JP2010281454A - Variable transmission machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To overcome the problem that, when the belt contact areas of input and output wheels are substantially equal to each other in belt transmission, the transmission efficiency is good, but when it is deviated from the range, the efficiency is deteriorated, and the usage band is narrowed even in low-speed range and high-speed range, and to attain a broadband high efficiency transmission method by assembling two transmission machines or two input and output pressurizing devices having transmission modes which are different from each other. <P>SOLUTION: The variable transmission machine includes a first input and output pressurizing device 11 or a first transmission machine which performs speed ratio control and torque control respectively by applying a pressurizing force and an elastic force to input and output wheels 1, 2 respectively, and a second input and output pressurizing device 51 or a second transmission machine which performs torque control and speed ratio control by applying the elastic force and the pressurizing force to the input and output wheels 1, 2 respectively, wherein a broadband transmission method is attained by switching between both the pressurizing devices 11, 51 or between both the transmission machines while combining each transmission band. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a continuously variable transmission used for general industrial machines, vehicles, electric motors, etc., and a variable transmission that achieves frictional force stabilization and broadband high-efficiency transmission by identifying and supplying elastic force and pressure to pulleys.

The operation of a constant horsepower belt continuously variable transmission is described in U.S. Pat. No. 4,973,288 or 5,269,726.
The product is under development, but a satisfactory product is not realized. 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] that is normally transmitted to the load by the output vehicle is a transmission relation between the rotational speed N [rpm] and the torque T [Kgm] P =
Determined by 1.027 × N × T. 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 variable pressure control of the area with the pulley and the constant friction. 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 of the push-type belt is maximum near the speed ratio ε = 1, but in other speed ratio areas, the contact area of both pulleys is not balanced and deteriorates. That is, it is assumed that heat is generated due to belt biting due to excessive frictional force on the increase side of the contact area in both pulleys and slip heat generation due to insufficient frictional force on the decrease side of the contact area.

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

The common problem to be solved by the present invention is that the input and output pressurization devices for the input and output vehicles have established a pair of combined ideas of speed ratio control and output torque control, respectively. It is another object of the present invention to provide a variable transmission that establishes a highly efficient and broadband transmission concept by providing a second transmission form of torque and speed ratio, respectively.
The first problem to be solved by the present invention is that the efficiency of a normal variable speed machine usually deteriorates when the speed ratio is outside the vicinity of 1, and naturally the efficiency disturbance does not match between the high speed region and the low speed region due to the influence of the elastic arrangement. Since the disturbance also occurs, the idea is to selectively switch one of the two transmission modes in the middle of the variable range for transmission.

  The second problem to be solved by the present invention is that, in a variable diameter transmission wheel, speed ratio control is performed when pressure is supplied, torque control is performed when elastic force is supplied, and the force and elastic force are switched by one command to each transmission wheel. Since the role of the upper control function can be selected, the idea is to selectively switch the transmission mode by synchronous switching of the pressurization mode to both the input and output vehicles.

  The third problem to be solved by the present invention is to suppress the friction force of the input vehicle in the high speed ratio range and the excessive friction force of the output vehicle, and at the same time, the friction force of the input vehicle and the output vehicle in the small speed ratio range. It is intended to provide a variable transmission with optimum transmission efficiency in the entire shift range by suppressing the shortage of frictional force.

  The fourth problem to be solved by the present invention is that when the above third problem is realized, an individual operation mechanism capable of discriminating the applied pressure and the elastic force is provided on one side of the input / output vehicle, and the applied force and the elastic force are identified on the other side. The idea is to provide a variable transmission that achieves high efficiency by arranging simple composite pressure mechanisms that can be supplied.

  The fifth problem to be solved by the present invention is to provide inelastic pressurization for accurately positioning the pulley V-groove on one or both of the input vehicle and the output vehicle of the continuously variable transmission, and absorption settling such as error and vibration. The idea is to provide a variable transmission that achieves high-efficiency transmission with an individual operation mechanism that can identify and supply the elastic force according to the rotational speed and torque command from the adjusting device.

  The sixth problem to be solved by the present invention further simplifies the fifth problem described above, and provides a simple and lightweight inelastic pressure force and elastic force by an elastic body for one or both of the input / output vehicles. The idea is to provide a variable transmission that achieves high efficiency with a pressurizing mechanism that can be identified and supplied in accordance with the control command.

