JP2011174616A - Adjustable transmission machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To achieve a transmission mechanism which enables error compensation of speed ratio or torque depending on an ambient air temperature change or a secular change by carrying out an independent operation besides a synchronous operation of speed ratio and torque as well as efficiency compensation to an excessive friction force or an insufficient friction force in a low speed area and a high speed area because two control functions for output rotation number, speed ratio, and torque are indispensable in the belt driven variable transmission of constant horsepower transmission type. <P>SOLUTION: In the adjustable transmission machine, two control functions for speed and torque are arranged mutually at two pressure units for pressurizing input and output vehicles, and for a speed ratio and a torque, different order supply paths are employed for order supply from a regulator to a belt pulley movable vehicle for complete separation and segmentation. Furthermore, the operation order for releasing the high compression state of the elastic body during stop of transmission is enabled in addition to the error compensation of speed or torque. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

The present invention relates to a variable transmission for use in general industrial machines, vehicles, electric motors, etc., and more particularly to a variable transmission that achieves frictional force stabilization and broadband high-efficiency transmission by identifying and supplying elastic force and applied pressure to a pulley and command control mode. .

The operation of the constant horsepower belt continuously variable transmission is under development in US Pat. No. 4,973,288 or US Pat. No. 5,269,726, but 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 two pulleys of an input / output vehicle in European Patent Application EP0931960A2. However, some unresolved issues remain. The first is the instability in which the frictional force between the belt and pulley of the input / output vehicle is out of balance, and the second is the problem of 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 estimated 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 is the cause, and the control mode is enhanced It is desirable to take measures.

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 force applied to the variable-diameter wheel is the elastic force of the speed ratio, and the torque control function is performed. For the command supply system that is divided into multiple commands such as ratio or output rotation speed command and torque command and individualized by each control element, it provides a variable transmission that achieves high efficiency transmission and long-term stable transmission, and elastic body torques as necessary While having a control action, the high pressurization causes the transmission member to be deteriorated, thus providing a preventive measure by command operation.

The first problem to be solved by the present invention is that when the two control functions of the speed ratio and the torque are individually applied to the two pressurizing devices of the input and output vehicles, the command supply of the adjusting device is also separated from the other control functions. This is a transmission control concept according to speed ratio versus contact radius / friction force characteristics that are individually servo controlled.

  The second problem to be solved by the present invention is that constant horsepower transmission requires rotational speed (speed ratio) control and torque control as described above in relation to the transmission relational expression, and the output rotational speed control is performed from the adjusting device to the first and second pressurizing devices. This is the idea of transmitting pressure commands and elastic force commands for controlling output torque in parallel to input or output vehicles for transmission.

  The third problem to be solved by the present invention is that when the pressure ratio is controlled by one force of the input / output vehicle and the torque is controlled by the elastic force by the other force, the elastic force supply side transmission vehicle rubs after the command supply stops. The idea is to stabilize the frictional force between the two cars because the force becomes excessive and the balance of the frictional force is lost, leading to unstable transmission.

A fourth problem to be solved by the present invention is that the adjusting device gives a control command such as a speed ratio or a torque command to the variable diameter wheel in the form of a pressure or elastic force command, but other commands using each command pressurization system in common. The idea is to switch the operation and stop of the first compression device or to release the high compression elastic body while the transmission is stopped.

  The fifth problem to be solved by the present invention is that the speed ratio control and the torque control of the input / output vehicle are shifted synchronously. However, the speed ratio control side transmission vehicle has no elastic force at the time of high load torque, and there is insufficient frictional force. It is an idea that prevents unstable transmission and inability to transmit due to excessive frictional force, and maintains the balance of frictional force in both cars.

  The sixth problem to be solved by the present invention is that when a speed ratio and torque control of an input or output vehicle is performed with a variable diameter vehicle, a pressure system path and an elastic force system path are simultaneously installed in a narrow space around the variable diameter vehicle. In addition, the command signal of the second pressurizing device is formed in an annular shape, and there is no cause of erroneous signals to each other, and the individual control is performed in a concentric circle arrangement.

