Continuously variable transmission with torque control

 

(57) Abstract:

The invention relates to continuously variable transmissions of the type band - gutter knock wheel. Continuously variable transmission includes a control unit (17), controlled by the operator through the pedal (18) of the accelerator or other governing body, two nodes of pulleys, each of which includes a shaft and two gutter knock wheel that changes the gear ratio component in the form of at least one band in drive contact with two nodes pulleys, sensitive to torque relationship, which is shareavenue coupling between at least one node of the pulley and its shaft, means for creating between them an axial force, which is a function of the magnitude and direction of torque transmitted by any node of the pulley, and load tools. Continuously variable transmission made thus able to adjust torque to such an extent that would satisfy the requirements of modern vehicles. 17 C.p. f-crystals, 12 ill.

The invention relates in General to continuously variable transmissions (BT), and in particular to the change gear ratio of the composite parts ("mariateresa, a flexible and substantially inelastic band, usually having the form of a belt passing over two nodes pulleys that rotate on two parallel, but placed at a distance of axes lying in a common radial plane. Band width is not changed, while two gutter knock wheel each node of the pulley have a common axis, however, the axial clearance between them may vary and thus change the radius of the circle, which moves the strip in contact with the hub of the pulley. If gutter knock the wheels of the first of the two nodes are moved apart in the axial direction, as a result, the radius of the circle of contact of the strip decreases, while gutter knock the wheels of the second node must converge to increase the radius, thus maintaining the belt tension. At the same time, if the first and second nodes are considered respectively as input and output elements of the variator, passed its final drive ratio is reduced. On the other hand, if the gutter knock the wheels of the first node closer in the axial direction, and gutter knock the wheels of the second node parted, the result of this ratio increases. All the time during work gutter knock wheel and the first and second nodes must premastication for transmission between the desired traction. Usually one gutter knock the wheel each node pulley fixedly mounted on the shaft, while the other is mounted for sliding on the shaft with axial slots, with the plane of the gutter knock the wheel farthest from the belt, represents the surface of the piston moving in the cylinder is communicated with a source of fluid under hydraulic pressure, which creates the required axial force. Obviously, if one gutter knock the wheel each node of the fixed pulley and the other gutter knock the wheel is mounted with the possibility of axial movement, as just described, any change of gear ratio must be accompanied by a slight axial displacement of the belt relative to each node of the pulley. Means to prevent any adverse effect of this phenomenon is well known to a person skilled in the field of technology, including axial reversal of the position of two gutter knock-wheels, fixed and movable between two nodes of the pulleys, so that the direction of the axial shift of the belt in the site in which the gutter knock the wheels closer together, match the shift of the belt in the other node, in which the gutter knock of wheels is offered concerning those what has become known in the art as "adjustment ratio", which is a so to say a direct command to the hydraulic controls of the two movable gutter knock of wheels to cause a predetermined difference of a pair of gutter knock of wheels and a relative predetermined convergence of the other pair, while maintaining sufficient axial load on both nodes of the pulleys to maintain the required friction force between the belt and gutter knock wheel. In contrast, recent improvements in technology related to rotary traction BT with toroidal path, demonstrated the advantages of the so-called "torque control", when at the request of the operator, by moving acceleratorkey pedal or other control, leading torque of a certain magnitude is applied to the variator or via the drive shaft (i.e., the load torque on the engine) or through a specific output torque applied to the follower shaft. Examples of control systems of this type for BT, and examples of BT with toroidal path, well suited for such management can be found in PA is that the elements of the torque control in BT, using a variable of the type which has a band and gutter knock wheel. One such proposal appeared in the scientific report 730003 under the heading "Calculation Equation for Infinitely variable V-Belt Transmission, in which regulated the speed and torque", presented at the International Automotive engineering Congress and exposition in Detroit, Michigan, in January 1973. In the variable represented by this proposal, one of the two nodes of the pulleys has shown some ability to sense torque caused by the ability of one of the gutter knock the wheels move in a spiral around the shaft on which it is installed, while the other node of the pulley was not sensitive to torque, but felt the input speed. The report proposes the use of such BT in some specialized vehicles, such as snowmobiles. However, it should be noted that the steering movements of the operator of such vehicle shall be without any doubt connected through acceleratorkey pedal with the movements of the controller of the vehicle, this Report does not contain a disclosure that the relative motion gutter knock wheels must be the water, that BT has limited the ability of controllability due to the fact that any output load, that is to say, the output speed and output torque are within gear ratio of the variator, just a simple equilibrium combination of input speed and input torque. BT with such limited ability to controllability does not meet the requirements of modern vehicles. There is another limitation of the variator described in the Report, which is that it cannot be used for the BT, which is now very necessary for practical use in cars, when the working range is extended so that it worked in more than one so-called "mode", in each of which the variator moves from one end of interval ratios to the other end. In such multi-modal models is usual to energy circularities the variator in the closed loop in one of these modes, in which the output power of the variator and its input power act as two input planetary gear and is special is paradatec the I in the closed loop thus the output of transmission and, consequently, the vehicle to be stationary. In practice, it is necessary that in most automobile transmissions, which have such a recirculation mode, the CVT was looking for a neutral gear position, when, for example, the motor starts running and reaches the idling speed while the vehicle is to be still in a state of rest. The report does not disclose the possibility of the existence of the recirculation mode power required to achieve a neutral gear position, and in the absence of the driver described the variator just looking for one limit of its range of gear ratios.

BT carried out in accordance with the present invention also differs from the type of the variable, which is shown in the description of the patent application US-US-A - 5217412. As repeatedly stated in this Description, it refers to BT, in which the operator creates one or another value of the gear ratio of the variator and changes in the value of torque will not have a direct effect on the value of gear ratio. In accordance with the present invention direct regulation of transfer values attributed the statement creates one or another torque on one or the other shaft of the variator and within the working limits, this torque will be maintained even when changing gear ratios. Another difference from the patent application US-A-5217412 is that for effective "torque control" is desirable for communication between at least one of the nodes of the pulley and its shaft to create a force dependent on both the magnitude of torque, and its direction; this force acts in such a way that seek to change the axial cultivation gutter knock of wheels. In the patent application US-A-5217412 there is only one sentient torque link (item 24) between the two sections of the shaft of one of the pulleys. When it works in a way that feels torque, it does not create any right related to the axial force applied to promote relative movement shkilnyk gutter knock of wheels.