  The seventh problem to be solved by the present invention is that both the speed ratio and the torque are stable for the stable transmission to the load equipment when the first and second transmissions are switched or the elastic force to each transmission wheel and the synchronous switching of the applied pressure. This is a concept that requires press switching, and in particular, completes the switching operation in a constant value state based on the speed ratio or output rotational speed.

The common problem of the present invention is that the operation mode of the input and output vehicles of the variable transmission is the torque and speed ratio transmission mode, respectively, and the operation is switched in the middle of the speed ratio and torque transmission mode and variable range, respectively. As a result, the transmission band is expanded and highly efficient transmission is achieved.
The first solving means of the present invention requires the variable transmission to share the function of torque and speed ratio control to the input and output vehicles, respectively, but the first transmission in which the input and output vehicles share the speed ratio and torque control. In contrast to the motive, the second transmission that shares torque and speed ratio control has a difference in transmission efficiency, so that the transmission is combined with the efficiency advantage of both vehicles.

  The second solving means of the present invention includes a pressurizing device that supplies elastic force to the input vehicle and supplies pressure to the output vehicle, and a pressurizing device that supplies elastic force to the input vehicle and pressurizes the output vehicle. The configuration is such that the pressurization mode is synchronously switched between the input / output vehicle according to the speed ratio or torque command in the middle of the device and the variable range.

  The third solving means of the present invention includes a first transmission device that provides a following vehicle function to the input vehicle of the continuously variable transmission and a reference vehicle function to the output vehicle, and further follows the reference vehicle function to the input vehicle and the output vehicle. And a second transmission device having a vehicle function, and each operation device switches the operation function of each vehicle in the middle of the shift range.

According to a fourth solution of the present invention, one of the movable wheels of the input / output vehicle is an individual controller in which two compression devices individually connect the elastic device and the contact device in series, and the other is a single compression device. the parallel body of the contact device respectively synchronized with identifying operating device in series connection with a configuration in which switching the operating functions of each car.

According to a fifth aspect of the present invention, there is provided a first pressurizing device in which an elastic device and a first compression device are serially superimposed on one or both of movable vehicles of an input / output vehicle, and a contact device and a second compression device connected in series. the second pressure device and having adjusting device is configured to apply a separate operating device for individually supplying s elasticity and pressure respectively.

According to a sixth solving means of the present invention, a composite pressurizing device is provided in which one or both of the movable vehicles of the input / output vehicle is superposed in series with the elastic device and the compression device, and the contact device and the elastic device are connected in parallel. it is configured to apply the identification supplying identification manipulator elastic force range and pressure range shift area corresponding to the command.

  The seventh solving means of the present invention switches the servo control between the direct control of the output vehicle and the indirect control of the input vehicle based on the detection value of the detector of the speed ratio or the output rotation speed, Each command is controlled or compensated and applied so that the speed ratio and torque can be switched to bumpless before and after switching.

  Although it is possible to secure the variable control of the output torque of the variable transmission by supplying the elastic force directly to the output vehicle, in the present invention, the elastic force can be supplied to the input vehicle and indirectly controlled by the output friction pressure via the belt. Therefore, there is a way for any configuration to be arbitrarily selected with the output shaft torque as an established form. Therefore, both the input and output vehicles can suppress both shortage and excess of frictional force. As a result, optimum torque can always be applied in any variable range, so a highly efficient and wideband variable range is achieved. This has the advantage of having a constant horsepower transmission variable transmission.

  Especially in a variable transmission using a variable diameter transmission vehicle, the efficiency deterioration form is different between the low speed range (high speed ratio range) and the high speed range (small speed ratio range), but the transmission mode of the first and second transmissions is different. By selecting or synchronously switching the pressurization mode between the applied pressure and elastic force to the input / output vehicle, it is possible to always apply the optimum torque, so depending on the load even at high load torque or low load torque Since the pulley friction force can be managed with high accuracy, there is an advantage that the stable transmission by applying the output torque can always be stably achieved, and at the same time, the high speed shift responsiveness can be guaranteed.