The seventh problem to be solved by the present invention is that when the first and second compression devices are centrally arranged around a variable diameter vehicle for speed ratio and torque control with an input or output vehicle, one of them is annularly formed with an elastic device. The idea is to take measures by penetrating the rotating shaft so that the three members including the variable diameter wheel are arranged coaxially and concentrically.

  The common solution of the present invention is to separate the command supply from the adjusting device to each transmission vehicle into a speed ratio command system path and a torque command system path, and to pressurize all the pressurization devices such as a drive source, a compression device, and an elastic device. The command supply path is configured so that other commands such as a depressurization command can be shared as needed.

  The first solving means of the present invention is to provide the speed ratio and the torque command which are separated and supplied to each other through the first and second drive sources respectively applied to the first and second compression devices which are controlled by the adjusting device to control the speed ratio and torque. By direct application, servo control is performed so that the speed ratio or torque can be independently operated, and high-efficiency operation is performed in accordance with a predetermined speed ratio vs. output friction pressure characteristic.

  The second solving means of the present invention is to install an elastic body on one side of the input / output vehicle and a first pressurizing device for speed ratio control and a second pressurizing device for torque control on the other side, In this configuration, the elastic force is balanced by both elastic forces, and the speed ratio command and torque command from the adjusting device are transmitted individually while balancing the frictional forces.

  The third solving means of the present invention is to apply a pressure command to one of the input / output vehicles and an elastic force command to the other and supply an elastic force from another elastic body to the transmission vehicle for supplying the pressure to both input / output vehicles. In this configuration, the other elastic body is variably controlled so that the elastic force is properly applied to the frictional force and the balance of the frictional force is not constantly lost.

The fourth solution of the present invention is to control the presence / absence of pressure supply and select an operation command to the first compression device to select simultaneous supply or single supply of pressure force and elastic force, or high compression while the transmission is stopped. In order to release the pressurization of the elastic device in the state and pressurize it at the time of start-up, a depressurization command is given to the second compression device.

  The fifth solving means of the present invention is that an adjustment device is provided by separately arranging a second pressurizing device that further performs a torque control function by supplying elastic force to a transmission wheel having a first pressurizing device that performs a speed ratio control function. By applying individually controlled torque commands to both the input and output vehicles, it is possible to achieve high-efficiency transmission against load torque fluctuations.

  The sixth solving means of the present invention is that the elastic device and the sliding device of the first or second compression device are formed in an annular shape and arranged coaxially and concentrically with each other, thereby providing the speed ratio and torque command applied by the adjusting device, respectively. In this configuration, both the command after signal conversion into the pressure and elastic force commands are applied in parallel to the axial direction along the pulley rotation axis.

  The seventh solving means of the present invention comprises three members, an annular sliding device, an annular elastic device, and a variable diameter wheel rotating shaft when the first and second pressurizing devices are simultaneously installed around the variable diameter wheel. Are arranged coaxially and concentrically to each other, and the pressure command and the elastic force command are individually supplied in parallel with each other through the rotating shaft.

  The present invention relates to a command supply path for an adjusting device applied to a first pressurizing device for controlling the number of revolutions (speed ratio) required for constant horsepower transmission and the like, and a second pressurizing device for torque control. Since the command supply path leading to the stage is separated and identified as the speed ratio command supply path and the torque command supply path, first, there is no restriction when sharing both the pressurizers with a single command, and the synchronous operation Can also be selected by the adjusting device. Secondly, if the speed ratio and torque commands are shared, the structure of the pressurizing device will remain limited, but if the commands are separated, the adjusting device side will select the command operation direction and polarity arbitrarily. Third, it can eliminate the cause of error signals between the command supply paths and prevent the reversal and reversal of each command, and fourth, error compensation and prevention of deterioration in addition to the adjustment command in the speed ratio or torque command supply path Other commands can be given, and fifth, a single movable vehicle is supplied with pressure and elastic force simultaneously Or the simultaneous supply of pressure to the input and output wheel both have effects such as, but leads to inability transmission simultaneous supply of an elastic force plays a good high efficiency transmission.

