JP2014132200A5 - - Google Patents

Description

Variable transmission

  The present invention relates to a variable transmission for use in general industrial machines, vehicles, electric motors, and the like, which distinguishes and supplies elastic force and pressure to pulleys to stabilize frictional force and achieve high-bandwidth high-efficiency transmission.

The operation of the constant horsepower type belt continuously variable transmission is under development in US Pat. Nos. 4,973,288 and 5,269,726, etc., but it does not lead to a satisfactory product. The idea is to pressurize the input / output vehicle simultaneously with hydraulic pressure in the latter and screw hoisting in the former. However, these ideas have decisive and significant functional or principle defects. The output horsepower P [W] transmitted to the load by the normal output vehicle is determined by a transmission relational expression P = 1.027 × N × T between the rotational speed N [rpm] and the torque T [Kgm]. The rotation speed is determined by the contact position between the belt pulleys, that is, the radius ratio, whereas the torque is determined by the contact friction pressure and the contact area between the two. This means that the rotational speed is determined only by the positioning control of the belt in the pulley, whereas the shaft torque is determined only by the area of the pulley and the variable pressure control of the constant friction pressure. Therefore, the above transmission relational expression itself indicates that the variable speed positioning control and the frictional pressure variable pressurization control should be discriminated and applied to each pulley in order to ensure the desired rotation speed and torque in the continuously variable transmission. Show. However, the above-mentioned US patent idea has no guarantee that the proper belt position is always maintained even if the positioning function of the pressurizing force synchronized with the input / output vehicle is provided, and there is no torque guarantee function for always applying a predetermined friction force to both the vehicles. This indicates that the above-mentioned patent ideas cannot secure and maintain an appropriate rotation speed and torque, and that constant horsepower transmission is impossible in principle.

On the other hand, the applicant of the present application proposed differentiation of each functional role of variable pressure control and variable diameter positioning control for each of two input / output pulleys in European Patent Application EP0931960A2. However, there are still some outstanding issues. The first is the instability of the frictional force between the belt and pulley, and the second is the problem of the accompanying deterioration in transmission efficiency. The former makes the low speed transmission of the tension belt impossible. This is because the friction coefficient of the friction transmission surface becomes unstable when the contact radius or the area is increased in the measure for securing the friction force by directly applying external pressure to the pulley, resulting in excessive friction force. In the latter case, the transmission efficiency is maximum even in the push-type belt near the speed ratio ε = 1, but in other speed ratio areas, the contact area of both pulleys and the frictional force are not balanced and deteriorated. That is, it is assumed that the brake heat generation due to the belt biting due to excessive friction force on the contact area increase side in both pulleys and the slip heat generation due to insufficient friction force on the contact area decrease side cause the simultaneous occurrence of the control form. Countermeasures are desired.

US Pat. No. 4,973,288 US Pat. No. 5,269,726 European Patent Application EP0931960A

A common problem to be solved by the present invention is that the conventional output pressurization device variably operates the frictional pressure between the belt and pulley by supplying elastic force to the output vehicle to control the output torque, but the input vehicle has no input torque management. It is an object of the present invention to provide a variable transmission capable of managing and applying the input torque of the input vehicle with high accuracy, since it has caused abnormal transmission noise, vibration, and deterioration of transmission efficiency.

The first problem to be solved by the present invention is that if the input vehicle controls the speed ratio and the torque by the output vehicle, the input vehicle cannot be given any torque by an external command, and abnormal noise and vibration are caused by disturbance in the applied pressure of both vehicles. The idea is to provide independent input torque control by individually applying a huge elastic force to the input vehicle because the efficiency also deteriorates.

The second problem to be solved by the present invention is that when the adjusting device transmits various mechanical commands from a plurality of pressurizing devices to a single belt, signal interference between the pressurizing devices due to the flow of signals from a plurality of operation points. This is the idea of always stably operating the speed ratio, input and output torque, etc. by preventing the interference.

The third problem to be solved by the present invention is that the elastic force can be selected as an arbitrary value between the excess and deficiency of the friction pressure as compared with the applied pressure, and the variable pressure of the elastic force can be applied depending on the friction pressure and the contact area. Is a high-accuracy input torque control concept that uses both vibration absorption and automatic belt centering.

The fourth problem to be solved by the present invention is that the simultaneous supply of pressure to both the input and output vehicles is impossible to transmit, but the simultaneous supply of elastic force has the advantage of promoting stable transmission. However, it is a torque control philosophy that allows arbitrary torque to be selectively applied and that ensures a highly efficient transmission characteristic at all times.

The common solving means of the present invention is that the input torque of the input vehicle itself is arbitrarily managed by an external command from a controller or the like, so that the speed ratio control is performed by the output vehicle and the constant-horsepower transmission or constant-torque transmission is used. Another object is to provide a variable transmission having an input torque applying structure for output torque control by supplying elastic force to achieve high efficiency transmission.

The first solving means of the present invention is that the compression device supplies an elastic force obtained by serially compressing the elastic device to variably operate the belt input inter-vehicle friction pressure to perform input torque control on the input vehicle, and the adjustment device inputs the input torque command. Is applied to the input vehicle in an open loop or closed loop so that the input torque is separately applied.

According to the second solving means of the present invention, each of the compression devices of a plurality of pressurizing devices is connected to a sliding device with an urging device that prevents the belt friction pressure from flowing out to the other urging device at the time of command supply by one of the urging devices. This is a control configuration in which the inversion and outflow of commands are mutually prevented to prevent mutual interference of signals among a plurality of others.

According to the third solving means of the present invention, an input torque command or torque value is set in advance in the storage device of the adjusting device, and an input torque command is given to the input pressurizing device from this value, and the friction of the elastic force command is always applied to the belt. By applying the pressure, the automatic belt alignment function and the input torque to the input vehicle are applied.

According to the fourth solution of the present invention, since the transmission should originally match the input power and the output power, the input torque and the output torque are differentiated at a ratio that the product of the speed ratio and the input torque becomes the output torque, and the two commands are further divided. In this configuration, both torques are controlled to be open or closed by adding compensation for correcting the deterioration of transmission efficiency.

  Up to now, the variable transmission has controlled the output torque by variably operating the friction pressure between the belt output cars with a huge elastic force on the output car, but the input car has no control of the input torque, so the input torque control is naturally not possible. This was possible, and it was forced to drive in an imbalanced state of the pressure constantly applied between the input vehicle and the output vehicle. The present invention has the concept of giving input torque control independent of the input vehicle by variably operating the friction pressure between the belt input vehicles by supplying a huge elastic force obtained by the compression device compressing the elastic device in series to the input vehicle. Established. As a result, the increase and decrease of the shaft torque of the input car can be controlled by an external command. As a way to eliminate the imbalance of the applied pressure was opened, extreme stability in transmission was established, and at the same time, stability in control operation was established. As a result, the following various applications and practical utility are produced.

  First, a new transmission control form called a first transmission form A that establishes torque control with an input vehicle and speed ratio control with an output vehicle has been established. Similar to the existing second transmission form B that performs speed ratio control on the input car and torque control on the output car, the first transmission form A alone is sufficient for the constant horsepower type transmission and the constant torque type transmission. As a motive, it can be put into practical operation only by a variable operation of the adjusting device. Further, as shown in the first embodiment and FIG. 7, when the first transmission form A and the second transmission form B are combined, only both high efficiency regions are selected and extracted, and the high efficiency bands are connected to each other. Thus, there is an advantage that a remarkable broadband high-efficiency transmission can be realized.

