted from a crankshaft of the engine 12 and the torque Converter 14, which carries the liquid clutch, final gear transmission 22 through the device 16 switching to-and-fro motion, the input shaft 36, part 18 for continuously variable transmission with belt drive and the device 20 of the reduction gear, after which it is divided into right and left driven wheels 24L and 24R. Here, the device 16 switching to-and-fro motion 16 and part 18 for continuously variable transmission with belt drive together form a continuously variable transmission 30 with a belt drive. In this regard, part 18 for continuously variable transmission with a belt drive in this example embodiment of the invention also can be considered as a continuously variable transmitting portion corresponding to the invention.

The torque Converter 14 is designed to transmit power through the liquid and includes a pump wheel R, which is connected to the crankshaft of the engine 12, and the rotor 14t turbine, which is connected to the device 16 switch for reciprocating motion through the shaft 34 of the turbine. In addition, between pump wheel R and rotor 14t turbines installed blocking clutch 26 of the torque Converter. Switching the supply of hydraulic pressure between the water the practical camera side clutch and the hydraulic chamber side trip through the switching valve control device of hydraulic pressure, which is not shown, or a similar tool, causes the clutch or release the locking of the coupling 26. When the locking sleeve 26 is fully entered in the engaged position, the pump wheel R and the rotor 14t turbines rotate together as a single item. At the pump wheel R applied mechanical oil pump 28. This mechanical oil pump 28 generates a hydraulic pressure used for shift control part 18 for continuously variable transmission with belt drive, creates the force of the compression belt and provides lubrication of the various parts.

The device 16 switch for reciprocating motion includes a planetary transmission with two gears as its main component. The shaft 34 of the turbine of the torque Converter 14 as a whole is connected with a sun gear 16s node planetary gear set and the input shaft 36 of the continuously variable transmission part 18 with a belt drive as a whole is connected with the planet carrier 16C planetary gear, and a carrier 16C and the sun gear 16s can be selectively connected to each other by means of the clutch C1 for forward movement. The ring gear 16r planetary gear set is selectively fixed to the casing using reverse brake B1. And the clutch C1 for forward and reverse brake B1 are devices hydraulic clutch, which Riccio is but concatenated hydraulic cylinder. As shown in figure 2, the clutch of the clutch C1 of the forward and reverse clutch brake B1 causes the device 16 switch for reciprocating motion rotates as a single unit, thus placing the transmission line capacity to move forward so that the forward rotation is transmitted continuously variable transmitting portion 18 with a belt drive without sacrificing speed. On the other hand, by clutch reverse brake B1 and the disengagement of the clutch C1 of the forward movement in the device 16 switch for reciprocating movement is set to the transmission line capacity to move backward so that the input shaft 36 is rotated in the opposite direction relative to the rotor 34 of the turbine, which leads to the transmission of reverse rotation of the continuously variable transmission part 18 with a belt drive. In addition, the clutch and the clutch C1 of the forward and reverse brake B1 sets the device 16 switch for reciprocating motion in the neutral position (open position)in which the power transmission is stopped.

Continuously variable transmitting portion 18 with a belt drive includes a pulley 42 variable transmission input side, the pulley 46 variable transmission output side and the drive belt 48. The pulley 42 variable transmission input sides of the, located on the input shaft 36, is an element of the input side variable effective diameter. The pulley 46 variable transmission output side, located on the output shaft 44, is an element of the output side, which also has a variable diameter. Belt drive 48 acts as a transmission element power, which is wrapped around pulleys 42 and 46 variable transmission with a friction contact with them, so that power is transmitted by friction between the drive belt and the pulleys 42 and 46 variable transmission. The pulley 42 variable transmission includes a fixed part 42 of the pulley, the movable pulley 42b and the hydraulic cylinder 42s input side. Similarly, the pulley 46 variable transmission includes a fixed portion 46a of the pulley, the movable pulley 46b and the hydraulic cylinder s input side. The fixed part 42 of the pulley mounted on the input shaft 36, while the fixed part 46a of the pulley mounted on the output shaft 44. The movable part 42b of the pulley is located on the input shaft 36 in such a manner that it can move axially but cannot rotate around its axis with respect to the input shaft 36. Similarly, the movable part 46b of the pulley is located on the output shaft 44 so that it can move in the axial direction, but not the may rotate about its axis relative to the output shaft 44. Hydraulic cylinder 42s input side creates an axial load, which changes the width of the V-shaped groove between the fixed part 46a of the pulley and the movable part 46b of the pulley, while the hydraulic cylinder s output side generates an axial load, which changes the width of the V-shaped groove between the fixed part 46a of the pulley and the movable part 46b of the pulley. The gear ratio γ (that is, the gear ratio γ = velocity NINrotation of the input shaft/speed NOUTthe rotation of the output shaft) is continuously changed by changing the width of the V-shaped groove formed by two movable pulleys 42 and 46, and, thus, the diameter of the wraps (effective diameter) of the belt 48 around these pulleys, the controlled hydraulic pressure in the hydraulic cylinder 42s input side pulley 42 variable transmission input side. Meanwhile, the compression force exerted by the drive belt 48 is changed by regulating the hydraulic pressure in the hydraulic cylinder s output side pulley 46 variable transmission output side. The drive belt 48 is made of left and right metal strips 51, each of which is formed of many steel layers, which are inserted into a variety of metal elements 49. In this regard, the pulley 42 variable transmission input side in this example, Varian is but carrying out the invention may be regarded as the primary pulley according to the invention, and the pulley 46 variable transmission output side may be considered as secondary pulley according to the invention. In addition, the hydraulic cylinder 42s input side in this example, a variant embodiment of the invention can be considered as a cylinder primary side according to the invention, the hydraulic cylinder of the output side s can be considered as a cylinder secondary side according to the invention, and the drive belt 48 can be considered as a belt according to the invention.