  In particular, (1) If both speed ratio and torque control functions are placed on any of the output vehicles that have input, constant horsepower transmission, constant torque transmission, and torque conversion transmission can be realized in synchronism or single operation, and the speed ratio and torque Since the compensation calculation can be managed instantaneously and with high accuracy, stable transmission and high-efficiency transmission are always guaranteed for a long time. (2) If the first and second pressure devices are installed side by side in one movable vehicle, either the speed ratio or torque control function can be selected by the adjustment device, or both can be supplied simultaneously. Since the torque control can be performed individually on both the output cars at the same time, high-efficiency transmission is achieved by high-accuracy torque management of both cars at all times. Realize. (3) Since one or both elastic devices of the input / output vehicle can absorb the error factor generated inside and outside instantly and return to stable transmission, the next shift operation is promoted, and as a result, a high-speed shift response can always be secured. . (4) When the first and second pressurizing devices are applied to both of the two transmission wheels, a first transmission mode in which the input and output vehicles respectively control the torque and speed ratio, and a second transmission mode in which the speed ratio and torque are controlled, respectively. As a result of the two types of transmission being achieved by a single transmission, when a more efficient transmission band is selected from both forms, a remarkably broadband high efficiency transmission is realized.

In addition to the above, the advantages of separately dividing multiple control elements are as follows: (a) The belt circumference elongation and belt pulley friction surface wear cause speed ratio and torque error factors, but these control elements are separated. Therefore, it is possible to compensate for errors using detectors such as rotation speed and friction pressure, etc. In addition to speed ratio error compensation, torque error compensation in the event of elastic deterioration of the elastic body is based on the idea of individually installing a pressure device. Realize. (B) When torque control is performed on both input and output vehicles, optimal torque control is always applied by supplying only two commands to the controller according to the load demand, such as during high load torque or light load torque. As a result, there is an effect that high-efficiency transmission is always achieved at both high and light loads.

(C) In addition to the speed ratio and torque, the control elements of the variable transmission have control elements such as an operation command that does not require variable and a decompression and pressurization command. In this case, the command supply system of the existing pressurization device It is also possible to give the operation of other functions by other commands by sharing the road. For example, in a transmission using an elastic body, the elastic body works effectively for giving torque control during operation, while the elastic force in a high pressure state accelerates the deformation deterioration of the transmission member including the elastic body during the stoppage. As a deterrent measure, the elastic body that is in a high pressure state at the time of stopping is released from high compression and a depressurization command to pressurize at the time of start-up is forcibly supplied to the elastic body pressure device to protect each transmission member and There is an advantage that the utility to achieve stable transmission works.

  In the present invention, in order to secure a predetermined output torque, the input vehicle is subjected to external variable pressurization control to obtain an indirect output friction force via the belt without depending on the direct external pressurization to the output vehicle. Any structure can be created, and it is possible to eliminate the shortage of frictional force in the input vehicle. Especially in continuously variable transmissions that use variable-diameter pulleys for input and output vehicles, when the contact radius or area between belt pulleys increases, the pulley pulleys do not supply substantial pressure to the pulley movable vehicle except during gear shifting operations. Since the frictional effect between the V-belt and pulley V-groove is indirectly generated based on the belt tension generated by the force, the instability of the friction coefficient that changes according to the external pressure is eliminated, and at high load torque Achieves stable and highly efficient transmission. 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.