  Secondly, as a result of the establishment of the input torque control concept for the input vehicle according to the present invention, both the input vehicle and the output vehicle can be individually but simultaneously supplied with a huge elastic force. There exists an advantage which can improve the fault which A or the 2nd transmission form B has significantly. In other words, if a huge elastic force continues to be supplied to only one vehicle, the imbalanced state of the applied pressure between the input and output vehicles becomes normal, causing abnormal vibrations and abnormal noise, and the transmission form becomes unstable and the transmission efficiency deteriorates at the same time. Shorten the life of the motive itself. However, when a giant elastic force is applied to both vehicles, the pressure imbalance is corrected and the pressure is dispersed on the belt, so that the transmission itself has the advantage of significantly increasing the stability and the advantage of extending the life.

  Thirdly, the transmission originally shifts the input power P1 (= N1 × T1) to the output power P0 (= N0 × T0), so both powers are ideally P1 = P0, and the speed ratio ε = N1 / N0. It is well known to those skilled in the art that the relation between the input and output torques is naturally T0 = ε × T1. The fact that the present invention has established the input torque control concept for input vehicles is that when it is necessary to increase or decrease the torque load as a transmission load, naturally the increase or decrease of the transmission torque between the input and output vehicles according to this input / output torque relationship is simultaneously performed on both vehicles. Since it indicates that it is only necessary to perform the pressurizing operation, the high-accuracy management of the input torque in addition to the output torque itself means that a new torque control concept that is inexpensive and extremely effective is established.

  Fourthly, the problem of deterioration of transmission efficiency in the low speed range or the high speed range, which is a fatal problem of the variable transmission, is mainly caused by slip heat generation or brake heat generation. Because the elastic force supply can be increased or decreased individually on the input vehicle side and the output vehicle side, the low speed range is corrected by applying a compensation value associated with the cause of the specific deterioration in efficiency. It ’s fine. In addition, since the individual operation of the compensation value can be performed in the same manner in the high speed region, there is an advantage that the usable practical band can be greatly expanded as a result.

  Fifth, in the present invention, if there is a request for change in one or both of the speed ratio and the torque, the variable transmission is characterized in that it operates in response to this transmission load. Therefore, not only the increase / decrease of the speed ratio, but also when the variable transmission of the present invention is applied to a vehicle, for example, it is possible to apply torque according to the torque load such as load change, so that it is always necessary load when traveling As a result, the required fuel application is guaranteed, so that fuel efficiency is remarkably improved and a high-efficiency transmission with low cost and low operating cost is realized. Therefore, there is an advantage that not only the efficiency of the variable transmission is improved, but also the industrial value of the load device itself such as a vehicle to which the variable transmission is applied is extremely increased.

1 is a cross-sectional view of the overall configuration of a variable transmission according to a first embodiment of the present invention. A cross-sectional view of the input vehicle and input controller of the first embodiment, A cross-sectional view of the output vehicle and output controller of the first embodiment, The block diagram of the drive source and adjusting device for each operating device of the first embodiment, A cross-sectional view of a pressure detector applied to the output operation device of the first embodiment, FIG. 6A shows the speed ratio versus contact radius / friction force characteristics of the first embodiment, FIG. 6B shows the operation characteristics on the input car side, and FIG. The speed ratio versus transmission efficiency characteristic diagram of the first embodiment is shown respectively. 2 is a sectional view of the overall configuration of a variable transmission according to a second embodiment of the present invention; Sectional drawing of the input vehicle and input operation device of the said 2nd Example is each shown. FIG. 3 is a sectional view of an input vehicle and an input operation unit of a variable transmission according to a third embodiment of the present invention; Sectional drawing of the output vehicle and output operation device of the said 3rd Example is each shown.

The idea of the present invention is not limited to the wet type in which both the transmission gear and the transmission control device are housed in the oil layer, but may be a dry type in which both are housed in the air, or may be individually housed. As a transmission form, the present invention is particularly effective for a constant horsepower transmission type variable transmission, but it may be applied to a constant torque transmission type variable transmission by operating only the speed ratio control alone. As the control mode, the operation device of the speed change control device has disclosed the individual pressurization method composed of the first and second pressurization devices and the composite pressurization method by the composite device in distinguishing the applied pressure and the elastic force. Both of the operating devices may be of a pressurizing method using an individual pressurizing device, or the input side may be a pressurizing method using a composite pressurizing device, and the output side may be of various pressurizing methods such as using an individual pressurizing device. A pressure detector may be provided on the input side to detect the friction pressure. At this time, the preliminary pressure shown in FIG. The pressurizing device, composite device, compression device, elastic device, or contact device that presses the pulley are all shown as non-rotating arrangements, but they may be used in a rotating state, and the mounting position is not limited to the periphery of the pulley. You may arrange | position in arbitrary positions with the pressure transmission device of a hydraulic jack or a lever.

  In the example of switching the pressurizing force and elastic force of the operating device, an example of switching preferentially at the speed ratio ε = 1 has been shown, but switching may be performed at an arbitrary speed ratio, and the reference of the switching operation is based on the speed ratio. Alternatively, the output speed or output torque may be switched to a priority standard. In this case, it is desirable that both the output rotational speed and the torque be safely switched to bumpless without instantaneous impact. Further, when the input power is changed in the output rotational speed, such as an internal combustion engine or a DC motor, only the output torque is controlled according to the rotational speed while the speed ratio control of the variable transmission is kept at a certain constant speed ratio. A torque converter may be provided by performing variable torque control by a single operation. Since the pulley for the standard vehicle function performs the rotational speed control and that for the following vehicle function performs the torque control, the control command that is also the speed ratio and torque command supplied from the adjusting device when the operation device is switched to each function. It is obvious that switching should be performed at the same time, and it is natural that the command should be controlled by discriminating and discriminating between the rotation speed command for speed increase / deceleration and the torque command for pressure increase / reduction. Accordingly, the compensated rotational speed command should be identified and supplied for the belt pulley friction surface degradation, etc., and the compensated torque command should be identified for the elastic body degradation and friction pressure reduction.

  Next, various changes can be made to the substitution of each device, parts, etc., and the common use. The pressurizing device may be arranged in any order as long as the compression device is connected in series with the elastic device and / or the contact device. The compression device may be a hydraulic sliding device such as another inclined sliding device or a hydraulic jack as long as the pressing position can be stably held even after the supply of the command signal is stopped. The elastic device is not limited to a disc spring, and may be any other type. The contact device may have other forms, for example, each elastic body itself may be provided with a contact tool and arranged in series. Each of the pressurizing means, such as a sliding tool, a sliding body, and a sliding material, may be shared and shared with each other, or may be replaced with other members such as a main body, a vehicle, and a pressure transmission device. The pressure transmission device and the first and second detectors may be of any other type. For example, the pressure transmission device may transmit the inside of the hollow shaft core of the pulley rotation shaft. The control motors of the first and input and output second drive sources are individually arranged for the input and output side pressurizing devices. However, the drive source includes a switch such as a known transmitter or a gear synchronous fitting device. The motor type may be an AC or a step motor. In the second pressurizing device that pressurizes the movable wheel and the elastic body at the same time, it is proportional or inversely proportional between the operation amount of the second compression device and the relative distance of the disc wheel, and inversely proportional or proportional between the elastic body and the elastic force. I just need it. Each operation device may have each compression device individually or in common with the first and second pressure devices.