  In particular, even tension type belts that tend to cause so-called entanglement phenomenon in which the belt bites into the pulley do not become unable to transmit, and are stable regardless of changes in ambient conditions such as belt pulley material, wet dry lubricity, temperature, etc. As a result, it is possible to create a stable friction transmission without taking any additional measures to prevent entrainment such as the conventional unstable cam mechanism. Increase / decrease in belt contact radius occurs in the input / output vehicle, and each controller has the ability to switch the function of the reference vehicle or the following vehicle to the corresponding pulley. Therefore, in the fields of vehicles, power receiving facilities, etc., there is an effect of realizing a highly efficient transmission with low fuel consumption, low price and low driving cost.

Furthermore, since the transmission of the present invention can be individually operated with the torque input controller and the speed ratio with the output controller, the synchronous operation of both can achieve constant horsepower transmission, only one of them can be variably operated and the other can be operated fixedly. As a result, there is an advantage that it can be used for both a constant torque transmission and a torque conversion transmission. At this time, if the elastic force is kept high for a long time when the transmission is stopped, the transmission member such as the belt pulley and the elastic body will be deteriorated, and the deterioration prevention measures can be taken to forcibly remove the elastic body when the transmission stops. There is.
In addition, the structure and installation position of the pressurizing device can be simplified to select a simple and lightweight form, or by using a pressure transmission device, the transmission can be reduced in size and weight at the same time.

  Furthermore, when the two transmission modes are switched in the middle of the variable range, the rotational speed of the input / output vehicle is detected and the switching is executed based on the speed ratio or output rotational speed, and the speed ratio or output rotational speed is a constant value. Because the operation switching operation is completed while the vehicle is in the state, there is no impact on the interlocking load device regardless of the transmission mode change, and the result is that stable and safe transmission is guaranteed as required by the load. There is an advantage that bumpless switching control is always realized.

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. The present invention may be applied to particular constant horsepower transmission type variable transmission device to but speed ratio control exhibited greater potency only by the single operation constant torque transmission variable Den motives. 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 between the applied pressure and the elastic force. Both may be a pressurization method using an individual pressurization device, the input side may be a pressurization method using a composite pressurization device, and the output side may be a pressurization method using an individual pressurization device. At this time, the preliminary pressure of FIG. 6B may naturally be variably controlled to the output vehicle, and it is not always necessary to give it. 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 between the pressure and elastic force of the operating device, an example of switching at the speed ratio ε = 1 has been shown, but switching may be performed at an arbitrary speed ratio, and the output rotation is not the speed ratio but the reference of the switching operation The number or the output torque may be switched as a reference. In this case, it is desirable that the output rotational speed and torque are instantaneously switched by bumpless. 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 the switching should be performed simultaneously, and it is natural that the command should be controlled by discriminating and selecting the rotation speed command for speed increase / deceleration and the torque command for pressure increase / reduction. Therefore, the compensated rotational speed command should be identified and supplied for the belt pulley friction surface degradation, and the compensated torque command should be identified and supplied for the elastic body degradation.

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 another hoisting machine, a hydraulic jack, a cam mechanism, or the like 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. Shared control motor output driving source has shown an example of individual arrangement for each pressure device input and output side, the driving source using a known transfer machine or gear synchronization fitting device such as a changeover device The motor type may be an AC or step motor. It should be noted that the simultaneous pressurizing device for the movable vehicle and the elastic body may have a configuration that is proportional or inversely proportional between the compression device operation amount and the disc wheel relative distance and inversely proportional or proportional between the elastic body and the elastic force. Each operation device may have each compression device individually or in common with each of the first and second pressure devices.

In a pressurizing device having the motor and the compression device, long-term high-precision positioning and pressurization value 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 a hoisting / sliding device such as a screw or a cam, the hoisting pitch, the rotational direction, and the thread groove machining direction such as a right screw / left screw A known element such as a gear 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 maintaining high accuracy and giving priority to high speed response of gear shifting operation, the belt circumference or elastic body deterioration error is periodically sensed and stored in advance in each rotational speed or torque command according to the amount of deterioration. The compensation amount is set to
In consideration of the calculation, the input and output operating devices may be fed back to the detected value of the substantial rotational speed or friction pressure, and servo-controlled in a closed loop. Further, when high-precision management of torque and speed ratio is required, each detected value is substantially compared with a reference value determined in advance, and negative feedback control is supplied to each input or output side controller. To achieve extremely high-efficiency long-term operation.