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 system using an individual pressurizing apparatus, or may be of various pressurizing systems such as a pressurizing system using a composite pressurizing apparatus on the input side and an individual pressurizing apparatus on the output side. 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 the pressurizing force and elastic force of the operating device, an example of switching preferentially at the speed ratio ε = 1 has been shown. However, switching may be performed at an arbitrary speed ratio, and the standard of adjustment operation and switching operation is set. The output rotation speed or output torque may be adjusted or switched to a priority reference instead of the speed ratio. 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. The pulley for the standard vehicle function performs the rotational speed control and that for the following vehicle function performs the torque control, so when the function is switched, the speed ratio and torque command supplied from the adjusting device should be switched simultaneously. Obviously, the command should be controlled by discriminating and selecting the rotation speed command for acceleration / deceleration and the torque command for pressure increase / deceleration, respectively. Accordingly, the compensated rotational speed command should be identified and supplied for the belt pulley friction surface degradation of the transmission member and the compensated torque command should be identified 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. The input and output pressurization device switches the input and output contact devices that can control the presence or absence of pressure supply to each pulley movable vehicle according to the contact or release state of the two sliding members with or without the gap between them. It may be given as Note that each of the pressurizing means, such as a sliding tool, a sliding body, a sliding material, etc., may be shared and shared with each other or may be replaced with other transmission 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 second or input / output drive sources are individually arranged for each of the pressure devices on the input and output sides. However, the drive source can be shared or unified, and a known transmitter or A switching device such as a gear synchronous fitting device may be used, and 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, each pressurization command supply system of the controller is separated from each other and positive signal, torque, and control signal error signals such as self-lock function, ie, reverse rotation prevention function and motor overrun prevention function, are positively eliminated. Is required. That is, 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 one or both of the sliding device and the urging device have a self-inversion prevention function. It is 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 types of command control modes of the adjusting device 90 are conceivable. When the output rotation speed N0 or the output torque T0 does not require accuracy, a single control command may be supplied as a preset operation amount. When maintaining high accuracy and stable transmission to give priority to high speed responsiveness of speed change operation, periodically detect deterioration error of transmission member such as belt pulley friction surface, circumference or elastic sag, and output rotation speed or The compensation amount according to the deviation between the detected value of the frictional force and the set value, the compensation amount according to the deterioration amount, and the compensation amount so that it becomes a value predetermined in the memory for each command of the rotational speed or torque
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 an open or closed loop for compensation. Furthermore, when high-precision management of torque and speed ratio is required, high load transmission is performed by comparing each detected value with a reference value determined in advance in memory and supplying negative feedback control to each input or output controller. However, it achieves long-term stable operation with extremely high efficiency. The adjusting device may be controlled in a programmable manner by means of a memory in which the speed ratio versus contact radius and output friction force setting pressure are stored in advance according to the load and an arithmetic processing unit.

  In the common embodiment of the present invention, when the frictional force between the variable-diameter pulley V-groove and the V-belt is controlled by the external pressure supply of the operating device, the other vehicle frictional force is externally elastic to secure the axial torque of one vehicle in the input / output pulley. It is to provide a continuously variable transmission that is not restricted by the belt type and is particularly suitable for a constant horsepower type by controlling the force by supplying force and indirectly adjusting the one axle torque via belt tension. In the first embodiment, in particular, in order to secure the output vehicle torque, the adjusting device compensates for the shortage of the friction force of the input vehicle by operating the input controller, and constantly supplies elastic force to the input vehicle to variably control the input vehicle friction force to adjust the belt tension. After that, the output vehicle is indirectly controlled with variable torque. In the second embodiment, in order to avoid belt entrainment due to direct pressurization to the output vehicle and to ensure the stability of the output frictional force, the adjustment device performs variable pressurization control on the pressurization value that should always supply elastic force to the input vehicle. By using the wedge effect of the output pulley V groove and adjusting the output friction force to control the variable torque, it is highly efficient in a particularly large speed ratio range without being restricted by the belt type such as tension type or push type belt. To achieve stable constant horsepower transmission.

  The third embodiment suppresses the frictional force shortage of the input vehicle and the excessive frictional force of the output vehicle in the large speed ratio region, and at the same time, the frictional force of the input vehicle and the frictional force of the output vehicle also in the small speed ratio region. The aim is to provide a continuously variable transmission with optimum transmission efficiency in the entire transmission range while suppressing the shortage. In the fourth embodiment, when the third solving problem is realized, an operation mechanism capable of discriminating the applied pressure and the elastic force is provided on one side of the input vehicle, and a simple operation capable of discriminating and supplying the applied pressure and the elastic force on the other side. It is to provide a continuously variable transmission that achieves high efficiency by arranging pressure mechanisms. In the fifth embodiment, an inelastic pressure force that accurately positions the pulley V-groove in one or both of the input vehicle and the output vehicle of the continuously variable transmission, and an elastic force that performs absorption settling such as error and vibration It is to provide an operation mechanism that can be identified and supplied according to each command. In the sixth embodiment, the fifth problem to be solved is further simplified, and a simple control command for inelastic pressure applied to one or both of the input / output vehicles and the elastic force by the elastic body with a single control command. It is to provide a pressurizing mechanism that can be identified and supplied according to the situation.