In a pressurizing device having the motor and the compression device, long-term high-accuracy positioning and friction pressure supply control are required to withstand high pulley pressure. Therefore, it is necessary to positively eliminate error signal factors for each control command such as a self-lock function, that is, a reverse rotation prevention function and a motor overrun prevention function, in each pressurization system of the operating device. Therefore, a metal surface contact friction means such as a trapezoidal screw or a one-way transmission device such as a worm transmission device should be used, or a stepping motor having a clutch, a brake function or a reverse rotation prevention function should be applied. Note sliding amount of the compression device, the output wheel movement amount l ₀ in the pulley moving amount 1p only I but total movement joined by the input vehicle movement amount l ₁ pulley movement amount 1p and elastic compression amount 1s of the follower vehicle function of the reference vehicle features The amount is 1p + 1s. Therefore, since the operation amount and the operation direction are different between the rotational speed command and the torque command, in the case of an inclined sliding device such as a screw or a cam, the pitch, that is, the gradient or the inclination, the rotational direction, the thread groove processing such as the right screw and the left screw, etc. Known elements such as the direction and the speed ratio of the gear transmission may be selected according to the design.

  Next, various control modes of the adjusting device 90 are conceivable, and when the output rotational speed N0 or the output torque T0 does not require accuracy, a single control command may be supplied as an initial operation amount. When high-speed response of variable speed and variable torque operation is prioritized by maintaining high accuracy and stable transmission, the belt circumference or elastic body deterioration error is periodically sensed and the rotation speed or torque according to the amount of deterioration. Each of the commands is given a compensation amount calculated by the CPU so that it becomes a reference value determined in advance in the memory, given to the input and output operating device, and given an operation value of the rotation speed, friction pressure or torque value, and open loop Substantial servo control may be used. When further precise management of torque and speed ratio is required, negative feedback control is performed by substantially comparing the detected values of the input / output vehicle speed, friction pressure or torque value with a reference value set in advance in memory. Is supplied to the input or output side actuators to achieve a long-term operation with extremely high efficiency even for high-load transmission by closed-loop servo operation.

  1 to 6, a variable transmission 10 for a vehicle includes a transmission 10A composed of a belt 3 provided between an input vehicle 1 and an output vehicle 2, and an input operation unit 9 and an output operation on the same plane side. 4 is configured with a shift control device 10B that adjusts the adjusting device 8 with an adjusting device 90 shown in FIG. In this example, the input operating device 9 is configured by using an individual pressurizing device 50 including input first and second input pressurizing devices 11 and 51, and the output operating device 8 is configured by sharing the output first and second output pressurizing devices. The combined pressure device 40 is composed of the output common pressure device 21 and is energized by the drive source 60 shown in FIG. The input first, input second and output common pressure devices 11, 51 and 21 have input first, second input and output common compression devices 14, 54 and 24, respectively, and an input elastic device 31 and an input contact device. 35 and the output composite apparatus 20 are respectively pressurized. The input operation device 9 is composed of input first and second input pressurization devices 11 and 51 for the input wheel 1, and the output operation device 8 is connected to the output wheel 2 for the output common pressure device 21 according to the individual command of the adjusting device 90. It operates in response to a single command and has the ability to discriminate and supply elastic force and pressure, respectively. Since there are almost equivalent functional parts on the input / output side, in this specification, when each part name needs to be distinguished from "input", "output" or "first", "second" , It may be omitted when it is understood by the description and drawings before and after.

  The transmission 10A includes variable-diameter pulleys 1 and 2 that are arranged so that the movable wheels 1a and 2a and the fixed wheels 1b and 2b face each other, and the former is slidable in the axial direction with respect to the latter through keys. The input shaft 1c and the output shaft 2c are arranged in opposite directions. The pulleys 1 and 2 are respectively supported by a pair of bearings 7 and 6 and rotate. Further, the pulley 10 is input between the main body 10 and the movable wheels 1a and 2a while separating the rotational force between the pair of bearings 5 and 4, respectively. The pulley movable wheel is pressurized by the first, second input and common pressure devices 11, 51 and 21, respectively. The main body 10 is assembled so that a first main body 10a that houses other transmission devices such as a vehicle and a second main body 10b that houses the variable transmission 10 are separable.

  As the V-belt 3, two types of belts, that is, a tension type in which the input wheel pulls the output wheel and a push-in type in which the input wheel is pushed and transmitted are well known, and both can be applied to the present invention. The description of the structure is omitted. For example, the former is described in U.S. Pat. No. 4,493,681, and the latter is only described in U.S. Pat. No. 3,949,621. In addition, since the idea of this embodiment achieves stable transmission without taking compensation measures for unstable friction force such as a cam mechanism even with a tension belt, the metal core 3a surrounds a composite material 3b made of heat-resistant resin, ceramic, metal, or the like. This is illustrated with a tension belt 3 of construction. The speed change transmission device 10A according to the present invention achieves a constant horsepower power transmission with high efficiency in the entire wide variable speed variable torque band as shown in FIG. 7 by the operation of the speed change control device 10B described below.

  Each of the operation devices 9 and 8 is configured to be able to individually identify and supply pressure or elastic force to the corresponding movable wheels 1a and 2a of the transmission wheels 1 and 2 according to a control command. In other words, the pressure supply by the first pressurizing device makes the corresponding transmission wheel function as a reference vehicle function, and the elastic force supply by the second pressurizing device makes the corresponding transmission wheel work by the following vehicle function. Here, the reference vehicle / following vehicle function refers to a function of setting a stable factor at the time of friction transmission on the reference vehicle side and self-converging and stabilizing the unstable factor on the following vehicle side. That is, the reference vehicle function is a function for determining the output rotational speed and speed ratio by determining the reference position of the belt at the time of friction transmission, and means positioning control of the pulley V groove for determining the belt contact radius. During speed change operation, pressure is applied from the pulley to the belt and variable diameter positioning control is performed. However, when the speed ratio is determined, the application of the pressure is substantially stopped and the position of the V groove by the movable vehicle is fixed. V-grooves with the same conditions are formed. The following vehicle function always maintains the supply of the specified friction pressure between the two, regardless of the positioning control, even if error factors such as belt / pulley contact surface abrasion and internal / external disturbance vibration occur. It is a function that determines the input or output torque of each axis by performing the self-setting or automatic centering function for instantaneously returning to the transmission state by the action of elastic force.