1 to 6, a variable transmission 10 includes a transmission device 10A composed of a belt 3 applied between an input wheel 1 and an output wheel 2, and an input operation device 9 and an output operation device 8 on the same plane side. It is comprised with the transmission control apparatus 10B adjusted with the adjustment apparatus 90 shown in FIG. In this example, the input operating device 9 has an individual pressurizing device 50 composed of the first and second input pressurizing devices 11 and 51, and the output operating device 8 has a combined pressurizing device 40 composed of the output pressurizing device 21. It is energized by the drive source 60 shown in FIG. Each pressurizing device 11, 51, 21 has a compression device 14, 54, 24, respectively, and operates the input elastic device 31, the input contact device 35, and the output composite device 20, respectively. The input operating device 9 is connected to the input wheel 1 by the first and second input pressurizing devices 11, 51.
Thus, the adjusting device 90 is individually provided, and the output operation unit 8 has the ability to identify and supply the elastic force and the pressurizing force to the output wheel 2 according to the speed ratio with a single pressure device 21. In addition, since there are substantially equivalent functional parts on the input / output side, in this specification, when it is necessary to distinguish between “input” and “output” for each part name, it is omitted when it is understood by the preceding and following descriptions and drawings.

The transmission 10A is a variable-diameter pulley 1 and 2 in which the movable wheels 1a and 2a and the fixed wheels 1b and 2b are opposed to each other, and the former is slidable in the axial direction relative to the latter via a key.
Are arranged in opposite directions on the input shaft 1c and the output shaft 2c, respectively. The pulleys 1 and 2 rotate while being supported by a pair of bearings 7 and 6, respectively, while further separating the rotational force between the main body 10 and the movable wheels 1a and 2a by the pair of bearings 5 and 4, respectively. The pressurizing devices 11, 51 and 21 respectively pressurize the pulley movable wheels. 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. 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 by a tension belt 3 having a structure. 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 makes the corresponding transmission wheel function as a reference vehicle function, and the elastic force supply makes the corresponding transmission wheel function as a 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. In the following vehicle function, even if error factors such as belt / pulley contact surface friction or internal / external disturbance vibrations occur, the specified friction force is always maintained between the two regardless of the positioning control described above, and the error factors are normally transmitted. This is a function for determining the shaft torque of each axis by performing the self-setting or automatic centering function for instantaneously returning to the state by the action of elastic force.

  In this example, the input operating unit 9 includes a first input pressurizing device 11 for supplying pressure to the input wheel 1 and a second input pressurizing device 51 for supplying elastic force, respectively. It consists of an input pressurizing device and drive sources 60a and 60b. The first pressurizing device 11 has a series structure of the contact device 35 of the input switching device and the first compression device 14, and the second pressurization device 51 has a serial structure of the elastic device 31 and the second compression device 54, respectively. Both are configured to 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 compression devices 14 and 54 are arranged in cascade on the same axis. The Therefore, the pressurizing form of each pressurizing device is that the device 14 transmits pressure to the elastic device 31 from the inner wall of the second main body 10b and the device 54 from the outer wall to the elastic device 31 via the pressure transmitting device 70 of FIG.

  The compression devices 14 and 54 of the pressurizing devices 11 and 51 are both composed of sliding devices 13 and 53 and biasing devices 12 and 52 for biasing the sliding devices 13 and 53. Each sliding device 13, 53 has two sliding tools 16, 17, 56, 57 and a pressing device 15, 55 that slides between both, and is a ball screw in this example. The sliding device 13 is formed in a tubular shape, and the 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 urging devices 12 and 52 are both worm transmissions including worms 18 and 58 and wheels 19 and 59 in this example, and commands are input to the shafts 18a and 58a to position the sliding devices 13 and 53 once. Even if the supply of control commands is stopped, it performs a self-locking function that maintains the position. The 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 pressure device 51, the sliding tool 56 moves up and down.