Figure 3 shows a view in cross section showing part of the construction of the pulley 46 variable transmission output side, which forms an element of the continuously variable transmission 30 with the belt drive shown in figure 1. As described above, the pulley 46 variable transmission output side includes a fixed portion 46a of the pulley, the movable pulley 46b and the hydraulic cylinder s input side. The fixed part of the pulley 46a is formed as a unit with the output shaft 44, which is rotatably held at both ends by bearings, not shown. The movable part 46b of the pulley mounted on the output shaft 44 so that it can move in the axial direction but does not rotate around its axis relative to the output shaft 44. Hydraulic cylinder s output is located on the opposite side with the Auron from the movable part 46b of the pulley relative to the fixed portion 46a of the pulley. The fixed part of the pulley 46a is formed in the form of a round disc, protruding in the radial direction, and a fixed side inclined surface 50 formed on the side opposite the movable part 46b of the pulley. The movable part 46b of the pulley includes a cylindrical part 52, mounted on the output shaft 44, and the flange portion 54 in the form of a disc, which acts in the radial direction from the end part of the cylindrical part 52. Many of grooves, not shown, passing in the axial direction, is formed in the radial direction on the inner peripheral surface of the cylindrical part 52 and the outer peripheral surface of the output shaft 44. These grooves are combined with each other, i.e. are arranged so that they are always in the same phase in the circumferential direction, with ball bearings, not shown, are located so that they are between the opposing grooves. Accordingly, the cylindrical portion 52 is able to smoothly move in the axial direction of the output shaft 44 by means of ball bearings, but not able to rotate around the output shaft 44. In addition, the flange portion 54 is connected as a single unit with the cylindrical portion 52 and has an inclined surface 56 of the movable part, formed on the side opposite to the fixed portion 46 of the pulley. The inclined surface 50 of the fixed side and the inclined surface 56 of the movable side together form a V-shaped groove 58, which passes the belt drive 48. Here, the tilt angle or the so-called angle-side inclined surface 50 of the fixed side and the inclined surface 56 of the movable side forms 11 degrees. In addition, figure 3 part above the axial center of the output shaft 44 is shown in a state in which the movable part 46b of the pulley is moved to the position closest to the side of the fixed portion 46a of the pulley so that the belt 48 is located at the outer periphery of the groove 58, while the part below the axial center of the output shaft 44 is shown in a state in which the movable part 46b of the pulley is moved to the position most remote from the fixed portion 46a of the pulley, so that the drive belt 48 is located at the inner periphery of the groove 58.

Hydraulic cylinder s output side includes a partition 60, mounted on the output shaft 44 so that it cannot move in the axial direction relative to the output shaft 44, the movable portion 46b of the pulley and the spring 62 disposed between the wall 60 and the movable part 46b of the pulley. The partition 60 is a cylindrical element which at one end has a closed bottom which is settled and the output shaft 44 so that that it is not able to move in axial direction relative to the output shaft 44. This baffle 60 includes a first disc-shaped portion 60A, which recedes in the radial direction from the outer peripheral surface of the output shaft 44, the cylindrical portion 60b, which runs in the axial direction of the movable part 46b of the pulley from the outer peripheral end of the first disc-shaped portion 60A, and a second disc-shaped portion 60C, which recedes in the radial direction from one end of the cylindrical portion 60b. The inner peripheral part of the first disc-shaped portion 60A is located between the stepped part formed on the output shaft 44, and a cylindrical spacer 64 installed around the outer peripheral surface of the output shaft 44, and thus, not able to move in the axial direction. The outer peripheral edge of the second disc-shaped portion 60C sealed impervious to oil seal using o-rings 67 relative to the inner peripheral cylindrical surface of the cylindrical portion 66 located on the flange portion 54 of the movable part 46b of the pulley. In addition, between the first disk-like part 60A of the partition 60 and the flange part 54 of the movable part 46b of the pulley is spring 62, which constantly exerts an axial force to move the movable h the STI 46b pulley to the fixed pulley 46a. Here one camera 68 hydraulic pressure formed by the movable part 46b of the pulley, baffle 60 and the output shaft 44. When the preset hydraulic pressure is supplied to this chamber 68 hydraulic pressure, hydraulic pressure moves the movable pulley 46b in the direction of the fixed portion 46a of the pulley so that it shrinks in the axial direction of the drive belt 48, which is in the groove 58.