  In this example, the input operating device 9 is an individual pressurizing device 50 having an input first pressurizing device 11 for supplying pressure to the input wheel 1 and an input second pressurizing device 51 for supplying elastic force. Consists of. Furthermore, the input first and input second pressurizing devices are constituted by input first and input second compression devices 14 and 54 and input first and input second drive sources 60a and 60b, respectively. The input first pressurizing device 11 is a series structure of an input switching device abutment device 35 and an input first compressing device 14, and the input second pressurizing device 51 is an elastic device 31 and an input second compressing device 54. Both are configured in series, and both press the movable wheel 1a of the pulley 1 in parallel with each other in the direction of the rotation axis through the common sliding body 36 and the bearing 5. The contact device 35 and the elastic device 31 are coaxially arranged on the outer periphery of the shaft 1c of the input wheel 1 and are arranged in parallel on the concentric circle and parallel to the axial direction, and the input first and second input compression devices 14, 54 are Cascade on the same axis. Therefore, the pressurization form of each pressurizing device is such that the input first compression device 14 from the inner wall of the second main body 10b and the input second compression device 54 from the outer wall through the pressure transmission device 70 of FIG. Pressure is transmitted to 31.

  The first and second compression devices 14 and 54 of the first and second pressurizing devices 11 and 51 are respectively the first and second sliding devices 13 and 53 and the first and second urging devices that urge them. 12, 52. The first and second sliding devices 13 and 53 have two sliding tools 16, 17 and 56 and 57, and first and second pressing devices 15 and 55 that slide between the two sliding tools 16, 17 and 56, 57. is there. The first sliding device 13 is formed in a tubular shape, and the second sliding device 53 is formed in a rod shape around the input wheel 1 and is spaced apart on the extension of the shaft 1. The first and second urging devices 12 and 52 are both worm transmissions composed of worms 18 and 58 and wheels 19 and 59 in this example, and are respectively connected to shafts 18a and 58a from first and second drive sources 60a and 60b. Once the first and second sliding devices 13, 53 are positioned once the speed ratio and the input torque command are input, the self-lock function is maintained that maintains the position even when the supply of each control command is stopped. The first and second pressurizing devices 11 and 51 pressurize the vehicle 1 between the taper roller 5 and the thrust bearing 5b in a non-rotating state. The male screw sliding tool 16 passed through the key 19a of the gear 19 and the female screw sliding tool 57 directly connected to the gear 59 do not slide up and down with rotation. In the second pressurizing device 51, the moving tool 17 moves up and down according to the inclination of the sliding devices 13 and 53.

  The abutting device 35 of the input first pressurizing device 11 functions as a switching device, and is composed of two sliding members 36 and 37 arranged through a gap 38, both of which are selected according to the selection of the operation command of the input first compressing device 14. The supply and stop of pressurizing force are controlled by the control command of the adjusting device 90 at the time of the abutting operation for abutting each other and at the time of the abutting release for separating the two. During the contact operation, the input first compression device 14 directly applies pressure to the input wheel 1 through the sliding members 36 and 37 and the bearing 5, so that the wheel 1 performs the reference vehicle function of the variable diameter positioning control. Become. When the contact is released, the gap 38 is generated and the input first compression device 14 does not act on the input vehicle 1, so that the torque control of the following vehicle function can be selected. In this example, the sliding material 37 is shared with the sliding tool 17 of the input first compression device 14, and the sliding material 36 is shared with the sliding body 34 of the elastic device 31. Reference numeral 77 denotes a rotation prevention device for preventing rotation.

  The elastic device 31 of the input second pressurizing device 51 is provided with a central through hole, and is composed of an elastic body 32 having a series structure of four disc springs, and two sliding bodies 33 and 34 that pressurize the elastic body 32 at both ends. The through holes are arranged concentrically on the outer periphery of the first sliding tools 16 and 17 of the input first sliding device 13 and the contact device 35. The elastic body is configured to be capable of transmitting elastic vibration at one end and not at the other end, and is supported in a floating state because both ends are slidable. As shown in FIG. 2, in this example, the elastic device 31 is provided with a pressure transmission device 70 between the input second compression device 54 and compresses the elastic body 32 in series, and simultaneously generates elastic force via the sliding body 34 and the bearing 5. At this time, the vehicle 1 performs the function of the following vehicle under variable pressure control. Therefore, the pressure applied by the input first pressurizing device 11 and the elastic force of the input second pressurizing device 51 are applied in parallel to each other through the common sliding body 34 and the bearing 5.

  The pressure transmission device 70 in FIG. 2 includes a first transmission means 71 and a sliding body 33 that are connected to the end portion 56a of the sliding tool 56 of the input second compression device 54 and extend symmetrically from the center pressure receiving and pressing point. Lateral transmission means 78 composed of the second transmission means 74 that also serves as the same, longitudinal transmission means 73 composed of the two pressure shafts 72 connected to both ends thereof and parallel to the axial direction of the sliding tool 56, and the elastic device 31. This is a support device 79 comprising a bearing that smoothly guides the sliding direction of the pressing pressure shafts 72, 72 and a body through hole. Each means 71, 72, 73 forms a rectangular frame and supports the shafts 72, 72 by the main body 10 d via linear ball bearings 75, 76 in order to maintain the rectangle even under high pressure, and is applied in the same direction as the sliding tool 56. Press. In this example, the sliding body 33 and the pressure ring 74 are shared and the elastic device 31 is pressurized in series.

  In this example, the output operating device 8 of FIG. 3 is a common pressurizing device 21 in which the pressure supply of the output first pressurizing device and the elastic force supply of the output second pressurizing device to the output wheel 2 are made into a single configuration. The two are identified and supplied in response to a control command to the shared drive source 60c. Unlike the input operation device 9, the composite device 20 in which the output elastic device 41 and the output contact device 45, which is an output switching device, are assembled in parallel, and the common compression in which the output first and second output compression devices are similarly configured in a single configuration. A common pressure device 21 which is a composite pressure device 40 assembled in series by the device 24 is provided. The common compression device 24 is a common sliding device 23 composed of two sliding tools 26, 27 and a common pressing device 25 of the ball screw 26a, and further a common energization of a worm transmission device composed of a worm 28 and a wheel 29 and having a self-locking function. It consists of device 22. The difference between the common and input second compression devices 24 and 54 is that the input second sliding device 53 is pressurized with a right-hand screw while the common sliding device 23 is pressurized with a left-hand screw. The sliding tool 56 moves up and down without rotation according to the inclination pitch. However, since the sliding tool 26 rotates and moves up and down, the bearing 49 is arranged, and further, the entire input second compression device 54 cannot vibrate. Although installed in the main body 10b, in the common compression device 24, only the common sliding device 23 supports the sliding tool 26 for supporting the elastic state between the transmission wheel 2 and the elastic device 41 in an interlocked state or a floating state. Has a spline coupling 26c extended between the wheel 29 of the common urging device 22 so as to be slidable in the axial direction, thereby enabling rotational transmission.

  The elastic device 41 to be pressurized through the bearing 49 has a sliding body 43 formed in an annular pan and an elastic body 42 composed of a plurality of disc springs that store and pressurize between the sliding body 44. In this example, the elastic body 32 in FIG. 2 is disposed on the transmission wheel side and the elastic body 42 in FIG. 3 is disposed on the main body side. Effectively suppresses vibration on the friction transmission surface by supporting it. The contact device 45 includes two sliding members 46 and 47. In this example, the sliding member 47 is shared by the pan-shaped outer edge of the sliding member 43, and the sliding member 46 is shared by the sliding member 44. FIG. 3 shows the left half of the center line with a gap 48 when the elastic device 41 is lightly loaded, so that the elastic device 41 exceeds the predetermined value in the right half and the elastic device 41 exceeds the predetermined value when the abutting device 45 is in the released state. Shows a state in which the applied pressure is identified and supplied to the transmission wheel 2 in the contact operation state. In the contact operation state of this example, the elastic force Ps of the elastic body 42 is always supplied while being applied to the applied pressure.