Feature, mainly attributable to BT ramanatha type with torque control, is - is there a sentient torque connection between the node of the pulley and its shaft, so as to enable movement of the pulley on the shaft and create a force between the pulley and the shaft, which is a function of the magnitude and naprosy generates a force that striving to breed gutter knock wheel, and whenever this shaft receives torque from the belt corresponding force tends to reduce gutter knock the wheels together. Thus, the content of the present invention should be distinguished from BT ramanatha type shown in the description of the Patent application US-US-A-5173084, in which there are potentially sentient torque of the relationship between each node of the pulley and its corresponding shaft. However, in the Patent application US-US-A-5173084 two potentially sentient torque relationships between the nodes of the pulleys and their respective shafts are different. Related to torque forces created in these two relations, act in unison on both nodes of the pulleys, or seeking to bring the wheel whenever energy is transmitted from the input shaft (12) to the output shaft (14), or to separate them, when energy is transferred in the opposite direction. As this is clearly explained in the description of the patent application, for example in the No. 5 line 23 - 32, it is made to simplify and/or reduce the volume of hydraulic pumps. Torque control is not achieved BT described in this description, and are not even mentioned any possibility torque control. It was especially from the like in the already mentioned Report 730003, prevents them from using multimode BT, which in certain circumstances requires the use of variable - for example when idling search for neutral gear position.

The present invention arose from understanding how BT is of the type which has a band and gutter knock wheel can be improved due to the fact that will be able to adjust torque to such an extent that would satisfy the requirements of modern vehicles, and which is comparable with the manageability already mentioned BT with toroidal path.

The invention defined by the claims, the contents of which are included in the description of the present invention, and discloses BT, which will be described with reference to the accompanying drawings, some of which are diagrams and performed schematically, and which

Fig. 1 is an axial section passing through the elements of the known variable that contains the belt and gutter knock wheel.

Fig. 2 is a similar view, passing through the variator in accordance with the present invention, in combination with hydraulic elements is Thor, it is shown in Fig. 2.

Fig. 4 - same as Fig.2, but shows an alternative variant of the variator.

Fig. 5 is a drawing of a hydraulic circuit.

Fig. 6 is an axial section passing through the gutter knock the wheels BT, using the diagram shown in Fig. 5.

Fig. 7 is an axial section passing through another variable.

Fig. 8 shows the hydraulic circuit connected to the variator shown in Fig. 7.

Fig. 9 and 10 is the same as that of Fig. 7, but shows other variators.

Fig. 11 shows the hydraulic circuit connected to the variator shown in Fig. 9 and 10.

Fig. 12 is an axial section, passing on to the next variable.

In the course of the description of the drawings the elements that perform essentially similar functions, may, where it allows the context, be denoted by the same reference numbers.

Fig. 1 shows a variable-speed drive, in which the belt or chain 1, a flexible but inextensible and with a constant width, transmits the traction force between the first node 2 pulley, containing gutter knock the wheels 3, 4 and the shaft 5, and the second node 6 pulley, containing gutter knock the wheels 7, 8 and the shaft 9. The shafts 5 and 9 are rotatably bhumih shafts, however gutter knock wheel 4 mounted on the shaft 5 through the spline 12 and, thus, capable of some relative axial movement. Similarly gutter knock wheel 8 mounted on the shaft 9 by using the spline 13. Gutter knock wheel 4 and 8 act as pistons, floating in the hydraulic cylinders 15 and 16, respectively, with the cylinders communicated through the block 17 management as a control element 18, and the source 19 hydraulic energy.

The shafts 5 and 9 are respectively the input and output elements of the variator, with arrows TinNinToutNoutdenote respectively the input torque, input speed, output torque and output speed of the variator. Unit 17 control operates in such a way that creates hydraulic pressure PTin the cylinder 16, sufficient to maintain belt tension, and pressure PT+PRin the cylinder 15, where PRis an increment that depends on the magnitude of the lowering pedal 18, if the increment is positive, it causes the convergence of the gutter knock of wheels 3 and 4, which leads to an increase in the value of the transfer otnositeljnogo relations. However, with gutter knock the wheels 3 and 7, mounted on the respective shafts 5 and 9, and gutter knock-wheels 4 and 8, mounted on these shafts only, with limited freedom of movement in the axial direction, there is no way, in the absence of hydraulic pressure, under which any of the gutter knock the wheels can move automatically, change the transmission ratio in response to changes in the torque transmitted by the variator. Thus, it becomes unacceptable for BT working in one, two or more modes in which recirculation occurs in at least one of these modes. This variable is also not easy, because this variable does not feel the torque, to determine the most favorable value of pressure PTthat is, for durability and performance, the least would be consistent with nebraskaland belt.

With each change command unit 17 controls the value of pressure PRchanges as soon as the node 2 pulley opens or closes, the unit 6 performs a return stroke, thus is ensured through placed on opposite sides of the cylinders 15 and 16 is that CR CLASS="ptx2">

In the corresponding variator made according to the present invention and shown in Fig. 2, gutter knock the wheels 3 and 4 node 2 is installed on the shaft 5 with the possibility of movement through the spiral slots 21, 22, respectively, these slots have different directions spiral generatrix, and gutter knock-wheels 7 and 8 node 6 is installed on the shaft 9 with axial slots 23, 24. Gutter knock wheel 3 and 7 installed as pistons, with the possibility of movement in the cylinders 25 and 26, and the cylinder chambers 15 and 25 reported among themselves and thus have the same hydraulic pressure as well as the cylinders 16 and 26. Spiral gearing between the gutter knock the wheels 3, 4 and the shaft 5 may in practice be made in the form of ball tracks, while the position of the 27 points to the balls. "Direction" spiral lines 21, 22 should be selected so as to match the direction of rotation shown by the arrows NINand NOUTat the expense of what any torque transmitted between the gutter knock wheel and belt, increases proportional to the axial force as gutter knock on the wheel and the shaft, and any application of torque will change the value of the gear ratio to reduce KRU position of the element 18 through the hydraulic unit 17 controls, now, however, separate pumps 30,31 serves fluid to the two nodes 2 and 6 of the pulleys. The pump 30 delivers fluid to the cylinders 15 and 25 node 2 through the inlet passage 32 and the pump 31 delivers fluid to the cylinders 16 and 26 to node 6 through the inlet passage 33. The fluid then leaves the cylinders nodes 2 and 6 through the outlet passages 34 and 35, respectively, where the control valves 36,37 to the drain 38. The main purpose of the valve 39 variable resistance located between the valves 36, 37 and the outlet 38, and also managed from node 17 to set the "base value" PTpressure in the cylinders, sufficient at any time when it comes to traction, to maintain sufficient tension between Globocnik wheels and belt. Now, whenever the leading conditions are such that the force is transferred from node 2 to node 6, node 17 controls the valve 36 and causes opening of the valve 37. The main pressure PTthus installed in the cylinders 16 and 26, and in the cylinders 15 and 25 node 2 set pressure PT+PCwhere PCis a function of the transmitted torque, which is the desire of the operator (using the pedal 18), and selects the external axial pressure that gutter knock the wheels 3, 4 will be implemented in response to this desire and, then the control unit 17 controls the valve 37 and opens the valve 36, thus the main pressure PTset in the cylinders 15, 25, and PTplus the PCin the cylinders 16, 26 of node 6. This control values PCmeans that the axial load forces acting on the two nodes of the pulleys directly respond to operator commands, and their values can be represented as a predefined function of the value of this command.