The oil channel 70, passing in the axial direction, is formed inside the output shaft 44, and formed the oil channels 72 and 74, which pass from the oil passage 70 in the radial direction. In addition, the oil channel 76 is formed so that it passes from the inner periphery to the outer periphery of the cylindrical part 52 of the movable part 46b of the pulley. If the working fluid is supplied to the oil channel 70 when the movable part 46b of the pulley is in the state shown in part under axial center of figure 3, the working fluid passes through the oil channel 72, and via the oil channel 76, which is connected to the oil channel 72 and into the chamber 68 of the hydraulic pressure. Axial load of the hydraulic pressure of the working fluid in addition to the force of elasticity of the spring 62 moves the movable portion 46b of the pulley in the direction of the fixed portion 46a of the pulley, squeezing, thus, the drive belt in the axial healthy lifestyles the Institute. In addition, when the movable part 46b of the pulley is moved to a predetermined position, the camera 68 hydraulic pressure starts to communicate with an oil channel 74 so that the working fluid is also fed from this channel 74. The oil channel 70 is connected with the circuit 78 hydraulic pressure device 77 regulation of hydraulic pressure, which will be described later.

Figure 4 shows the circuit 78 hydraulic pressure that generates a device 77 adjust the hydraulic pressure of the hydraulic pressure in the hydraulic cylinder 42s input side and the hydraulic cylinder s output side.

The pressure of the working fluid sucked from the oil pan 80 through the filter 82 coarse, increases the oil pump 28, and then it is fed to the oil channel 86. The pressure of the working fluid in the oil channel 86, that is, the output pressure of the pump is regulated by the valve 88 to control pressure, which is controlled based on the output signal of the hydraulic pressure from the solenoid SLT. This regulated pressure is the pressure PL in the pipeline. When the working fluid having the pressure PL in the pipeline, is supplied to the oil channel 90, which is branched from the oil passage 86, the pressure is regulated by the valve 92 to control pressure, to ascertain the major oil channel 90. The control valve 92, the pressure control is carried out based on the output signal of the hydraulic pressure supplied from the solenoid SLS regulation of the compression belt. A working fluid with a regulated pressure through the oil channel 70 to the output shaft 44 and is supplied to the hydraulic cylinder s output side. Accordingly, the compression force acting on the belt drive 48, wrapped around a pulley 42 variable transmission input side and the pulley 46 variable transmission output side, can be adjusted by controlling the pressure of the working fluid supplied to the hydraulic cylinder s output side.

On the other hand, the working fluid supplied from the oil passage 86 in the oil channel 94, is supplied to the valve 96 controls the speed change. The valve 96 controls the change speed solenoid switches DS1 hand speed and the solenoid DS2 side to reduce the speed for opening and closing the connection between the hole 98 of the pressure in the pipe and a drain hole 100, and the outlet 102 of the hydraulic cylinder 42s input side pulley 42 variable transmission input side. For example, when the solenoid DS1 hand speed is enabled, opens a connection between the hole 98 of the pressure in the pipeline and in the original hole 102 so that the pressure PL in the pipe is fed into the hydraulic cylinder 42s input side. On the other hand, when the solenoid DS2 side of the speed reduction enabled, opens a connection between the outlet 102 and a drain hole 100 so that the working fluid is discharged from the hydraulic cylinder 42s input side. By controlling the supply and release of fluid to the hydraulic cylinder 42s input side and out of the radius of rotation of the drive belt 48, which passes around the pulley 42 variable transmission input side, is changed accordingly so that the continuously variable transmitting portion 18 with a belt drive smoothly switches. In addition, as described above, the pressure in the pipeline in this example, a variant embodiment of the invention is regulated by the valve 88 to control the pressure through the solenoid SLT and the hydraulic pressure POUT(MPa) regulating force of the compression belt is fed into the chamber 68 of the hydraulic pressure of the hydraulic cylinder s output side, is regulated by the valve 92 to control the pressure through the solenoid SLS regulation of the compression belt. As the pressure in the pipe, and the hydraulic pressure POUT(MPa) regulating force of the compression belt can be adjusted independently. Various solenoid valves used in in the trojstva 77 to control the hydraulic pressure, preferably controlled by an electronic control device on the basis of different technical data coming from the sensor, vehicle speed sensor value pressing on the accelerator pedal and the like, which are not shown.

In this example, a variant embodiment of the invention, the camera 214 compensation of the centrifugal hydraulic pressure described above and shown in Fig.6, are excluded from the design. In the typical case, when the camera compensate for the centrifugal hydraulic pressure is not applied, the compression force of the belt attached to the belt drive 48, becomes excessive, when the vehicle moves with great speed, the centrifugal hydraulic pressure in the chamber 68 of the hydraulic pressure, is shown in figure 3. Here the coefficient For the stock is used as an indicator of relative slippage of the belt, the compression forces exerted by the drive belt 48. The ratio For a stock is calculated, for example, according to the expression (1)below, which is well known.

Here POUT(MPa) represents a hydraulic pressure regulating force of the compression belt, that is, hydraulic pressure adjusting belt tension supplied into the chamber 68 of the hydraulic pressure of the hydraulic cylinder s output sides of the. The symbol β represents the ratio of the centrifugal hydraulic pressure (MPa/(km/h)2) hydraulic cylinder s output side, V (km/h) represents the vehicle speed, SOUT(mm2) is receiving pressure area chamber 68 hydraulic pressure, W (N) represents the load of the spring 62, T (Nm) represents the transmitted torque, θ (rad.) is the side angle of the fixed and mobile parts 46a and 46b pulley, D (m) is the diameter of the wrapping belt 48 on the side of the pulley 42 variable transmission input side and µ is the coefficient of friction between the transfer belt 48 and pulley 46 variable transmission output side.