  The abutting device 35 of the first pressurizing device 11 is composed of two sliding members 36 and 37 arranged via a gap 38, and abutting operation for abutting the two according to the selection of the operation command of the compressing device 14. The time and the contact release time for separating the two are controlled by the control command of the adjusting device 90. During the contact operation, the 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. When the contact is released, the gap 38 is generated and the compression device 14 does not act on the input wheel 1. In this example, the sliding material 37 is shared with the sliding tool 17 of the 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 second pressurizing device 51 includes 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. Are arranged concentrically. 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 compression device 51 and compresses the elastic body 32 in series and supplies the elastic force generated simultaneously through the sliding body 34 and the bearing 5. At this time, the vehicle 1 performs the function of the following vehicle of the variable pressurization control. Accordingly, the pressure applied by the first pressurizing device 11 and the elastic force of the 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 of FIG. 2 is connected to the end portion 56a of the sliding tool 56 of the compression device 54, and is a second transmission device that doubles as a first transmission means 71 and a sliding body 33 that extend symmetrically from the center receiving and pressing point. A lateral transmission means 78 composed of a transmission means 74, a longitudinal transmission means 73 composed of two pressure shafts 72 connected to both ends thereof and parallel to the axial direction of the sliding tool 56, and further for pressing the elastic device 31 A support device 79 including a bearing for smoothly guiding the sliding direction of the pressure shafts 72 and 72 and a main body through hole is formed. 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 shown in FIG. 3 is configured such that a single output pressurizing device 21 supplies a pressing force supply of the first pressurizing device and an elastic force supply of the second pressurizing device to the output wheel 2 by a drive source 60c. Both are identified and supplied in response to the control command. Unlike the operation device 9, a composite pressurizing device 40 in which the composite device 20 in which the output elastic device 41 and the output contact device 45 as an output switching device are assembled in parallel is further assembled in series by a single output compression device 24. It has an output pressurizing device 21. The compression device 24 includes a sliding device 23 including two sliding tools 26 and 27 and a pressing device 25 for the ball screw 26a, and further includes a worm transmitting device urging device 22 including a worm 28 and a wheel 29 and having a self-locking function. . The difference between the compression devices 24 and 54 is that the sliding device 53 is pressurized with a right-hand screw but the sliding device 23 is pressurized with a left-hand screw, and the sliding tool 56 moves up and down without rotation. Since the moving tool 26 rotates and moves up and down, a bearing 49 is arranged, and the entire compression device 54 is installed in the main body 10b so as not to vibrate. In the compression device 24, only the sliding device 23 is a transmission wheel. 2 and the elastic device 41 are supported in an interlocking state or floating state capable of transmitting elastic vibration, and the sliding tool 26 is slidable in the axial direction between the wheel 29 of the urging device 22 and a spline coupling 26c. Has been extended to enable 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.

  It should be noted that the pressurizing device 21 is composed of a longitudinal transmission means 83, a lateral transmission means 88, and a support device 89 having the same structure as the pressurization device 51, and has a rectangular frame pressure transmission device 80 symmetrically, so that similar reference numerals are given. Omit. 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 10 d of the pressurizing 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 appropriately sense not only the applied elastic force or applied pressure but also the value of the friction force on the output friction transmission surface during constant speed ratio operation, and to perform negative feedback control of the torque by the friction pressure.