In a variant of the invention shown in Fig.4, gutter knock the wheel of node 2 is installed on a spiral ball screw 22 and, as before, works within the cylinder 15, but gutter knock wheel 3 mounted on the axial slot 42, which is made on the sleeve 41, made in one piece with gutter knock wheel 4. Gutter knock the wheels 3 and 4 thus rotate together, but they are capable of limited relative axial movement, and cage thrust bearing 43 mounted on the flange 44, made in one piece with the shaft 5, fix the relative axial position of the shaft and gutter knock wheel 4. Node 6 gutter knock wheel 8 mounted on the straight slots 24 and move, as before, as the piston in the cylinder 16, but gutter knock wheel 7 now just constantly connected with the shaft 9. Odnosa the IC 42 accepts torque from the gutter knock wheel 3 to the gutter knock the wheel 4, where through the screw 22 to the shaft 5. As shown in Fig . 1, the cylinders 15 and 16 on opposite sides ensures that once the gutter knock the wheel of one of the nodes 2,6 diverge, while the wheels of another node converge, and Vice versa, then the projection of the center line 20 of the belt 1 remains essentially constant.

In practice, it would be also desirable to avoid any misalignment which may occur for any reason in the course of the work between the ideal clamping force on the belt and the values of the pressures in the cylinders 15, 25, 16, 26, especially towards the range of gear ratio, when the belt is to be near its maximum and minimum radii at each node of the pulley. Although it is not identical in its effects, the aspects of this particular BT made in accordance with the present invention, can be compared with the characteristics of "hydraulic end stop for rotary traction BT with toroidal path, described for example in patent descriptions GB-B-2023753, ER-IN-0133330 and ER-IN-0444086. In Fig.2 the location and size of the exhaust passages 34 and 35 and the arrangement of the passages 45 and 46 helps to create this effect "end stop", although it will be clear that other the effect sizes would be appropriate. In node 2, pulley size and the position of the exhaust passage 34 are so chosen relative to the cylinder 15, so that, if the gutter knock the wheels 3 and 4 tend to disperse in the axial direction for a predefined limit, the gutter knock the wheel 4 will eventually completely close the passage 34, overlapping the overall yield for the two liquid communicated to the cylinders 25 and 15, thus the pressure in the two cylinders will increase until a residual pressure in the pump 30 and thus will resist further divergence gutter knock of wheels. On the other hand, if the gutter knock-wheel approach one another closer than it was pre-determined, the passage 45 is opened. This passage is communicated directly or indirectly with sink 38 through the valve 39, but under the control of the bypass valve 36. Thus this reduces the pressure in the cylinders 15, 25 and prevents further approximation gutter knock of wheels. Node 6 pulley arrangement and dimensioning of the passage 35 and the position of the passage 46 will operate to the same effect.

Will be taken into account that the action of such a mechanism hydraulic end stop" in practice can not only successfully achieve the goal of preventing a strong increase in compressive svjazanny this effect desire to retain the contact radius of the belt and gutter knock wheel in predetermined limits. In this regard, Fig. 2 also shows and mechanical end stoppers" on the pulley in the form of rings 29 mounted for rotation on the shafts 5, 9 between the gutter knock the wheels of nodes 2 and 6, which physically prevent contact of the belt 1 with each of the gutter knock of wheels, for example, if hydraulic brakes are not able to prevent the divergence of the gutter knock of wheels at a great value with which the belt can be in contact with the shafts. There is no such need for such wheels in the variant shown in Fig.4, where the sleeve 41 of the node 2 and the shaft 9, as shown in Fig. 6, rotating in a consistent mode with gutter knock the wheels of 3.4 and 7.8, respectively. Of course, many other options are physical barriers to prevent divergence or convergence gutter knock of wheels for the selected range.

Fig. 3 shows the essential elements of a dual BT, in which the primary motor 50 causes the rotation of the shaft 5 node 2 pulley (as shown in Fig. 2) with a speed of NIand also, through a belt 51, the transmitting rotation with a constant gear ratio, which reduces leading speed to a value of 1/2 of NIon one half discoraging clutch 52. The other half of the coupling is connected to a support 53 planetary element 56 BT and one of the halves 57 visokoprizemni clutch 58. The other half 59 of this clutch and the Central gear 60 of the planetary gear 54 are both connected to the output shaft 9 of the variator, so to say to a common shaft gutter knock of wheels 7 and 8.

To illustrate the operation of the vehicle containing the BT shown in Fig.2 and 3, the nature of the operations will be now explained since the state of rest. The operator can control the transmission line of the vehicle using a conventional lever switch traction control (with the entrance to the block 17, indicated schematically position 47), having at least a standard N,P,D and R positions.

When the motor 50 starts to operate with the lever traction control positions "N" or "P", both of the clutches 52 and 58 are in the position of disengagement. When selecting "D" clutch 52 will begin to occupy the position of the clutch. If the vehicle is stationary and the variator does not have a gear ratio, known in the art as "neutral" (i.e., the value of gear ratio, which for a limited rotation of the input shaft 5 creates a zero rotation of the output element 56), the braking torque will be applied to the variator clutch 52. To ten 37 and 36 control will open and there will be no pressure drop in two nodes 2, 6 pulleys. However, generally it will be "main" pressure provided by the valve 39, as has been explained. Host planetary gear 54 has a gear ratio E=2, with the belt 51 has a constant ratio equal to 1/2, as it has already been explained. In the stationary position of the vehicle belt 51 will try to drive the output shaft 9 of the variator, through the coupling 52 and the planetary gear 54, the speed, the value of which is equal to 3/2NI. The shaft 9 can actually rotate at a speed equal in value to, say, 1/2 of NIand if so, he will try to overclock both himself and the input shaft 2 of the variator. Accelerating torque on the latter will be created through the action of the helical ball track 21, 22 of the axial force, which reduces the two gutter knock the wheels 3, 4 node 2 pulley to one another, thus increasing the gear ratio. Forces will not be provided any resistance, because there is no pressure drop at nodes 2 and 6 of the pulleys.