If the ratio of the stock falls below 1.0, belt 48 will slip relative to the pulley 46 variable transmission output side. On the other hand, if the ratio For the stock to increase beyond a value of 1.0, then the compression force of the belt attached to the belt drive 48, becomes excessive, thus reducing the service life of a belt drive 48 and reducing its efficiency. In this case, although there is some fluctuation of the friction coefficient associated with the tolerances in the manufacture of the belt 48, the coefficient For stock usually installed, for example, approximately in the range of the e from 1.0 to 1.5 and preferably in the range of from 1.2 to 1.5, inclusive.

Here, in this example, a variant embodiment of the invention, even if the camera compensate for the centrifugal pressure of the pulley 46 variable transmission output side is not applied, hydraulic pressure POUTcontrol power compression belt and the region SOUTadmission pressure of the cylinder chamber 68 hydraulic pressure is set so that the coefficient For the stock was in the aforementioned range. Figure 5 shows a table which gives results of calculations of K0stock in the vehicle in this example, a variant embodiment of the invention, and the various parameters used in this calculation. Factor K0stock is calculated when the lowest preset pressure which may be regulated by valve 92 to control the force of the compression belt-driven hydraulic pressure POUT(hereinafter also referred to as "the smallest adjustable pressure"), is fed into the chamber 68 of the hydraulic pressure of the hydraulic cylinder s output side when driving with a maximum speed on a level road, that is, when the vehicle is moving at maximum speed on a level road when the centrifugal hydraulic pressure is the greatest.

K0stock for the vehicle in this example, a variant of the embodiment of the invention installed on a level, for example, 1,18. In this case, the coefficient For the stock has a value of less than 1.5.

In addition, pressure indicator hydraulic pressure POUTpower regulation compression belt chamber 68 hydraulic pressure of the hydraulic cylinder s output side at maximum speed on a level road, shown in figure 5, is 0,327 (MPa), which is higher than the lowest adjustable pressure of 0.2 (MPa). Here is a calculated indicator pressure calculated under the condition that the coefficient For stock is 1.3, and, thus, the required hydraulic pressure coefficient For the stock of 1.3. In this regard, the coefficient of friction µ, in the typical case, is approximately 0,08-0,10. While calculating the coefficient of friction µ is defined as 0,09. In addition, the lowest controllable pressure is set based on the technical data of the system to control the hydraulic pressure applied to each vehicle.

To achieve the above coefficient K0reserve indicator and pressure in the vehicle in this example, variants of the invention, the region SOUTadmission pressure of the cylinder chamber 68 hydraulic pressure of the hydraulic cylinder 46c of the output side is set small. In the vehicle in this example, a variant embodiment of the invention ar is e S OUTtaking the pressure cylinder is set as 121,4 (cm2). In this regard, the region SOUTtaking the pressure cylinder is set such that the ratio To the stock did not fall below 1.0 in the context of the maximum transmitted torque and the maximum adjustable pressure when the vehicle is stopped. Job small area of SOUTreceiving pressure cylinder also results in a smaller ratio of the centrifugal hydraulic pressure so that the coefficient For stock becomes smaller according to the Expression (1). When the intake pressure is set small, the pressure PL in the pipeline required to create a given compression force of the belt increases, which may adversely affect the efficiency, due to the increased load on the oil pump 28. On the other hand, the resulting circuit hydraulic pressure in which the pressure PL in the pipeline in this example, a variant embodiment of the invention is regulated by the solenoid SLT and valve 88 to control pressure, and the controlling force of the compression belt hydraulic pressure POUTsupplied into the chamber 68 of the hydraulic pressure of the hydraulic cylinder s output side, is regulated by the solenoid SLS control the compression belt and valve 92 to control the pressure. Since the pressure PL in the pipeline, the hydraulic pressure P OUTcontrol power compression belt can be adjusted independently, increasing the pressure PL in the pipeline can be kept to a minimum. There is an increase in pressure PL in the pipeline is limited by the range of speed reduction (gear ratio γ>1,0), where the hydraulic pressure supplied to the hydraulic cylinder s output side becomes higher than the hydraulic pressure supplied to the hydraulic cylinder 42s input side, and thus, is limited to cases, as when starting from standstill or low transmission when driving at a low speed. Thus, by holding the increase of the pressure PL in the pipeline at a minimum adverse impact on practical fuel consumption is restrained.

In addition, in the vehicle of this example variant of the invention, the lowest controllable pressure is set low. More precisely, in the vehicle in this example, a variant embodiment of the invention lowest controllable pressure is 0.2 (MPa), as shown in figure 5. Accordingly, the indicated pressure for the vehicle in this example, a variant embodiment of the invention, comprising 0,327 (MPa)exceeds 0,2 (MPa), which means that it can be managed. If the chamber 68 side hydraulic the ski pressure supplied air, when the hydraulic pressure in the chamber 68 of the hydraulic pressure of the hydraulic cylinder s output side is reset, the responsiveness when the hydraulic pressure decreases. Thus, it is necessary to apply the hydraulic pressure required to fill the chamber 68 of the hydraulic pressure of the working fluid. The required hydraulic pressure is lowest controllable pressure, but in this example, a variant embodiment of the invention applied to the control valve of the hydraulic pressure, which regulates the pressure to a very low pressure to reduce the low pressure. Also managed to reduce changes in the control valve, for example, by controlling the hydraulic pressure sensor hydraulic pressure or a similar tool.