As shown in FIG. 4, the operation devices 8 and 9 individually apply drive sources 60 a, 60 b, and 60 c to the pressurizing devices 11, 51, and 21, respectively, and individually supply control commands from the electronic adjustment device 90. . 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 memory 97 is composed of three processing information, the memory 97a is the control information when the pulley 1 is operated as the following vehicle function and the pulley 2 is operated as the reference vehicle function, and the memory 97b is the pulley 1 as the reference vehicle function and the pulley 2 follows. The control information when the vehicle functions is operated, the memory 97c is a constant torque type transmission when each of the pulleys 1 and 2 is operated synchronously and when each of the operating devices 8 and 9 is individually operated independently. The control information of the torque conversion type transmission is stored in advance. The filter 99 removes elastic vibration components from the elastic force. Each device of the drive source 60 and the adjusting device 90 described above is already disclosed in, for example, Sanyo Denki Co., Ltd. “1998-99 Servo System General Catalog” and the like, and is 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 will be described. That is, in the high speed ratio range where ε> 1, the first transmission device, that is, the first transmission device A, which has the following vehicle function for the input vehicle 1 and the reference vehicle function for the output vehicle 2 and is individually operated, In the small speed ratio range of ε <1, both the operation is performed so that the input vehicle 1 is operated by the second transmission device, that is, the second transmission device B, which is provided with the reference vehicle function as the output vehicle 2 and the following vehicle function as the output vehicle 2. The operation modes of the 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 the time of start-up, the maximum friction ratio is applied to the input wheel 1 by the maximum compression pressure of the elastic body 32 because of the maximum speed ratio εmax of FIG. The maximum frictional force 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 is supplied through the bearing 49, the 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. Therefore, the frictional force 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 abutment device 35 is reduced on the input vehicle side, but there is no influence, and the elastic body 32 is compressed by the compression device 54 As a result, the compression is reduced to P11 as shown in FIG. 6A, so that the supply elastic force as the torque command is reduced and the input friction force is also reduced. On the output vehicle side, the frictional force due to the belt tension decreases, so the output frictional force is also reduced to P01, and the simultaneous compression device 21 keeps the composite device 20 as it is, and the relative displacement is only between the sliding tools 26 and 27 of the compression device 21. Then, the movable vehicle 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 pressure reduction due to 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. It is preferentially switched to a pressure of 35. At the same time, on the output side, the slidable tool 26 is raised by the action of the urging device 22 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 slid. It is transmitted to the vehicle 2 through the moving 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 state of the output wheel 2 and the pressurizing device 21 with the speed ratio εs 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, both the compression devices 14 and 54 may be always driven, but it is not always necessary to do so. The compression device that does not affect the vehicle 1 may stop and wait for the supply of control commands during that period as in the case of the left sliding body in FIG. Further, 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 a long period of high compression pressure, there is a possibility that the predetermined frictional force 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, depressurization or pressurization that forcibly releases or pressurizes high pressurization of the pressurization devices 51 and 21 from the adjustment device 90 to low pressurization. A pressure command can be given to prevent aged deterioration by forced release during long-term shutdown. 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 pressurization control of the input operating device 9, but in order to guarantee a highly accurate desired friction force in the output wheel 2 even when the elastic bodies 32, 42 deteriorate, A detector 94 is used for torque calculation. Even when the output vehicle 2 works as a reference vehicle function, an elastic force may be supplied, and the wedge frictional force can always be detected by the same detector, so that the servo control may naturally be performed. The torque compensation control when the frictional force is reduced may be obtained by knowing the torque from the detected value of deterioration of the elastic body 31 in advance and servo-controlling the input operating unit 9 so as to be suitable for the frictional force determined by the CPU 95 and the memory 97a. By further performing open loop or closed loop control, it is possible to achieve any use of torque control with a predetermined frictional force supply. The same applies to the case where the rotational speed detector 93 is used when the output rotational speed is controlled by the indirect positioning control of the input operating device 9.

  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, the elastic force is not applied at all except during the speed change operation, or the elastic force Ps that is slightly variably controlled is applied. The transmission failure due to the belt winding phenomenon due to the external pressurization of the belt 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 first transmission device A in the high speed ratio region and the second transmission device B in the small speed ratio region are not simply connected stably, but both the speed change regions are greatly expanded while maintaining a wide band. In order to establish a stable maintenance of the desired frictional force, it achieves a high-speed shift response and also achieves a high-efficiency transmission in both end regions of the shift region. 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 differs from the first embodiment only in the configuration of the input operation device 9 and is substantially the first and second transmission devices A and B.
The variable torque control and the variable diameter positioning control operation by the function switching are completely 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 the input operating device 9 forms the input pressurizing device 11 of the composite pressurizing device 50 ′ by connecting the single compressing device 14 and the composite device 30 in series like the output operating device 8. is there. In the composite device 30, the elastic device 31 of the second input pressurizing device 51 and the contact device 35 of the first input pressurizing device 11 are preliminarily compressed and assembled in parallel. In this example, the sliding tool 17 of the 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 shared, and unlike the composite device 20, both ends are closed in a compressed state. It forms a 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 frictional force characteristics in FIGS. 6A and 6B, the input elastic body 32 is responsible for the high pressurization area characteristic Ps1 and the output elastic body 42 is responsible for the low pressurization area 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, the contact device 35 generates the gap 38 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 frictional force 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 unit 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 frictional force 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 frictional 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 given by the elastic frictional force 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 force 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. Further, even if the input wheel 1 is provided with the operation device 9 of FIG. 10 and the output vehicle is provided with a constant speed ratio pulley (not shown), the idea of adjusting the output torque with the input operation device 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.