If the value of the gear ratio will deviate from the set value, the torque on the input shaft 5 will be reversed and axial forces will throw gutter knock to areator find the right one for making the gear ratio before the vehicle will be released from the position of rest to its low-speed mode, it is to say that the mode in which the clutch 52 is in the position of the clutch, the clutch 58 is in the position of disengagement and energy is recycled by the variator.

When the pedal 18 is kept now in the lowered position, the unit 17 control registers the team and knowing the mode and the current value of the gear ratio (using the input signals, shown schematically positions 61, 62), interprets this command as the output torque or load torque on the engine. In order to move forward with a low-speed mode requires that the value of the gear ratio of the variator decreased from 3/2 to 1/2. Thus energy is transferred from node 6 to node 2, and gutter knock wheel 7,8 mounted on the output shaft 9 must move towards one another. This is called opening the valve 36 of the control unit, and a pressure rise in communicating cylinders 16, 26 is invoked by increasing the AC resistance in the valve 37.

The axial load on gutter knock the wheels 7, 8 is now applied by a set of compressive pressure generated by the valve 39 and the differential pressure created by the valve 37 torque control. The axial load on gutter knock the AK as the angles of the conical surfaces of all gutter knock of wheels is equal, it follows that when the force created by the differential (i.e., torque control) pressure balances the force from the spiral, then the gear ratio of the variator will be sustainable. As the axial force from the spiral is a function of the input torque of the variator, the pressure drop must itself be a function of this torque, whether the controlling torque pressure be attached to the node 2 pulley through the valve 36, or to node 6 through the valve 37. The pressure difference of course is also the function "output" torque of the variator, modulated instantaneous transmission ratio of the variator.

If conditions allow, the pressure differential will cause the regulator to a lower value of its ratio to 1/2. Then the block 17 will cause tripping discoraging clutch 52 and simultaneously the clutch visokoprizemni clutch 58, the values of the transmission ratio of the variator and the planetary gear were chosen so that the change is a change that is known in the art as "synchronous" and does not cause an instantaneous change of speed of rotation of the output element 56. With the clutch position of the clutch 58, and so the e rotation of the variator throughout its range gear ratio, 1/2, where he presently is, to its maximum value of 2. During this mode, whenever the energy must be transferred from the primary motor 50, a torsion load will be determined by the valve 36, the pressure control.

The action of the valve 39 in the establishment of the main compressive force between the gutter knock the wheels and the belt was already described. You must pay attention that the useful transmission power between the gutter knock the wheels and the belt is a tangential force and that there is an upper limit on the fraction of axial compressive force, as determined by the valve 39, in which this tangential force can be without slippage. This limit is determined by the coefficient of friction between the gutter knock the wheels and the belt. On the other hand, excessive compressive force will reduce the durability and efficiency.

When BT is configured to control the torque, it is straightforward to compute the tangential force at any value of gear ratio and thus to determine the optimum compressive strength. The value of gear ratio is measured simply and block 17 receives the electrical input of the dimension indicated by the position 62. Tangentially wheel, and this radius is itself a function of the value of gear ratio. The input signal to the valve 39 from block 17 allows the valve to regulate the hydraulic pressure in the cylinders 15, 25, 16, 26, so as to find the optimum effect.

In Fig. 5 pumps 30 and 32 deliver fluid to the cylinders 63, 64 having pistons 65, 66. During normal operation, the return line fluid from these cylinders to drain 38 through outlet openings 67 and 68, along the lines 69 and 70, and valves and controls, respectively, while the values of the pressure in lines 69 and 70 are PAand PBrespectively. To prevent pressure PAand PBwhose values exceed predefined values, provided the exhaust valve 71. In rotary traction BT with toroidal path and with the ability to control torque, which is described, for example, in European patent application EP-IN-0444086, the parts 65 and 66 are in a relationship with the opposite surfaces of the hydraulic piston double-acting, connected to the bearing element of one of the rollers, the orientation of which changes to change the value of the transmitted ratio against the previous figures, the cylinders 63 and 64 in the usual manner communicated respectively with each of the two nodes 2 and 6 of the pulleys of the variator, and in this example of execution of the invention the pressure applied to these two nodes are adjusted in such a way as to create one of these nodes arithmetic sum of the desired power clamps and the force associated with the torque, and the other node only force clamp. Clamp force encourages gutter knock wheel to engage with the belt in sustainable respectively transmitting the pulling force of the contact, and the force associated with the torque balances, in equilibrium, the axial force from sensitive to torque screw or similar mechanism. In this example, the execution of the invention the pressure created by the valves A and B in the cylinders 63 and 64, are only related to torque forces. Clamp force is created separately, the description of this process follows. The fluid injection pumps 30,31 is on line 72 connected to the two input holes of the valve 73, which passes only the more in the moment of pressure PAPBand smaller cuts. The output line 74 passes through the valve 75 downward pressure to the cylinders 76, 77, mounted parallel to and containing the gutter knock wheel clamping force. In the same way the piston 79 applies a clamping force to the other gutter knock the wheel, while the relationship between the pistons 65, 66, 78 and 79 will be explained with reference to Fig. 6.

First of all it should be noted that due to the fact that the cylinders 76 and 77 are installed in parallel, in the direction of travel of the fluid, the valve 75 in these cylinders there is the same pressure. And this, of course, is necessary because the same pulling force must be transmitted to both gutter knock wheel. Secondly, any movement of the piston 78 in one direction will actually be balanced by the movement of the piston 79 in the other direction and Vice versa. Thus virtually all the fluid displaced from the cylinder 76, flows into the cylinder 77, and Vice versa, thus reducing the need for pumps 30 and 31 to adjust the flow of fluid depending on the movement of the two clamping pistons 78 and 79. It should be noted that only one of the two pump powers the cylinders of the clamp at any point in time. All this allows you to use a pump of smaller capacity compared to the case when the cylinder 63 and 64 were required to develop and counter-torque force and the clamping force, as in the previous figures.