  The common pressure device 21 also includes a vertical transmission means 83, a horizontal transmission means 88, and a support device 89 having the same structure as the input second pressure device 51, and has a rectangular frame pressure transmission device 80 symmetrically. The explanation is omitted. The difference is that, in this example, the entire pressurizing mechanism is arranged on the back side of the fixed wheel 2b to transmit elastic vibrations to each other. FIG. 5 is a cross-sectional view of the pressure detector 94 of the first detector disposed between the main body 10d of the common pressure device 21 and one end of the composite device 20. An annular detection end 101 configured such that the main diaphragm 104 in which the annular elastic body 42 and the sliding member 47 are liquid-sealed can be compressed simultaneously, and the auxiliary diaphragm 106 is displaced by extending radially from one position of the detection end 101. The lead-out end 102, a pressure-electric signal conversion unit 103 having a semiconductor strain gauge disposed at the end, and an oil medium 105 are further provided. It is possible to properly sense not only the applied elastic force or applied pressure but also the value of the friction pressure on the output friction transmission surface during constant speed ratio operation, and to perform negative feedback control of torque by the friction pressure.

As shown in FIG. 4, the operation devices 8 and 9 respectively have the input first, input second, and shared drive sources 60 a, 60 b, and 60 c individually for the input first, input second, and common pressure devices 11, 51, and 21, respectively. Control commands are supplied individually from the electronic control device 90 which is provided adjacently. Each drive source 60 has a gear head 64, a DC servo reversible motor 65, a brake 66, and an encoder 67, respectively, and corresponding reference part numbers are denoted by reference symbols a, b, and c. Both controllers require servo control synchronized with each other, but the amount of movement of the compression devices 14, 54 and 24 is different, so that control commands to the corresponding shafts 18a, 58a and 28a are sent from the adjusting device 90. Gear transmissions 61a, 61b, 61c having different speed ratios provided individually are provided, and gears 68, 69 are attached as necessary.

  The adjusting device 90 is input via a CPU / arithmetic processing device 95 and storage devices 96 and 97 composed of various RAMs and ROMs through a conversion amplifier 98 such as A / D to D / A and an input / output device 91 having a transmission bus. And output information. Input information includes a start command for the transmission 10 such as a starter switch such as an engine, a control command such as a shift command or a depressurization command, and a rotation speed detector 92 for the transmission wheels 1 and 2 as the second detector in FIG. , 93, the belt pulley frictional contact pressure from the pressure detector 94 through the filter 99, and the encoder operation amounts Ra, Rb, Rc, and the like. The output information is operation commands Ea, Eb, Ec and brake commands Ba, Bb, Bc from the conversion amplifiers 98a, 98b, 98c to the motors 65a, 65b, 65c.

  The storage device 96 has basic information for the arithmetic processing unit 95 to execute programmable control. The storage device 97 is composed of three pieces of processing information. The memory 97a is control information when the pulley 1 is operated as the following vehicle function and the pulley 2 is operated as the reference vehicle function. The memory 97b is the pulley 1 as the reference vehicle function and the pulley 2 is the following vehicle. The control information when the function is activated, the memory 97c stores the synchronous operation information when the functions of the pulleys 1 and 2 are switched, and the constant torque type transmission and torque when each of the actuators 8 and 9 is operated individually and asynchronously. Control information such as a conversion type transmission, a simultaneous operation of input and output elastic forces, and a command operation for depressurization is stored in advance. The filter 99 removes elastic vibration components from the elastic force. The devices of the drive source 60 and the adjusting device 90 described above are already disclosed in, for example, Sanyo Denki Co., Ltd. “1998-99 Servo System General Catalog” and the like, and are not commercially available.

  Next, the operation of the first embodiment will be described. The idea of this example is that when the contact radius between the belt pulleys is large for any input or output vehicle using a tension belt, the transmission vehicle is always used as a reference vehicle function and the contact radius is small. Is to control the supply by identifying the applied pressure or elastic force from each corresponding operating device in order to always make the transmission vehicle function in the following vehicle function. In this example, the case where the speed ratio ε (= N1 / N0) of the input and output rotational speeds N1 and N0 is switched based on ε = 1 in the intermediate region will be described. In other words, in the high speed ratio range where ε> 1 or the low speed range, the transmission mode of the first transmission device A is configured by individually operating the input vehicle 1 with the following vehicle function and the output vehicle 2 with the reference vehicle function. In the small speed ratio range or high speed range where ε <1, the input vehicle 1 is provided with a reference vehicle function and the output vehicle 2 is provided with a follow-up vehicle function so that the second transmission device B is operated individually, The operation modes of both the operating devices 8 and 9 and the transmission are switched. In FIG. 1, the input wheel 1 has the minimum radius r10 and the output wheel 2 has the maximum radius r00. Therefore, in the operating device 9, the contact device 35 of the input switching device is in the released state, and the operating device 8 Assume that the abutment device 45 of the output switching device supplies pressures in the abutment operation state to form the first transmission device A, and a speed increase command is supplied during this transmission.

  FIG. 6 is an operational characteristic diagram in which the speed ratio ε of the speed change range is shown on the horizontal axis, and the frictional force P between belt pulleys and the contact radius r are shown on the left and right vertical axes. FIG. 6A is an input vehicle and FIG. Each characteristic is shown. At startup, the input wheel 1 is subjected to the maximum input friction pressure by the maximum compression pressure of the elastic body 32 because of the maximum speed ratio εmax of FIG. The maximum output friction pressure due to the tension is guaranteed in the V groove of the output wheel 2 through the V belt 3 having the maximum tension. In the case of this example, even when the output contact device 45 is in contact operation, the elastic pressure of the elastic body 42 passes through the bearing 49, the common sliding device 23, and the pressure transmission device 80, and the basic pressure Ps0 of the two-dot chain line in FIG. Continue to be supplied. Accordingly, the output friction pressure of the output wheel 2 becomes the maximum value P0max in which the belt tension and the basic pressure Ps0 are superimposed. When the speed increasing command is applied and the three motors 67 are moved, the shafts 18a, 58a, and 28a are rotated, and the gap 38 of the contact device 35 is loosened on the input vehicle side, but there is no influence, and the elastic body 32 is compressed second. Since the compression is reduced to P11 by the device 54 as shown in FIG. 6A, the supply elastic force as a torque command is reduced and the input friction pressure is also reduced. Since the output friction pressure due to the belt tension decreases on the output vehicle side, the output friction pressure is also reduced to P01, and at the same time, the composite device 20 is left as it is by the common compression device 21, and only between the sliding tools 26 and 27 of the common compression device 21. Is relatively displaced, and the movable wheel 2a is forcibly moved by the supply pressure as a speed ratio command through the pressure transmission device 80, and the belt radius is reduced to r01. At the same time, the radius r10 of the input wheel 1 increases and moves to r11 regardless of the reduced pressure by the action of the elastic force. This series of operations is performed simultaneously and synchronously. Similarly, when the speed increasing command is applied again, the same operation is repeated and repeated until the speed ratio ε = 1 is reached.