1, 2 Pulley 3 Belt 8, 9 Operator 10 Variable transmission or main body 11, 21, 51 Pressure device 12, 22, 52 Biasing device or worm transmission 13, 23, 53 Sliding device 14, 24, 54 Compression device 15, 25, 55 Press device 30, 20 Composite device 31, 41 Elastic device 35, 45 Contact device or switching device 40 Compound press device 50 Individual press device 60 Drive source 70, 80 Pressure transmission device 90 Adjustment device 92, 93 Second detector or rotational speed detector 94 First detector or pressure detector

Claims (10)

An endless V-belt is arranged between the input and output wheels made of a variable diameter wheel, and friction transmission is carried out by an input and output operation unit that performs speed ratio control when supplying pressure to the variable diameter wheel and performing torque control when supplying elastic force. In variable transmission,
The first input or output vehicle performs the torque and speed ratio control by the elastic force or pressure supply of the second input or first output pressurizing device, respectively, and the second input or output vehicle is the first input or Operation between the first transmission and the second transmission in the middle of the variable range, and the second transmission that achieves the speed ratio and torque control by the pressurizing force or elastic force supply of the second output pressurizing device. A variable transmission comprising an adjusting device for switching. An endless V-belt is arranged between the input and output wheels made of a variable diameter wheel, and friction transmission is carried out by an input and output operation unit that performs speed ratio control when supplying pressure to the variable diameter wheel and performing torque control when supplying elastic force. In variable transmission,
A one pressurizing device that combines a second input pressurizing device that supplies elastic force indirectly to the input vehicle via a one elastic device and a first output pressurizing device that supplies pressure directly to the output vehicle; A second input pressurizing device that combines a first input pressurizing device that supplies pressure directly to the input wheel and a second output pressurizing device that supplies elastic force indirectly to the output vehicle via the other elastic device; Further, the input and output vehicles each have an adjustment device that switches the pressure between a first variable band that performs torque and speed ratio control and a second variable band that performs speed ratio and torque control, respectively, in the middle of the variable range. A variable transmission. An input and output vehicle composed of a movable vehicle and a fixed vehicle, an endless V-belt provided between the input and output vehicles arranged in opposite directions to the input and output shafts, and an input provided in the input and output pressurization devices, respectively. And an input / output operation unit for displacing the movable vehicle of each corresponding vehicle corresponding to the output compression device by a driving source, and further, the input and output elastic bodies are supplied with the input and output for supplying elastic force to each corresponding vehicle. In variable transmissions consisting of input and output elastic devices respectively in the device,
Each of the corresponding vehicles has a first input / output pressurizing device for applying pressure to each compression device and a second input / output pressurizing device for applying elastic force to each elastic body via a series. The input and output pressurizing device for discriminating and supplying elastic force or pressurizing force, the second input pressurizing device to follow the input vehicle function, and the first output pressurizing device to the output vehicle as a reference vehicle The first transmission that performs the function by the operation of each operation device, the reference vehicle function for the input vehicle with the first input pressurizing device, and the vehicle function for following the output vehicle with the second output pressurizing device And the corresponding vehicle of the first transmission and the second transmission by synchronously switching the operation modes of the two operation units in the middle of the variable range. Suppose output speed or speed ratio command and output torque command to the above input and output actuators for variable control Variable Den motive made and a that adjusting device. An input and output vehicle composed of a movable vehicle and a fixed vehicle, an endless V-belt disposed between the input and output vehicles opposite to each other on the input and output shafts, and an input and output pressurizing device are provided for each corresponding vehicle. In a variable transmission consisting of input and output actuators that move a movable vehicle with a drive source,
A first pressurization device in which the first compression device presses the contact device in series and performs a reference vehicle function by applying pressure, and a second pressurization device in which the second compression device presses the elastic device in series and performs a follower vehicle function by elastic force A separate pressurizing device that individually supplies the functions to the corresponding vehicle according to a speed ratio and a torque command, and a contact device and an elastic device in which a single compression device is pressed in series are further connected in parallel to each other. The abutment device is capable of compressing displacement of the elastic device during the abutment operation and disabling at the time of abutment disengagement, and a composite pressurizing device for discriminating applied pressure and elastic force to a corresponding vehicle according to a control command; Further, one of the input and output pressurization devices is the individual pressurization device and the other is the composite pressurization device, and the input and output operation devices are the reference vehicle function and the follower vehicle, respectively. the input and output in order to middle synchronized switching of the variable regions between features Variable Den motive made and a regulating device for controlling the operation device. An input and output vehicle composed of a movable vehicle and a fixed vehicle, an endless V-belt provided between the input and output vehicles arranged in opposite directions to the input and output shafts, and an input and output pressurizing device are provided for each corresponding vehicle. In a variable transmission consisting of input and output actuators that move a movable vehicle with a drive source,