If zhidkosti and 77, in this case, the clamping forces generated by the pistons 78 and 79, were in General very large. The valve 75 carries out the reduction of the pressure coefficient, essentially proportional to the value of the instantaneous gear ratio of the CVT, because the force of the clamp must be a function of the traction force on the belt, which in turn is a function of torque and radius of the circle of contact of the belt with gutter knock the wheel, i.e., measures of gear ratio. The pressure, which creates a clamping force is proportional only torque and, therefore, should be modified instantaneous gear ratio to produce the desired clamping forces. To protect the circuit from a dangerous increase in hydraulic pressure in the result of any fault in lines 69 and 70 are installed check valves 71 to prevent the return torque operation and the same valve 80 connected to the valve 73, to protect the operation of the clamp. However, the valve 75 must be of a type that is returned to the fully open position, passing full pump pressure to the cylinders 76 and 77, to ensure continuity of transmission of tractive effort, even for example in the event of a malfunction in ZENITSA Central programmable electronic control unit 17 controls, receiving (through 61,62 and 47) input signals indicating the speed of the vehicle and the engine, the choice of gears and other relevant parameters, and especially from the driver through the pedal 18 accelerator. The placement of the output passages 67 and 68 of the cylinder in raised benches (67a and 68a) formed on the rear walls of the respective cylinders, provides the effect of "end stop" as a security guarantee from wrong actions, in accordance with methods well known in the art. If the piston 65 is outside of its normal course and comes close to the ledge 67a, it increases the output resistance of the pass, and with it the fluid pressure in the cylinder 63, up to the maximum adjustment of the check valve 80, thus increasing the resistance to further movement of the piston beyond its limits.

Fig. 6 shows BT, which applies the hydraulic circuit shown in Fig. 5. Variable contains the node 6 pulley having a gutter knock-wheels 7 and 8, and node 2 pulley having a gutter knock the wheels 3 and 4. The belt 1 transmits motion from one node pulley to another node in the pulley. Gutter knock-wheel fixed on the shaft 9, which in this design is given in DAC that there may be a limited relative axial movement between the shaft and this gutter knock wheel. Gutter knock wheel 8 carries a flange 81 with the formation of an annular space of variable volume, limited by the shaft 9, gutter knock-wheel 8, the flange 81 and a circular plate 82 mounted on the shaft. The compressive pressure acting on the node pulley 6, is formed in this space, which is thus consistent with the specified cylinder 76 in Fig. 5 and which is communicated through the inlet channel 83 and the channel 84 with a decreasing pressure valve 75.

Gutter knock wheel 3 other node 2 pulley connected to the shaft 5 through a spiral slot 22. The second gutter knock wheel 4 node 2 is installed by spline connection 42 on the sleeve extension 41 of the first gutter knock wheel 3, so that two gutter knock the wheels 3, 4 can move in the axial direction, but could not rotate one relative to another. Ball thrust bearings ferrule supported by the flange 44 attached to the shaft 5, restricts the movement of the gutter knock wheel 4 to the right, as shown in Fig. 6. As can be seen in Fig. 4, a spiral slot 22 provides targeted at both ends of the sentient torque link between node 2 pulley and shaft 5: gutter knock the wheels 3, 4 will tend to disperse, when a torque in one direction of rotation, and the second rim, and on its outer rim compacted forms a sliding fit with the flange 88, made gutter knock on the wheel 3. Speed ring 89 smaller fixed gutter knock on the wheel 3 and forms with it a reinforced sliding fit in the position 90. The ring 91 is installed on the shaft 5 and the outer rim of this ring forms a reinforced sliding fit 92 with the inner wall of the ring 89. Between the shaft 5, gutter knock the wheel 3 and the ring 87, 89 and 91 thus limit three annular chambers of variable volume. These cameras are indicated by the positions 77, 63, and 64 in Fig. 6. The camera 77 is communicated through the inlet passage 93 and the channel 84 with a decreasing pressure valve 75 and provides the clamping force. The channel 84 is held in the axial direction of the shaft 5, as well as on the shaft 9. The fluid enters the cylinders 63 and 64 of the pump 30,31, not shown in Fig. 6, the passages 94 and 95, respectively, and then she goes to the passages 67 and 68, as shown also in Fig. 5. In the construction shown in Fig. 6, effectively, when two cylinders 63 and 64 have a common geometric axis and separated by a fixed ring 91, while on the left side surface of the ring 89 is becoming the piston 65 and the left surface of the gutter knock wheel becomes piston 66. The trail is respectively, and so they lie along the axes of the respective inlet passages 94 and 95 to provide the already described effect of limiting the movement end position.

In the embodiment shown in Fig. 6, the shaft 9 may conveniently actuate the pumping device 85, shown in broken lines and containing hydraulic pumps 30 and 31. The last drive sprocket 96 BT to be in mesh with the drive gear 96a mounted on the third shaft 97, the gear 98 mounted on a shaft 9, is engaged with the toothed wheel 98a, just having a shaft 97 a common geometric axis, and the gear 99 mounted on a shaft 5, is engaged with the drive gear 99a, also having a shaft 97 common geometric axis. The operating range of the variator shown in Fig. 6, is extended by providing them with the means of working in two consecutive modes, designated as "low" and "high". If we accept that the shaft 9 rotates at a constant speed, the normal low mode will evolve from a state in which the belt 1 moves from maximum to minimum radius across the node 6 of the pulley (but in the opposite direction across the site 2), and during this brandley rotation to a complete stop (status, known from the prior art as "neutral rate") and then accelerates the rotation in the forward direction as long as the belt does not take a position with a minimum radius at node 6 of the pulley. At this moment simultaneously driven clutch (the construction of which will be described) to disable the low mode and turn on high, when this ratio and the dimensions are so chosen that allow you to achieve what is known in the art as "synchronous change", not including instantaneous changes of the transmitted ratio. In high mode, the belt is pushed back to the maximum radius at node 6 of the pulley and to a minimum at node 2 and the final gear wheel 96 continues to accelerate until its final, extremely fast speed.

To achieve these two modes toothed wheel 98 carries a flange 100 that supports one half discoraging clutch 101, the other half of which carries a bearing planetary gear epicycle gear site. The sun gear 103 of this node is installed on the tubular extension 104 supported gear 99a, and elongation and a gear wheel mounted for rotation wok is raised flange 106, which is mounted on the shaft 97 at position 107 and which also carries an annular gear wheel 108 epicycle site. When operating in low mode clutch 101 and 105 respectively on and off, and epicycle site mixes the input signals from the shaft 9 through a support 102 planetary gear and shaft 5 (via the sun gear 103) for actuating the annular gear wheel and, thus, the shaft 97 and the final drive sprocket 96. At the point of "synchronous change" couplers 101 and 105, respectively, off and off, then a direct connection of the shafts 9 and 97 by means of gear wheels 98,98 and is interrupted, and the shaft 97 is driven directly only from the shaft 5 through the gears 99 and 99a, flange 104, visokoprizemni clutch 105 and flange 106. The piston and the hydraulic cylinders used to actuate the clutch 101, 105, shown under items 110, 111, 112, 113, respectively.