  Further, when the speed increasing command reaches ε = 1, the contact devices 35 and 45 function as both switching devices, and the operations of the two operating devices 8 and 9 are switched instantaneously. That is, on the input side, the slightly left gap 38 of the abutting device 35 is instantaneously erased by the command of the adjusting device 90, and the sliding members 36 and 37 enter the abutting operation state, and the elastic force of the elastic body 32 is changed to the abutting device. Switching is performed with the speed ratio fixed to the pressure of 35 preferentially. At the same time, the slide device 26 is raised by the action of the common urging device 22 on the output side to depressurize the composite device 20, so that the contact device 45 enters the contact release state from the pressure detector 94, and the elastic force of the elastic body 42 is reduced. It is transmitted to the vehicle 2 through the common sliding device 23 and the pressure transmission device 80. Therefore, in the small speed ratio range of ε <1, the input vehicle 1 increases the contact radius and functions as the reference vehicle function, and the output vehicle 2 decreases the contact radius and functions as the second transmission device B configured as the following vehicle function. In the first transmission device A, the output rotational speed is directly controlled by the output operation unit 8, and the output torque is switched by indirect control via the belt tension by the input operation unit 9 to form one pressurizing device on both sides. After that, in the second transmission device B, the output rotational speed is indirectly controlled by the speed ratio command of the operating device 9 and the output torque is directly controlled by the torque command of the operating device 8 to form the other pressurizing device. Therefore, thereafter, stable transmission is continued in exactly the same manner except that each control command by the adjusting device 90 and the supply switching of each compensation signal are performed. The left half of FIG. 3 shows the compression state of the output wheel 2 and the common pressure device 21 with the speed ratio ε s at the output rotational speed when the speed increase command is further applied. The same operation is performed up to the minimum speed ratio εmin.

  On the other hand, returning to the maximum speed ratio εmax can be achieved by an operation procedure reverse to that described above by giving a reverse rotation command to each motor 65. In the present example, the function switching at the speed ratio ε = 1 eliminates the adverse effects of the longitudinal extension of the belt 3 and the thickness change in the width direction. An example in which the command supply of torque and speed ratio command to each pressurizing device is switched based on the speed ratio signal ε and torque signal calculated from 93 and the pressure detector 94 will be described. In practice, however, each command is controlled by applying an operation gap as shown in FIGS. 6A and 6B in order to prevent hunting between the transmission devices A and B near the speed ratio ε = 1. In the above example, since only one of the elastic device 31 or the contact device 35 of the operating device 9 affects the pressurization of the vehicle 1, the first and second compression devices 14 and 54 may always be driven. There is no need to do so, and the second compression device 54 that does not affect the vehicle 1 may stop supplying torque commands during that period as in the left sliding body in FIG. It is sufficient to always drive both at the same time. Furthermore, when the transmission members such as the elastic bodies 31 and 41, the pulleys 1 and 2 and the belt 3 are worn or deteriorated due to high compression pressure over a long period of time, there is a risk that the predetermined friction pressure cannot be continuously maintained in each of the cars 1 and 2. However, in this example, even when the transmission operation is stopped in the maximum speed ratio state of FIG. 1, the pressure removal forcibly releasing or pressurizing the high pressure of each of the pressure devices 51 and 21 from the adjustment device 90 to the low pressure. Alternatively, a command for pressurization can be given to take measures to prevent aged deterioration by forced release when the operation is stopped for a long time. Each amplifier 98 may be switched quickly by switching the DC motor 65 by operating the supply voltage or the pulse amount only when switching between the two operating devices, and may switch the function by supplying an instantaneous speed command.

  Further, in this example, there is a case where the output torque is achieved by indirect or direct pressurization control of the input and output manipulators 9 and 8, but when the elastic bodies 32 and 42 are deteriorated, a highly accurate desired friction pressure is input and In order to guarantee the output wheels 1 and 2, a pressure detector is used for torque calculation. Even when the input / output vehicles 1 and 2 work as a reference vehicle function, an elastic force may be supplied, and the wedge friction pressure can always be sensed by the same detector, so that the servo control is naturally performed. Torque compensation control at the time of reduction of each friction pressure or torque is carried out by using the CPU 95 and the memory 97a that know each friction pressure or torque detection value due to deterioration of the elastic body 31 or the like to the friction pressure or torque reference value determined in advance according to the load. Servo control may be performed by applying closed loop control to the input or output operation devices 9 and 8 as appropriate, and variable torque control with predetermined friction pressure supply can be arbitrarily controlled by open loop control or the like. . The same applies to the case where the rotation speed detector 93 is used when the output rotation speed is controlled by indirect or direct positioning control of the input or output operation devices 9 and 8.

  The effect of this example is that when the contact radius or area between the belt pulleys of both cars 1 and 2 is reduced, the continuous supply of high-pressure elastic force is maintained, so slipping due to insufficient pressurization is eliminated, and the contact radius or When the area increases, elastic force is not applied at all except during gear shifting operation, or only variably controlled elastic force is applied, so there is no friction coefficient fluctuation or excessive friction force destabilization. Transmission failure due to the belt winding phenomenon due to pressure is eliminated. Therefore, in the present specification and claims, “substantially non-pressurized” means that the elastic force may be positively variably controlled within a range that does not adversely affect the frictional transmission. As a result, as shown in FIG. 7, the maximum efficiency range between the first transmission device A in the high speed ratio region and the second transmission device B in the small speed ratio region is obtained by using the difference between the two maximum efficiency ranges of the two efficiency characteristics. In addition to the stable connection in the middle area, it is shown that both speed change areas can be greatly expanded while maintaining stability and widening of the band can be achieved. In addition, high-efficiency transmission is also achieved at both ends of the low-speed range and the high-speed range. However, the greatest advantage is that not only the conventionally known push-type belt but also a tension-type belt can be applied without any adjusting device such as a cam mechanism because the belt winding phenomenon is eliminated. The function switching position of each operating device is not necessarily limited to the speed ratio ε = 1 and can be arbitrarily changed.

  8 and 9 show a second embodiment variable transmission. The second embodiment is different from the first embodiment only in the configuration of the input operation unit 9, and the variable torque control and the variable diameter positioning control operation by switching the functions of the first and second transmission devices A and B are substantially performed. Is exactly the same. Therefore, members having the same or similar functions are denoted by the same reference numerals as in the first embodiment, and the differences are described. The structural difference is that, like the output operation unit 8, the input operation unit 9 is connected in series with the combined compression unit 14 and the combined unit 30 that share the first and second compression units. The common pressurization device 11 and the common drive source 60a formed by sharing the input first pressurization device and the input second pressurization device are formed. In the composite device 30, the elastic device 31 of the input second pressurizing device 51 and the contact device 35 of the input first pressurizing device 11 are preliminarily compressed and assembled in parallel. In this example, the sliding tool 17 of the common sliding device 13, the sliding body 33 of the elastic device 31, and the sliding material 37 of the abutment device 35 are integrated and used as a composite device 20. Forms a closed circular pan-shaped storage frame. The elastic body 32 is compressed and accommodated with sliding members 36 and 37 that also serve as the sliding body 34. As shown by the solid lines of the friction pressure characteristics in FIGS. 6A and 6B, the input elastic body 32 is responsible for the high pressurization region characteristic Ps1 and the output elastic body 42 is responsible for the low pressurization region characteristic Ps0. In the case of the former, a disc spring having an elastic compression pressure larger than that of the latter is selected, but it also varies depending on the friction coefficient between belt pulleys. The sliding member 37 is provided with a screw 39 between the movable member 37a and the movable member 37b, so that the operating point of the contact or release state of the contact device 35 can be adjusted. The contact device 45 may be configured in the same manner.