In addition, in the vehicle in this example, a variant embodiment of the invention for holding the centrifugal hydraulic pressure at a minimum speed of rotation of the pulley 46 variable transmission output side is relatively low. In design, such as in the vehicle in this example, a variant embodiment of the invention, in which the rotation from the engine 12 is transmitted continuously variable transmitting portion 18 with a belt drive is ez low speed and in which the gear device 20 is located after continuously variable transmitting portion 18 with a belt drive, the speed of rotation of the pulley 46 variable transmission output side relative to the speed of movement of the vehicle is determined by the gear ratio of this gear device 20 and the radius of the tire. Accordingly, the rotation speed can be reduced by reducing the gear ratio of the gearbox or increase the radius of the tire.

In addition, in the vehicle in this example, a variant embodiment of the invention uses the motor 12, which can produce a relatively large torque So as a result, the coefficient For stock can be set low. Considering all these factors, the coefficient For stock can be maintained at a lower level in comparison with K-factor0stock above, and can always keep the pressure equal to or greater than the lowest controllable pressure.

Accordingly, despite the fact that the compression force of the belt can be excessive at maximum speed due to the increase of the axial load produced by the centrifugal hydraulic pressure, pushing the movable portion 46b of the pulley movable pulley 46 to the output side in the direction that increases the force of the compression belt, because there is no camera to compensate for the centrifugal hydraulic pressure to neutralize this axial load, according to b is stupenchatoi transmitting part 30 with a belt drive in this example is a variant embodiment of the invention the compression force of the belt is restrained from reaching excessive levels by reducing the area of S OUTreceiving pressure hydraulic cylinder s output side. In this case, you also reduce pressure applied to the hydraulic cylinder s output side. On this point independent control of the pressure PL in the pipeline and regulation of the hydraulic pressure POUTregulation of the force of the compression belt in the hydraulic cylinder of the output side makes possible the elimination of such problems as excessive reduction in pressure PL in the pipeline and hydraulic pressure POUTcontrol power compression belt in the hydraulic cylinder s output side, or the inability of the switch to increase speed due to the fact that the hydraulic pressure required to switch continuously variable transmitting portion 18 with a belt drive, is not supplied to the hydraulic cylinder 42s input side 42s, etc. in Addition, when the area SOUTreceiving pressure hydraulic cylinder s output side is reduced, the pressure PL in the pipeline must be increased to increase the hydraulic pressure supplied to the hydraulic cylinder s output side when the vehicle is moving at low speed. However, if the pressure PL in the pipeline can be adjusted independently of the hydraulic pressure POUTregulation forces siati the belt in the hydraulic cylinder s output side, increasing the pressure PL in the pipeline may be limited to a sharp decrease of the range of reduction rate (γ>1), resulting in adverse effects on practical fuel consumption can be eliminated. In addition, the region SOUTreceiving pressure cylinder hydraulic cylinder s output side is reduced, while the factor of safety relative to the skew of the belt, the pressing force of the belt is obtained when the pressure supplied to the hydraulic cylinder s output side, set to the lowest value of pressure while driving with a maximum speed on a level road in which the vehicle moves with a maximum speed on a level road, takes a value less than or equal to 1.5, which allows you to save the life of the belt without deterioration. As a result the camera compensate for the centrifugal hydraulic pressure from all practical considerations may be excluded when Troubleshooting problems described above of the prior art.

In addition, the continuously variable transmission 30 with a belt drive in this example, a variant implementation of the invention is lighter, more compact and less expensive, because the camera compensation hydraulic pressure is excluded from the design. In addition, there is no need to work W is dcosta, served in the camera compensate for the centrifugal hydraulic pressure, causing the volume of the oil pump can be reduced.

Next will be described another example of a variant embodiment of the invention. Parts in this embodiment of the invention, which are similar to parts in the example of a variant embodiment of the invention described above will be denoted by the same reference positions, and their description will be omitted.

7 shows a block diagram of the circuit 302 hydraulic pressure, which is generated by the device 300 to control the hydraulic pressure corresponding to another example of a variant embodiment of the invention. The design unless the device 300 to control the hydraulic pressure similar to an automotive device 10 of the power transmission described above, and its description will be omitted.

The pressure of the working fluid sucked from the oil pan 80 through the filter 82 coarse, increases the oil pump 28 and then supplied to the oil channel 304. The pressure of the working fluid in the oil channel 304, i.e., the output pressure of the pump is regulated by the valve 306 pressure regulation. Regulated pressure is the pressure PL in the pipeline. The working fluid having the pressure PL in the pipeline, served in the oil channels 310 and 312, which autotweets is from a branch point in the oil channel 308. The pressure of the working fluid supplied to the oil channel 310, is regulated by the regulating valve 314. The valve 314 of the pressure regulation is controlled based on the output signal of the hydraulic pressure from the solenoid SLP to control the hydraulic pressure on the input side. The working fluid with regulated pressure is fed to the hydraulic cylinder 42s input side pulley 42 variable transmission input side.

On the other hand, the pressure of the working fluid supplied to the oil channel 312, is regulated by the valve 316 pressure regulation. Valve 316 pressure regulation is controlled based on the output signal of the hydraulic pressure supplied from the solenoid SLS control hydraulic pressure output side. The working fluid with regulated pressure is fed to the hydraulic cylinder s output pulley 46 variable transmission output side.