It should be noted that the action sensitive to torque connection between the gutter knock wheel and shaft (for example the position 22 in the example of Fig. 6) in response to a modify command is in effect, the search for more low speed shaft that transfers energy (item 5 on the t is the variator seek to find the value of gear ratio, which reduces the transmission energy. It should be noted, and some other characteristics of the invention, shown in Fig. 6. First of all, two couplers (101, 105) and the epicycle installed on a separate node from nodes 6 and 2 shaft (97). This is done in order to get the transmission with small distances between the axes, suitable for installation in vehicles with a transverse engine installation. Secondly, in principle does not matter which of the nodes 2.6 pulley will be attached sensitive to torque relationship (22). Thirdly, the advantage of installing sensitive to torque connection 22 and all associated hydraulic passages and channels in the shaft 5 is that both ends of this shaft are potentially unloaded, with access to hydraulic connections easier than on the shaft 9 whose one end is connected to the primary engine 50.

In the example shown in Fig. 7 and Fig. 8, the belt 1 passes traction between node 2 pulley mounted on the shaft 5, and node 6 pulley mounted on the shaft 9. In this example, the shaft 5 is connected with the primary motor 50, and the shaft 9 but of the present invention, to the final output gear wheel 96 BT, in which one of the components is variable. Node 2 pulley contains gutter knock wheel 4, with a spiral ball race 22 is installed between this gutter knock-wheel and the shaft 5, and thus this gutter knock the wheel and shaft capable of limited relative movement, containing both rotational and axial component. Gutter knock wheel 4 is also installed with the ability to move as a piston within the hydraulic cylinder 15 formed by a housing mounted on the shaft 5. Node 2 pulley also includes a second gutter knock wheel 3 that is installed at position 42 with the spline on the sleeve 41, is made on the first gutter knock the wheel 4. Item 42 allows relative axial movement between the parts 3 and 41, but it is sealed to prevent leakage of fluid through the slot. Ball cage 43, mounted on the radial flange 44 attached to the shaft 5, allows gutter knock the wheel 3 to rotate around the shaft, however, prevents him from relative motion from right to left. Thus, the example shown in Fig. 7 in General, similar to the examples shown in the previous figures. However, gutter knock and 42, 41, 120, 121, and 119 interact to define the boundaries of the second hydraulic cylinder 122.

Design another node 6 pulley on the output shaft 9 is the same, but the elements are in the reverse direction, from left to right, and corresponding elements are indicated by the same reference numbers, but with the indices ', i.e., the first and second gutter knock-wheel 4' and 3'. The direction of the turns of ball tracks 22 and 22' are designed so that when energy is transferred from the shaft 5 to the shaft 9, the direction of turns of the spiral ball track 22 to strive to create a force tending to dissolve or, so to speak, to move in the axial direction at different sides of the gutter knock-wheel on the shaft 5, the direction of turns of the spiral ball track 22' seeks to create a force tending to reduce gutter knock-wheel on the shaft 5. If the energy moves in the opposite direction, the direction of action of force is also reversed. Straight slots 42 and 42' creates the possibility of such a movement, but prevents relative rotational movement between the two gutter knock the wheels.

In the control circuit shown in Fig. 8 and 11, is provided by the pumps 30 and 31, and the Central unit 17 control valves a and b maintains erpendicular the load on the belt (or chain) was sufficient to prevent slippage, but not excessive, and thus, these axial forces that are dependent on torque, ball screws were balanced algebraically. Perpendicular load is initially a coefficient of friction between the belt and gutter knock wheel and the sum of the input and output torques. The last value can be expressed as a function of torque, the value of which is under control, which is thus known, and the speed ratio of the variator (which can easily be measured). Thus the optimal perpendicular load (compressive strength) can be maintained over the operating range.

If gutter knock wheel, for any reason, will be outside the normal operating range, in this case work "hydraulic brakes", well known in the art. In the same way, as shown in Fig.5, the outlet line 69, 70, leaving the two cylinders 15 and 15', are installed in the ledges 67a, 68a, which are coaxial parts of the bottoms, where the inlet line are cylinders of pumps 30, 31, respectively. As gutter knock the wheel closer to one of the ledges 67a 68a or before it is actually referred to that ledge, it closes vypusk way preventing further advancement of the gutter knock wheel by increasing the fluid pressure in the cylinder above the values which it would have if it were determined only by the corresponding control valves A or B.

As is clearly shown in Fig.8 separate hydraulic cylinders 15, 122; 15', 122' of the example described in Fig. 7 and 8, allow each source (30 and 31) of energy to be communicated directly with the "big" or "dependent torque cylinder (15 and 15') of one node of the pulley and with the "small" or "clamping" of the cylinder (122' and 122) of the other node. It should also be noted that there is still desirable that the perpendicular load on the strap would be high enough to prevent proculture, especially when the hydraulic stopper increases the pressure to counteract the overload torque of the variator. To ensure this effect, the angles of the helix ball screws must be above a certain value set by the parameters of the variator, in particular used the coefficient of friction and, as in the case shown in Fig. 8, square, large and small pistons.

In embodiments of the invention described in Fig. 9 and 10, reference numbers that have already been used in Fig. 7 continue to designate similar elements. Nevertheless, in Fig. 9 instead of tol is now the second gutter knock wheel (3, 3') at each node as installed (as well as for node 2 in Fig. 2) on the same ball track (21, 21'), with ball tracks each node have opposite directions. Moreover, the cylinders shown in Fig. 7, is not provided and two gutter knock the wheels of each node on a path identical, with gutter knock the wheels 3 and 3' are acting as pistons within such enclosures that are installed on the shafts 5 and 9, with the result cylinders 15 and 125, 15' and 125' are hydraulically communicated along the lines indicated by the positions 126 and 126'. In the variator shown in Fig.10, the similarity with the variator shown in Fig. 7, even closer, the only significant difference lies in the fact that it is not provided by the cylinders 122 and 122'. Gutter knock the wheels 3 and 3' each node thus has a simpler form, but still move along the slots 42 and 42' mounted on the sleeves 41, 41', which are driven gutter knock-wheels 4 and 4', with ball tracks 43 and 43' to prevent the Commission of gutter knock wheels axial movement in the opposite direction. In the example embodiment of the invention shown in Fig. 10, thus there is only one means by which the axial hydraulic force is applied to questline of the invention, it is shown in Fig. 9 and 10, Fig. 11 shows the main elements of the hydraulic circuit containing, in the same way as in Fig. 7, the Central programmed control block 17, two pumps 30 and 31, and two valves A and B control. The pump 30 and valve And communicated with the cylinder 15 (and, as shown in Fig. 9, the cylinder 125 through connection 126) one node of the pulley and the pump 31 and a valve In communication with the cylinder 15' (and, as shown in Fig.9, the cylinder 125' through connection 126') of another node pulley. Although for simplicity in Fig. 9 and 10 are not shown, the cylinders 15 and 15', as shown in Fig. 11, executed with speed stoppers 67a and 68a to create the effect of "end stop", as it was already explained with reference to Fig.8.