  The difference between the composite devices 30 and 20 is that the compression direction of the elastic body is opposite to each other. The composite device 30 is an elastic body closed type compressed and stored in advance, but the device 20 is an open type. 6A and 6B, since the operating device 8 controls the positioning of the belt 3 with the applied pressure while the transmission 10 is operating with the first transmission device A, a gap 38 shown in FIG. The elastic body 32 works effectively. However, when moving to the second transmission device B, the operating device 8 enters the variable pressure control area of the elastic force, and at the same time the contact device 35 disappears the gap 38 and the operating device 9 moves to the contact operation state of FIG. In the small speed ratio range, the function of the elastic body 32 is substantially invalidated, and the input vehicle 1 operates as a reference vehicle function. The belt 3 is shown as a push-in type with an endless belt 3a and a large number of blocks 3b.

  The utility of this example is substantially the same as that of the first embodiment, but further reduction in size and weight can be achieved. However, since the composite device 30 is a closed type, the elastic body 32 for preventing deterioration cannot be depressurized while the transmission is stopped, but the pressure detector 94 is used for output torque control even if the compression pressure of the elastic body 32 changes over time. Since the CPU 95 and the memory 97c constantly adjust the predetermined output friction pressure in the output wheel 2, the decrease in the elastic force can be overcome by the compensation operation that increases the operation amount of the input operation device 9. Even without a detector, an elastic material with little deterioration may be used to withstand long-term transmission or readjustment with the screw 39 may be performed.

FIGS. 10 and 11 show a third embodiment showing the common base concept of the present invention, in which both actuators have their input vehicle and output vehicle cross sections of the variable transmission constituting the first transmission device A without constantly switching functions. FIG. In this example, the input operating device 9 has a function of following the torque control by variable pressurization control that always supplies elastic force with a torque command, and the output operating device 8 supplies pressure with a speed ratio command during shifting. In the steady state, the vehicle functions as a reference vehicle for speed ratio control by variable positioning control without pressure. In order to obtain a large friction pressure between the belt pulleys, the method of applying a huge external pressure to the transmission wheel does not stabilize the friction coefficient, resulting in inability to transmit due to excessive friction force. In particular, this tendency is more likely to occur in the output vehicle 2 than in the input vehicle 1. The reason is that the output rotational speed N ₀ becomes smaller and, conversely, the output torque T ₀ needs to increase accordingly. In this example, even if the pressure is supplied when the control command is supplied, the external pressure by the pressurizing device is not applied to the V groove of the output wheel 2 at all during the constant speed ratio operation. The configuration is equivalent. Ensuring the predetermined output torque is a concept that is determined only by the belt tension applied by the elastic friction pressure of the input wheel 1 that functions as a following vehicle by the input operation unit 9. Regardless of the type of belt, such as the chain belt 3 shown in the figure, which is likely to cause an in-pulley pull-in belt or a push-in belt that is unlikely to occur, stable transmission and high-efficiency transmission in a large speed ratio range are achieved.

  Structurally, the input operation device 9 includes an elastic pressure device 51 and a drive source 60b in which the compression device 14 serially compresses the elastic device 31 by removing the contact device 35 from the operation device 9 of FIG. The output operation device 8 removes the composite device 20 from the operation device 8 of FIG. 1, 3 or 8 and applies pressure only during the shifting operation by the compression device 24 in which the sliding device 23 and the urging device 22 are directly connected. The output wheel 2 has a structure that fulfills the reference vehicle function of variable diameter positioning control. Since other structures are the same as those of the first and second embodiments, the same reference numerals are assigned and detailed description is omitted. Since the detection end 101 of the pressure detector 94 senses the pressure at the thrust bearing 4b of the wheel 29, the value of the friction pressure can always be sensed between the compressor 24 and the main body 10d via the movable wheel 2a and the pressure transmission device 80. Similar to the embodiment, servo control is performed on the controller 9 by the adjusting device 90, and further open or closed loop control is performed, whereby arbitrary torque control by appropriate frictional force management can be achieved.

The reason why either of the input / output vehicles in the above-mentioned embodiment has the function of following the vehicle by the elastic force is to provide the elastic force itself with the ability to absorb error factors such as the belt circumference extension and thick miso so that it is always stable transmission This is to make it possible to maintain. Therefore, even if the input operation device 9 is a variable transmission assembled with the structure of FIG. 10 and the output operation device 8 with the structure of FIG. 3, the input elastic body 32 is selected to have a spring pressure larger than that of the output elastic body 42 and is substantially selected. When it functions as an applied pressure, it performs stable transmission. Therefore, in the present invention, the elastic force may be supplied to the input and output vehicles at the same time to perform torque control in both vehicles, but the pressure supply state should not be at least simultaneously. Accordingly, one of the operating devices 8 and 9 is an individual pressurizing device or a composite pressurizing device, and the other is an elastic pressurizing device in which the second compressing device compresses the elastic device in series. Therefore, variable torque control according to the load is possible. Accordingly, at this time, it is not necessary for each pressurizing device to have a switching device such as a contact device as in the third embodiment, etc. Further, a constant speed ratio not shown in FIG. Even if the pulley is applied, the idea of the present invention for adjusting the output torque with the input operation unit can be achieved and included in the scope of the present invention.
Therefore, the present invention includes various changes and modifications within the scope that can be easily created by those skilled in the art from the claims.

In Embodiment 1, the output pulley is a variable diameter type or constant speed ratio pulley and the belt contact radius is constant. In the second embodiment, the adjusting device is a variable transmission that is programmable controlled by a storage device and an arithmetic processing unit that store a preset pressure reference value of speed ratio versus input / output friction pressure determined in accordance with a load. In the third embodiment, the adjusting device uses the closed loop control or the input / output torque in which the compensation amount corresponding to the deviation between the detected value of the friction pressure or torque and the set friction pressure or the torque reference value is added to the operation amount to the input operation device. A variable transmission that performs open loop control in response to a predetermined elastic force command. In Embodiment 4, each compression device is composed of a sliding device having a pressing device between two sliding tools and an urging device for moving the pressing device, and is self-reversing to one or both of the sliding device and the urging device. A variable transmission with a blocking function. In the fifth embodiment, the first input device and the first output pressure device can control the presence or absence of the supply of pressure to each pulley movable vehicle according to the contact or release state of the two sliding members with or without the gap between them. Variable transmission with a simple input and output contact device. In Embodiment 6, each elastic device is composed of an elastic body and two sliding bodies arranged at both ends of the elastic body, and one end of the elastic body that supports transmission of elastic force vibration at one end and not at the other end. Variable transmission with the other end compressed by a second or shared compressor.