In addition, the signal hydraulic pressure from the solenoid SLP to control the hydraulic pressure of the input side and the solenoid SLS control hydraulic pressure output side is received by the valve 318 three-way switch. The valve 318 three-way toggle switches with solenoid SLP to control the hydraulic pressure of the input side and the solenoid SLS control hydraulic pressure output the side for opening and closing communication between the first inlet 320 and the second inlet port 322 and the outlet 324. For example, when the solenoid SLP to control the hydraulic pressure on the input side is enabled, communication between the first inlet 320 and the outlet 324 is open, because the signal hydraulic pressure solenoid SLP to control the hydraulic pressure on the input side is input as the control pressure for the pressure regulated valve 306. On the other hand, when the solenoid SLS control hydraulic pressure output side is enabled, the connection between the second inlet port 322 and the outlet 324 is open so that the signal hydraulic pressure solenoid SLS control hydraulic pressure output side is supplied as control pressure to the valve 306 pressure regulation. Accordingly, the pressure PL in the pipeline is regulated according to the quantitative ratio between the signal hydraulic pressure solenoid SLP to control the hydraulic pressure of the input side and the solenoid SLS control hydraulic pressure output side, and to the valve 306 pressure regulating a higher hydraulic pressure. In addition, the valve 306 pressure regulation is controlled by a higher hydraulic pressure for regulating the pressure PL in the pipeline. On the other hand, the hydraulic pressure POUTforce control with the Atiyah belt, supplied into the chamber 68 of the hydraulic pressure of the hydraulic cylinder s output side, is regulated by the valve 316 pressure regulation through the solenoid SLS control hydraulic pressure output side, and thus, the pressure PL in the pipeline and hydraulic pressure POUTcontrol power compression belt can be adjusted independently.

This type of circuit 302 hydraulic pressure is also able to achieve results similar to effects achieved in the variant example of implementation of the invention described above and, thus, eliminates the use of cameras compensation hydraulic pressure for all practical purposes.

Above have been described examples of embodiments of the invention with reference to the accompanying drawings. There might also be other examples of embodiments of the invention.

For example, in the circuits 78 and 302 hydraulic pressure in the above typical embodiments of the invention, the pressure PL in the pipeline and hydraulic pressure POUTcontrol power compression strap supplied into the chamber 68 of the hydraulic pressure of the pulley 46 variable transmission output side can be adjusted independently. However, since the hydraulic pressure can be adjusted independently, the invention can also apply the I circuit hydraulic pressure, having another structure.

In addition, these typical embodiments of the invention a continuously variable transmitting portion 18 with a belt drive is switched by controlling the supply and discharge of hydraulic pressure in the hydraulic cylinder 42s input side and out. However, the invention can also be applied in the design, in which the continuously variable transmission part with a belt drive is switched by regulating the pressure of the working fluid supplied to the hydraulic cylinder 42s input side.

In addition, the car device 10 transmit power in these examples of embodiments of the invention is used in vehicles with front-engined and with drive to the front wheels, although the invention can also be used with the vehicle of another type, such as a vehicle with four-wheel drive. Furthermore, the design, etc. of the switching device 16 for reciprocating motion can be easily modified in a way appropriate to the scope of the invention.

Although the invention has been described with reference to typical variations in its implementation, it should be understood that the invention is not limited to the described variants or designs. On the contrary, the invention provides coverage of the various options the brand and equivalent devices. In addition, although the various elements of the described embodiments of the invention shown in the various examples of combinations and configurations, other combinations and configurations, including more, less or only a single element, are also consistent with the essence and scope of the invention.

1. Automotive continuously variable transmission with belt drive for use in a vehicle moving at speeds up to maximum speed, and a continuously variable transmission with belt drive includes a continuously variable transmitting portion (18), which rotation is transmitted from the source of power without sacrificing speed, while the vehicle moves forward, and one camera (68) hydraulic pressure applied to the secondary pulley (46), characterized in that it contains: device (77) control hydraulic pressure that switches the continuously variable transmitting portion (18) by controlling one of the i) supply and discharge of working fluid, and ii) the pressure of the working fluid relative to the cylinder (42s) the primary side, is applied to the primary pulley (42), and adjusts the pressing force of the belt (48), wrapped around a primary pulley (42) and a secondary pulley (46), by regulating the pressure supplied to the cylinder (s) secondary side formed by one camera (68) Hydra is symbolic of pressure, the device (77) to control the hydraulic pressure independently regulates the line pressure and the pressure applied to the cylinder (s) secondary side, and the receiving area of the pressure cylinder from the cylinder (s) secondary side is set such that the ratio of the reserve force of the compression belt relative slippage of the belt is obtained when the pressure supplied to the cylinder (s) secondary side, set on the specified lowest level of the controlled pressure when the vehicle is moving at maximum speed on a level road, has a value less than or equal to 1.5.

2. Transmission according to claim 1, characterized in that the receiving area of the pressure cylinder from the cylinder (s) secondary side is set such that the ratio of the reserve force of the compression belt relative slippage of the belt is obtained when the pressure supplied to the cylinder (s) secondary side, set on the specified lowest level of the controlled pressure when the vehicle is moving at maximum speed on a level road, has a value of from 1.0 to 1.5, inclusive.