Fig. 12 shows an example implementation of the invention according to the second aspect of the present invention, in which the variable-speed drive with adjustable torque, basically the same type as that shown in Fig. 6, simply and economically adapted in such a way as to create a parallel installation of more than one combination of nodes of pulleys and a belt, for a total intake and exhaust shafts, and thus to equalize the torque on all of the individual belts, but to increase the total torque of the PTO is t to pass. Although Fig. 6 shows a variator with two straps, it is clear that this principle can also be applied to the variator, which has more than two belts. As will become clear from the following description in the variator shown in Fig. 12, methods of installation sites of the pulleys on the intake and exhaust shafts dissimilar: mounting of ball tracks recorded on the exhaust shaft. Thus the symmetry that exists in Fig. 5, not shown, and, therefore, the hydraulic circuit comparable to that shown in Fig. 8, can not be used.

In Fig. 12 shaft 9, driven in the same manner as in Fig. 6, the primary motor 50 drives two belt 1 by means of two nodes 6 pulleys. Prom gutter knock wheel 7 these two nodes are fixed on the shaft 9, while the inlet gutter knock the wheels 8 are in engagement with the shaft 24 by means of rectilinear slots 24 and, thus, capable of limited axial movement. The cylinder 76 with variable volume is set between the gutter knock wheel 8 and the shaft 9, while it is isolated with the aid of annular seals 127.

Belts 1 are in engagement with nodes 2 pulley on the other shaft 5, which is connected, as before, to the final transfer 9ץ tracks 22 and tolkovanie the extensions 41, have internal gutter knock wheel 3 through straight splines 42. Internal gutter knock wheel 3 secured against mutual rapprochement through ball or roller tracks 43, mounted on the opposite surfaces of the flange 44, mounted on the shaft 5. Each of the outlet shaft 4 fixed to the profiled ring 89, which forms a compacted, sliding fit with the shaft 5 at position 90. Another profiled ring 87, which forms with the shaft 5 from its internal reference surface fixed and reinforced landing, compacted forms, but sliding fit with the sides of its outer bearing surface, which is opposite the outer flange 88 of the rings 89. Sealed hydraulic cylinders 77 variable volume with an inlet passage 93 is thus established between the rings 89 and 87. The annular element 91 on the inner radius of the forms with the shaft 5 reinforced landing, with the outer radius forms a reinforced landing opposite the inner flange 129 of the rings 89. Thus, the blocks and the adjacent elements form a sealed hydraulic cylinders 63 and 64, 64a and 63a mutually changing volume. The cylinders 63 and 63a of imethod 95, moreover, the elements 91 is formed with outlet openings 68 and 67, communicating with the cylinders 64 and 63a, respectively.

The corresponding connected hydraulic circuit is essentially shown in Fig. 5. Through channels (not shown) formed in the shaft 5 of the pump 30 delivers fluid to the cylinder 63 (63a and through the inlet 94, the pump 31 delivers fluid to the cylinder 64 (64a and through the inlet 95, and output passages 67, 68 from the cylinder is connected to the drain 38 through valves A, B control, respectively. In the same way as shown in Fig. 8 valves a and b are configured Central programmable electronic control unit 17 controls the BT so that runtestcase forces created by the pressure in the cylinders 64 and 64a, equal and each of them is "dependent on the torque component of the overall axial course-load force applied to each of the nodes 2 of the pulleys. Through valve 73 (which selects for transmission the higher of the two pressures pressure) and the third controlled valve 75 one or the other of the pumps 30 and 31 also communicates with the cylinders 76 and 77 to pressure with a corresponding clamp force between the belt and gutter knock wheel on node 6 pulleys, and the pressure comny among themselves, and they are provided with the same pressure in the cylinders is equal to the area; "regulators torque the cylinders 63 and 64, 64a and 63a do not create your own efforts on these shafts, since the pressure forces are balanced from a spiral ball tracks 22.

It should be noted that the input shaft 9 must contain only one fluid channel for supplying fluid from the valve 75 in the cylinder 76 through the inlet 83, while the input shaft 5 must be much larger number of hydraulic channels for fluid supply to many shows passages and channels. In the General case this is advantageous, since both ends of the shaft 5 are potentially free, giving you the ability to more easily provide hydraulic communication than in the case of shaft 9 whose one end is connected with the primary motor 50.

1. Continuously variable transmission band type - gutter knock a wheel containing the control unit (17), controlled by the driver or other operator (by means of the control element 18), the change gear ratio of the component containing at least one strip (1) in drive contact with two nodes (2, 6) pulleys having parallel, but at a distance who meet the shaft (5, 9) and installed it on two gutter knock-wheels (3, 4, 7, 8) with the possibility of changing the distance between the axes of the gutter knock of wheels that are sensitive to torque the connection (21, 22) between at least one node of the pulley and its shaft, and means for creating between them an axial force which is a function of the magnitude and direction of torque, which is transmitted by a node pulley, and load tools(30, 15, 25, 36, 39; 31, 16, 26, 37, 39), acting on the nodes of the pulleys for impact load forces on the gutter knock wheel, characterized in that sensitive to torque the connection (21, 22) on one of the shafts (5, 9) contains shareavenue coupling between him and gutter knock wheel(3, 4, 7, 8).

2. Transmission under item 1, characterized in that shareavenue grip extends axially and circumferentially.

3. Transmission under item 2, characterized in that shareavenue grip has a generally spiral path.

4. Transmission under item 1, characterized in that the two gutter knock-wheels (3, 4, 7, 8) node (2, 6) pulley contain terminal arresters (36, 29) to limit axial movement of one of the gutter knock of wheels relative to another node (2, 6) pulley.

5. Transmission under item 1, wherein in the opposite direction.

6. Transmission under item 1, characterized in that it contains hydraulic load funds(15, 16, 25, 26), creating end load.

7. Transmission under item 1, characterized in that it contains a valve (34), providing an increase or decrease of the limit load, depending on the axial position of the gutter knock-wheels on the shafts.

8. Transmission under item 1, characterized in that it contains limit stopper (29) to prevent slippage of the strip with the inner radii of the wheels in the gutter knock if gutter knock wheel will go in the axial direction over a long distance.