In the seventh embodiment, the adjusting device is a variable transmission that is switched at the time when the speed ratio is ε = 1. In embodiment 8, the adjusting device has a variable transmission having an operation gap between the speed ratio decrease and increase at the time of operation when switching each operation device. In Embodiment 9, each operating device is a variable transmission in which a composite pressurizing device is applied to the input operating device and an individual pressurizing device is applied to the output operating device. In Embodiment 10, the adjusting device is a variable transmission that releases the compression of each elastic device of the second and combined pressurizing devices while the transmission is stopped. In embodiment 11, the adjusting device is a variable transmission having a pressure detector for sensing input / output friction pressure between the main body and the second or common compression device and the elastic device. In the twelfth embodiment, the input and / or output operation device is composed of two pressurizations in which the upper and lower lateral transmission means extending left and right from the pressure receiving point and the ends of the respective lateral transmission means are connected to each other. A variable transmission having a pressure transmission device comprising a longitudinal transmission means formed of a shaft and a support body that slidably supports the vertical transmission means with a main body and a bearing.

In Embodiment 13, each operating device is provided with each elastic device or abutting device, each compression device, or each pressure device arranged around the pulley, and the compression device, the elastic device, A variable transmission in which pressure is transmitted between the contact device and the pulley bearing by a pressure transmission device. In a fourteenth embodiment, the first and second pressurizing devices are variable transmissions in which one of the compression devices is annular and penetrates the pulley shaft and the other is applied to the shaft extension. In the fifteenth embodiment, the first and second pressurizing devices are variable transmissions in which the elastic device and the corresponding contact device, which are annular each other, are applied in parallel to the pulley axial direction. In the sixteenth embodiment, the first and second pressurizing devices are variable transmissions that are pressurized via the bearings of the pulley movable wheel and the shared sliding body of the elastic and contact devices. In Embodiment 17, the variable actuator is composed of an elastic pressurizing device in which both the operating devices are compressed individually and the other compression device is compressed in series by the second compression device.

In the eighteenth embodiment, the composite pressure device is a variable transmission in which the corresponding contact devices are arranged concentrically on the inner side or the outer side of the annular elastic device. In a nineteenth embodiment, the composite pressurizing apparatus comprises an annular device in which one of the sliding bodies closes the corresponding contact apparatus for controlling the gap between the two sliding materials, and the elastic apparatus composed of the two sliding bodies and the elastic body. Variable transmission with a single composite device formed in a formwork. In a twentieth embodiment, the composite pressurizing apparatus is arranged such that one of the two sliding members is slidable on the mold sliding member and the other is slidable between the elastic member and the one sliding member, and the minimum compression pressure Ps1 is set in advance. A variable transmission that is a sealed closed type and arranged in the input controller. In a twenty-first embodiment, the composite pressure device uses one of the sliding members as the formwork sliding member and the other as the main body, and supplies the maximum compression pressure Ps0 of the elastic member when the sliding members contact each other. A variable transmission that is an open type and arranged in the output controller. In Embodiment 22, the variable actuator is composed of an elastic pressurizing device in which both the operating devices are compressed by the combined pressure device and the other compression device is compressed in series by the second compression device.

1, 2 Pulley 3 Belt 8, 9 Operator 10 Variable transmission or main body 11 Input first pressurizing device 12 Input first biasing device or worm transmission device 13 Input first sliding device 14 Input first compression device 15 Input First pressing device 30, 20 Composite device 31, 41 Elastic device 35, 45 Contact device or switching device 40 Compound press device 50 Individual press device 51 Input second press device 52 Input second bias device or worm transmission Machine 53 Input second sliding device 54 Input second compression device 55 Input second pressing device 60 Drive source 60a Input first drive source 60b Input second drive source 60c Output shared drive source 70, 80 Pressure transmission device 90 Adjusting device 92 , 93 Second detector or rotational speed detector 94 First detector or pressure detector

Claims (7)

The input or output first pressurizing device applies a pressure force to the belt from the input or output first compression device, and controls the positioning of the belt contact radius sandwiched by the input or output vehicle consisting of a variable-diameter transmission vehicle to variably operate the speed ratio. In the variable transmission
The input second pressurizing device gives the input elastic force obtained by the input second compression device compressing the input elastic device in series to the input wheel and the contact surface of the belt, and variably presses the belt friction pressure applied to the contact surface. A variable transmission characterized in that the input torque is variably operated by controlling. The input or output first pressurizing device applies a pressure force to the belt from the input or output first compression device, and controls the positioning of the belt contact radius sandwiched by the input or output vehicle consisting of a variable-diameter transmission vehicle to variably operate the speed ratio. In the variable transmission
The input second pressurizing device is configured such that the input second compression device performs input torque control on the input vehicle by an input elastic force obtained by serially compressing the input elastic device, and each compression device is connected to the sliding device by a belt. A variable transmission characterized in that an urging device for preventing the reverse flow of the friction pressure is connected, and that one of the urging devices prevents the command from flowing out from the other urging device when the command is supplied and maintains the input torque with high accuracy. Motivation. The input or output first pressurizing device applies a pressure force to the belt from the input or output first compression device, and controls the positioning of the belt contact radius sandwiched by the input or output vehicle consisting of a variable-diameter transmission vehicle to variably operate the speed ratio. In the variable transmission
The input second pressurizing device applies the input elastic force obtained by the input second compression device compressing the input elastic device in series to the input wheel, and the belt friction pressure predetermined for the speed ratio in the storage device of the adjusting device. Alternatively, the variable transmission is characterized in that an input torque command calculated from the input torque is received from the adjusting device, and the belt is automatically aligned and the input vehicle is always subjected to input torque control.   4. The variable transmission according to claim 1, wherein the variable transmission includes an output second pressurizing device that performs output torque control on the output vehicle with an output elastic force obtained by serially compressing the output elastic device by the output second compression device. A variable transmission characterized in that the input and output torques are controlled in an open or closed loop according to the carrying load. The input or output first pressurizing device applies a pressure force to the belt from the input or output first compression device, and controls the positioning of the belt contact radius sandwiched by the input or output vehicle consisting of a variable-diameter transmission vehicle to variably operate the speed ratio. In the variable transmission
The input and output second pressurizing device performs input and output torque control by applying the input and output elastic force to the input and output vehicles obtained by the input and output second compression device respectively compressing the input and output elastic devices in series. As a result, the adjusting device differentiates the input and output torque commands so that the product of the speed ratio and the input torque becomes the output torque, and applies the efficiency compensation to the input and output second pressurizing devices, respectively, thereby applying the speed ratio. A variable transmission characterized in that the input and output torques are controlled by open or closed loop.   6. The pressurizing device according to claim 1, wherein each of the pressurizing devices comprises an inclined sliding device or a hydraulic sliding device capable of stably maintaining the pressurizing position of the input or output vehicle even after the supply of the command is stopped. The sliding device is connected to a drive source through an urging device that prevents the reverse outflow of a mechanical command, and a command from the adjusting device is applied to the drive source or the urging device. 7. The variable transmission according to claim 6, wherein the variable transmission is depressurized and pressurized so as to depressurize the input or output elastic device in a high compression state when the variable transmission is stopped, to continue the operation stop and to repressurize at the time of start-up. A variable transmission characterized in that a command for pressure is applied from an adjusting device to an input or output second drive source or an input or output second compression device.