A first pressurizing device for applying a pressure applied to the movable vehicle of the corresponding vehicle by a variable diameter positioning control by applying a pressing force generated by the first compressing device in series pressing the contact device at the time of shifting; and a second compressing device; A second pressurizing device that constantly applies the elastic force generated by pressing the elastic device in series and gives the following vehicle function by variable pressurization control to the movable vehicle of the corresponding vehicle; and further, the input or / and the output vehicle The above input or / and output operation unit having the individual pressurizing devices juxtaposed with the first and second pressurizing devices, and each corresponding vehicle is switched and selected between the reference vehicle function and the following vehicle function in the middle of the variable range. A variable transmission comprising: an adjustment device that applies a speed ratio and a torque command to the drive source in order to achieve the above. An input and output vehicle composed of a movable vehicle and a fixed vehicle, an endless V-belt provided between the input and output vehicles arranged in opposite directions to the input and output shafts, and an input and output pressurizing device are provided for each corresponding vehicle. In a variable transmission consisting of input and output actuators that move a movable vehicle with a drive source,
An elastic pressure device that presses the compression device and the elastic device in series and supplies elastic force; and an inelastic pressure device that presses the compression device and the contact device in series and supplies pressure. A combined pressurizing device for discriminating the applied pressure and the elastic force by making the compression displacement of the elastic device made impossible at the time of contact operation and enabling at the time of contact release, and a control command for the input or / and output vehicle The input or / and output actuator having the above-described combined pressurizing device for discriminating the applied pressure and elastic force in accordance with the function and switching the reference vehicle function and the following vehicle function, respectively, and the composite pressurizing device further includes the input or / and output vehicle. And a control unit for supplying the control command to the drive source for discriminating and switching between the pressure supply region for the reference vehicle function and the elastic force supply region for the following vehicle function in the middle of the variable region. Transmission. In a variable transmission that performs friction transmission by an input and output pressurizing device that pressurizes each movable vehicle of an input and output vehicle wound with an endless V-belt by a command of a drive source,
The input pressurizing device having first and second input pressurizing devices that respectively perform speed control and torque control by supplying pressure and elastic force to the input vehicle, and a speed ratio by supplying pressurizing force and elastic force to the output vehicle. And the first and second output pressurizing devices that respectively perform torque control, a first detector that obtains a speed ratio from the detected rotational speed values of the input and output vehicles, and further in the middle of the variable range When switching the speed ratio, the speed ratio control is performed based on the numerical value of the output speed, and the function control of each servo control is effected between the direct control of the output vehicle and the indirect control of the input vehicle. A variable transmission having an adjustment device that controls or compensates for a speed ratio and torque by a speed ratio and a torque command switched and supplied between the controls. 6. The control device according to claim 1, wherein the adjusting device selectively switches the switching operation performed by the variable transmission in the middle of the variable range when the speed ratio is 1 or in the vicinity thereof. Variable transmission. 9. The input / output pressurizing device according to claim 8, wherein the input / output pressurizing device controls the supply or shut-off of the pressurizing force to the input / output vehicle according to the contact or release state of the gap between the two sliding members. Variable transmissions that have devices as switchers and are synchronized with each other. 8. The pressure adjusting device according to claim 1, wherein the adjusting device is configured to apply a high pressure and a low pressure to release a high compression state of each elastic device when the variable transmission is stopped. A variable transmission in which at least the input or output pressurizing device is subjected to a decompression and pressurization command forcibly switching between them.