3. Transmission according to claim 2, characterized in that the receiving area of the pressure cylinder from the cylinder (s) secondary side is set such that the ratio of the reserve force of the compression belt relative slippage of the belt is obtained, when the pressure supplied to the cylinder (s) secondary side, set on the specified lowest level of the controlled pressure when the vehicle is moving at maximum speed on a level road, has a value of from 1.2 to 1.5, inclusive.

4. The method of controlling an automotive continuously variable transmission with belt drive for use in a vehicle moving at speeds up to maximum speed, and a continuously variable transmission belt transmission includes a continuously variable transmitting portion (18), which receives rotation from a source of power without sacrificing speed, while the vehicle moves forward, and one camera (68) hydraulic pressure applied to the secondary pulley (46), characterized in that it includes steps in which: the switch continuously variable transmitting portion (18) by controlling one of: (i) filing and release the working fluid, and ii) the pressure of the working fluid relative to the cylinder (42s) the primary side, is applied to the primary pulley (42); and adjust the compression force of the belt (48), which is wrapped around the primary (42) and secondary (46) pulleys, by regulating the pressure supplied to the cylinder (s) secondary side, which is formed by a single camera (68) hydraulic pressure independently perform one of (i) management is odaca and release of the working fluid, and (ii) control for regulating the pressure of the working fluid relative to the cylinder (42s) primary hand, when this receiving area of the pressure cylinder (s) secondary side, set so that the factor of safety relative slippage of the belt forces the compression belt is obtained when the pressure supplied to the cylinder (s) secondary side, set at the specified lower controlled pressure level, when the vehicle moves with a maximum speed on a level road, has a value less than or equal to 1.5.



 

Same patents:

FIELD: transport.

SUBSTANCE: shifting device with servoamplifier (10) for vehicle gearbox includes means for selecting and shifting gears and control rod (20) of servoamplifier (10). The servoamplifier (10) is affected by manual shifting force to be amplified. Herewith, means (90, 100, 112, 114, 150) are provided. These means have elasticities (e.g. as springs) to modify affecting the servoamplifier (10) force of manual shifting inside servoamplifier (10) before and/or during creation of secondary force.

EFFECT: low-consumption flow of affecting and secondary force limiting process.

12 cl, 8 dwg

Sheave // 2362073

FIELD: mechanical engineering.

SUBSTANCE: invention relates to mechanical engineering, particularly to sheaves for usage in impregnating devices. Sheave contains rim collars, which are connected by common central axis. Rim collars are also connected to each other by axis. On specified axis there are located free hubs. Amount of specified axis with located in it bushes can be eight items.

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FIELD: engines and pumps.

SUBSTANCE: invention relates to the two-stage belt transmission system to actuate the vehicle engine auxiliary equipment with the first and second transmission ratios. The system incorporates a clutch assembly fitted on the drive rotary shaft, a one-direction clutch fitted directly on the rotary shaft. The system incorporates also a good few rotary auxiliary appliances coupled to rotate along with the clutch assembly and, via the one-direction clutch, with the rotary shaft connected so that the said auxiliary appliances are driven from the clutch assembly with the first transmission ratio and actuated directly by the rotating shaft via the one-direction clutch with the second transmission ratio. The clutch assembly is designed to operate at a preset engine operating condition so as to set a transfer between the first and second transmission ratios. The clutch assembly is engaged on starting the engine up.

EFFECT: two-stage belt transmission, lower and narrower driving speed ranges.

40 cl, 15 dwg, 4 tbl

FIELD: mechanics.

SUBSTANCE: invention relates to assemblies for converting rotary movement to progressive movement and may be used for various actuators including window lifts in cars. Converter consists of a grooved body in the form of closed shape, working element of progressive movement with drive coupling and rotary drive. Working element of progressive movement is a set of cylindrical or tapered rollers with circular grooves along generatix. Rollers are placed to each other in the grooves. Rotary drive in the shape of chain gear is installed so that in the points of teeth catching with rollers, they are located in holes formed by circular grooves between each two side-by-side rollers.

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FIELD: mechanical engineering; transport engineering.

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EFFECT: reduced overall dimensions of variable-speed drive, increased load-carrying capacity of drive chain.

3 cl, 8 dwg

FIELD: mechanical engineering.

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3 cl, 6 dwg

FIELD: mechanical engineering; drives.

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FIELD: the invention refers to machine building particularly to transmissions with flexible gearing members and may be used in mechanical draughts with changeable gear ratio.

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2 dwg

FIELD: mechanical engineering.

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FIELD: mechanical engineering, particularly gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members.

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3 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.

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27 cl, 3 dwg

FIELD: transport.

SUBSTANCE: proposed system comprises gearshift element including rod and lever parts, gearshift fork parts, multiple rod elements of gearshift mechanisms jointed to said fork gearshift parts. Lever part move to select and shift gear and gets pressed against selected gearshift ledge element. Every said element comprises a separate tooth-like ledge. Said lever part moves to selection axis and rotates about the latter to exert force in gearshift direction on one side of selected element tooth-like ledge and to exert force in gearshift direction on opposite side.

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5 cl, 14 dwg

Building vehicle // 2390679

FIELD: transport engineering.