9. Transmission under item 8, characterized in that the limit stop (29) contains between gutter knock-wheels (3, 4, 7, 8) ring mounted rotatably on the shaft (5, 9) site pulley (2, 6).

10. Transmission under item 1, characterized in that the strip is a strip of belt type.

11. Transmission under item 1, characterized in that the strip is a stretch of the chain type.

12. Transmission under item 1, characterized in that it has at least two operating modes, at least one of which energy circulates in a closed cycle through the variator.

13. Trance side load forces on at least two nodes of the pulleys (2, 6) is reported so that the passage between them of the fluid flow, they are under equal pressure.

14. Transmission under item 1, characterized in that it contains the primary motor (50) connected to one of the axes (10) of the variator, and in which any of the sensitive torque relations is closed on the second axis (11) of the variator.

15. Transmission by p. 14, characterized in that the hydraulic loading means (15, 16) are mounted on each axle and the fact that the transmission has channels for the movement of the fluid interacting with a load means (15, 16) formed in the shafts (5, 9) on these axes.

16. Transmission under item 12, characterized in that it contains a driven shaft (56), gearing (51) and the sleeve (52) to support the operation of the transmission in more than one mode, while the slave shaft is displaced relative to one of the axes (10, 11) of rotation of the variator, and gearing (51) and a sleeve (52) is installed coaxially with the driven shaft.

17. Transmission under item 1, characterized in that it contains two or more combinations of devices stripe - site pulley(1, 3, 4, 7, 8) between the shafts (5, 9) and means counterbalancing torque.

18. Transmission under item 1, characterized in that it behold one node (2), associated with the first axis (10) of the variator and the second component to at least one node (6) associated with the second axis (11) of the variator, and Vice versa, for the second energy source (31).

Priority points:

20.12.93 on PP. 1 - 13, 16 and 18;

02.06.94 on PP.14 and 15;

26.08.94 on p. 17.

 

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Hydraulic vehicle // 2246061

FIELD: transport mechanical engineering.

SUBSTANCE: hydraulic vehicle comprises at lest one hydraulic pump (10) which is actuated by engine, one hydraulic motor for actuating wheel (31), hydraulic circuit (50) for connecting hydraulic pump (10) with hydraulic motor (30), and valve (60) for control of flow. The input shaft of hydraulic pump (10) is directly connected with the crankshaft of the engine. Valve (60) returns oil, which is supplied from hydraulic pump (10) to valve (60), to hydraulic pump (10) in the first position. In the second position, valve (60) supplies oil, which is supplied from hydraulic pump (10) to the valve, to hydraulic motor (30). In the third position, valve (60) supplies oil, which is supplied from hydraulic motor (10) to the valve, to the drain branch pipe of hydraulic motor (3).

EFFECT: simplified design and reduced weight.

1 cl, 5 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: mechanical engineering.

SUBSTANCE: method comprises changing transformation ratio by changing viscosity of fluid in the working space by changing voltage. The working space is defined by the spaces of blade rims of the reactor wheels. The voltage is supplied to the windings which generate magnetic field whose vector of magnetic induction generates magnetic viscosity in the fluid. The fluid is made of a magnetic liquid.

EFFECT: simplified method of control.

1 dwg

FIELD: transport mechanical engineering.

SUBSTANCE: device comprises electric means for measuring working volume of pumps and hydraulic motors and pickup (60) for measuring the speed of rotation of the shaft of the pump station. The electric circuits are provided with threshold control members (67) and (80) interconnected between pickup (6) and the electric means. Between threshold control members (67) and (80) and electric means for changing working volume of pumps (67) and (80) and hydraulic motors (13), (14), (17), and (18) of the drive of end wheels are variable resistors (77), (78), (86), and (87) that are controlled by pickups (89) and (89) of pressure difference in hydraulic circuits of the drive of the intermediate wheels and the drive of each pair of end wheels.

EFFECT: enhanced reliability and prolonged service life.

3 cl, 4 dwg

FIELD: transport mechanical engineering.

SUBSTANCE: system comprises electric means for changing working volumes of pumps and hydraulic motors and pickup (60) of the speed of rotation of the shaft of the pumping station. The electric circuit has variable resistor (61) and switch (62) interconnected between pickup (60) and electric means (40-45) and controlled by pedal (63) for supplying fuel to the engine, resistor (64) connected in parallel to the switch, and threshold control unit (67). The electric circuit also has threshold control unit (80) interconnected between the pickup and electric means (54-59), with the threshold being controlled by pedal (63).

EFFECT: improved quality of control.

3 cl, 4 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 mechanical engineering.

SUBSTANCE: automobile comprises driving engine, device for transmitting torque made of the clutch with actuating device, gear box with actuating device, and control device. The control device acts on the device for transmitting torque and gear box. The action on the gear box is composed of the first component of motion (choice component) and second component of motion (shift component). The actuating device of the gear box has first and second drives. One motion in the gear box is rotation, and another one is translational motion. The kinematical section of the transmission for converting the motion of one of the drives into the motion of choice comprises transmitting link made of the worm with the worm wheel, carrier for converting rotation into the axial motion, and member for converting axial motion into rotation of choice. The versions of kinematical sections for converting the motion of one of the drives into the choice motion are proposed.

EFFECT: simplified structure and reduced cost.

33 cl, 30 dwg

FIELD: transport mechanical engineering.

SUBSTANCE: automobile comprises driving engine, device for transmitting torque made of a clutch with actuating device, gear box with actuating device, and control device. The device for transmitting torque and/or gear box is set in operation automatically by means of control device or input of data in the control device. The gear box is actuated by the first component of motion (choice component) and the second component of motion (shift component). The actuating device of the gear box has first and second drives for providing the first and second motions. In the gear box, one motion is translational and the other one is rotational. The sectional member for transmitting motion to the shaft of the control of gear shift has at least one axial groove for transmitting rotation and at least one ring groove or segment of the ring groove for transmitting the axial motion.

EFFECT: simplified structure, enhanced convenience, and reduced cost.

31 cl, 15 dwg

FIELD: gearing.

SUBSTANCE: method comprises changing the state of blocking friction clutch through the period of its pulse engaging-disengaging.

EFFECT: enhanced efficiency.

4 dwg

Hydraulic drive // 2278310

FIELD: positive-displacement transmissions of tracked vehicle turn mechanisms.

SUBSTANCE: proposed drive has pump and hydraulic motor and auxiliary pump whose delivery line is brought to return line and to replenishing valves; hydraulic motor is adjustable; delivery line of auxiliary pump is connected with control cavity of spring-loaded piston which is kinematically linked with adjusting member of adjustable hydraulic motor.

EFFECT: enhanced reliability.

3 cl, 1 dwg

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