SUBSTANCE: vehicle consists of motor, of hydraulic pump, of running hydro-motor, of running wheel, of adjustment block, of vehicle speed measurement block. The adjustment block is designed to operate under mode of reduced slipping in the range of low speed, when speed of the vehicle is less or equal to specified speed. This is designed to reduce maximal speed of motor rotation, when speed of the vehicle decreases.

EFFECT: reduced hazard of slipping.

6 cl, 9 dwg

Transmission // 2374532

FIELD: transport.

SUBSTANCE: transmission comprises gear shift element (51) displacing towards gear shift and gear shift selection directions, gear shift lever (40) having a pair of fork parts (41) spaced apart in gear shift direction and gear shift fork (20-23) linked with gear shift lever via gear shifter (30). Aforesaid element (51) is moved to displace one of aforesaid fork parts to wards gear shifting to selectively move gear shift lever to make gear shifting with the help of gear shift fork and gear shifter rod. Aforesaid pair of fork parts (41) is arranged spaced apart towards gear shifting direction.

EFFECT: fast and efficient gear shifting.

4 cl, 7 dwg

FIELD: machine building.

SUBSTANCE: invention is related to the field of motor transport machine building. System of automatic transmission control comprises pump, hydraulic distributor of modes having three positions, slide type pressure controller, hydraulic distributors of transmissions, pump filter, distributor filter, lubricating throttle, heat exchanger. In the first position hydraulic distributor of modes connects forward manifold and backward manifold to drain cavity. In the second position hydraulic distributor of modes connects forward manifold to the main manifold, and backward manifold to drain cavity. In the third position hydraulic distributor of modes connects forward manifold and backward manifold to the main manifold. Hydraulic distributors of transmissions are arranged as electromagnetic, and supply power fluid via control manifold to hydraulic cylinders of transmission control elements. Slide type pressure controller comprises stem with two pistons - left and right - that separate the stem into three sections. Pump filter is installed in supply channel between drain and controller drain channel. Distributor filter is installed in main manifold between pump and hydraulic distributor of modes. Lubricating throttle is installed in lubricating manifold, through which liquid is supplied to lubrication system. Heat exchanger is installed between lubricating system and lubricating throttle.

EFFECT: higher reliability of automatic transmission.

2 cl, 2 dwg

FIELD: machine engineering, namely stable-speed drives of subsidiary aggregates.

SUBSTANCE: drive includes planetary ball gearing 1000 with gradual variation of gear ratio; step motor, worm gearing. Planetary ball gearing includes planetary members having rolling contact with inner and outer raceways and it may gradually vary gear ratio in range 0.3 - 1.0. Inlet shaft of said gearing is joined with primary propeller such as crankshaft of transport vehicle engine through driving belt B1. Gearing includes at least one outlet shaft coaxial to inlet shaft. Processor analyzes revolution number of crankshaft and respectively varies gear ratio with use of step motor joined with worm gearing for keeping stable revolution number at outlet regardless of revolution number of crankshaft.

EFFECT: possibility for keeping stable revolution number of gearing regardless of revolution number of crankshaft of primary propeller.

21 cl, 18 dwg, 3 tbl

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable gear box comprises a number of velocity governors. Driving disk (34), driven disk, and cylindrical bearing member (18) are in contact with the first, second, and third points on each of the velocity governors. Disk (60) of the thrust bearing transmits rotation to the driving disk. At least two generators of axial loading are interposed between the driven and driving disks and disk of the thrust bearing and can apply the axial loading to the driven disk.

EFFECT: improved structure.

62 cl, 27 dwg

FIELD: mechanical engineering.

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

EFFECT: simplified control and control of gear ratio.

8 dwg

FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in wide range of vehicles, for instance, in minicars or trucks, snow movers, carts used when playing golf, cross country cars and scooters. Proposed driving pulley contains two centrifugal mechanisms, namely, positive unit and negative unit. Both units contains corresponding group of flyweights exposed to action of centrifugal force at rotation of driving pulley. Positive unit is used as standard speed governor which shifts one of two flanges of driving pulley towards other flange to increase diameter of running-over-over of driving pulley when speed rises. Negative unit is used to apply opposite force of positive unit when speed of rotation exceeds threshold value to delay rise of ratio of steplessly adjustable drive to higher ratio under action of positive unit. It provides maintenance of high speed of rotation at intensive acceleration and slow speed of rotation at slow speeds of vehicle.

EFFECT: provision of additional control over entire range of change of ratio of steplessly adjustable drive to decrease force created by centrifugal system of driving pulley.

12 cl, 6 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in wide range of vehicles, for instance, in minicars or trucks, snow movers, carts used when playing golf, cross country cars and scooters. Proposed driving pulley contains two centrifugal mechanisms, namely, positive unit and negative unit. Both units contains corresponding group of flyweights exposed to action of centrifugal force at rotation of driving pulley. Positive unit is used as standard speed governor which shifts one of two flanges of driving pulley towards other flange to increase diameter of running-over-over of driving pulley when speed rises. Negative unit is used to apply opposite force of positive unit when speed of rotation exceeds threshold value to delay rise of ratio of steplessly adjustable drive to higher ratio under action of positive unit. It provides maintenance of high speed of rotation at intensive acceleration and slow speed of rotation at slow speeds of vehicle.

EFFECT: provision of additional control over entire range of change of ratio of steplessly adjustable drive to decrease force created by centrifugal system of driving pulley.

12 cl, 6 dwg

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