The common implementation means of the present invention is to constantly supply and control the elastic force generated by compressing the elastic device by the compression device in the other vehicle in order to ensure the torque of the one vehicle in the input / output pulley that transmits constant horsepower to each other. In addition, the other vehicle is variably pressurized and controlled according to the output rotation speed or speed ratio command, and the adjusting device is variable by adjusting the one axle torque indirectly through the belt by operating the other vehicle friction force. It is to provide a continuously variable transmission that achieves torque control. The first implementation means includes a pressurizing device that constantly supplies an elastic force generated by serially compressing the elastic device to the input vehicle, and a drive that performs variable pressurization control via the pressurizing device according to a command from the adjusting device. In this configuration, the input axle frictional force is variably controlled by an input operating device as a power source, so that the output axle torque is indirectly variably controlled via the belt. The second implementation means has a following vehicle function that performs variable pressurization control by always supplying elastic force to the input vehicle, and a reference vehicle function that performs variable positioning control by substantially applying no pressure during shifting and non-shifting during output shifting. This is because the feed adjuster indirectly controls the variable torque of the output shaft with the wedge friction force created by the V belt and the output wheel V groove from the input vehicle friction force with the input actuator.

  The third implementation means provides the following vehicle function to the input vehicle and the reference vehicle function to the output vehicle in the high speed ratio range of the continuously variable transmission, and further follows the reference vehicle function to the input vehicle and the output vehicle in the small speed ratio region. Car functions are given, and each controller switches the operation function of each car in the middle of the shift range. In the fourth embodiment, one of the input / output movable vehicles 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 of the elastic device and the contact device. It is that each pressure switch was performed with the identification controller that connects parallel bodies in series. The fifth implementation means includes a first pressurizing device in which an elastic device and a first compression device are superposed in series, a contact device and a second compression device in series on one or both of the movable I / O vehicles. It is to provide an operating device that individually supplies elastic force and pressure with the pressure device. In the sixth embodiment, the pressure device formed by serially superimposing the elastic device and the compression device and connecting the abutment device and the elastic device in parallel to one or both of the movable vehicles of the input / output vehicle is in accordance with the control command. It is to provide an operating device that distinguishes between the elastic force range and the pressure range.

  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 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. In response to the command, the input operation unit 9 has a first and second input pressurization devices 11 and 51 for the input wheel 1 and an adjustment device 90 for the output operation unit 8 and a single pressurization device 21 for the output wheel 2. Each has the ability to distinguish and supply elastic force and pressure. 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. 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 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 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. At the time of gear shifting operation, a variable diameter positioning control is performed by applying a pressure from the pulley to the belt, but when the speed ratio is determined, the application of the pressure is substantially stopped and the V groove position by the movable vehicle is fixed, so the normal constant speed ratio A V-groove with the same conditions as the pulley is formed. In the following vehicle function, even if error factors such as belt pulley contact surface friction and internal / external disturbance vibrations occur, the specified frictional 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-settling or automatic alignment function for instantaneous recovery to the moment by the action of elastic force.

  In this example, the input operating device 9 is an individual having 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, and an individual command supply system. It is comprised by the input pressurization apparatus of the pressurization apparatus 50, and the 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 the speed ratios and torque commands from the drive sources 60a and 60b are input to the shafts 18a and 58a, respectively. Once the moving devices 13 and 53 are positioned or the friction pressure is determined, a self-locking function is maintained that maintains the position or the frictional force even if the supply of the command is stopped. 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 functions as a switching device and is composed of two sliding members 36 and 37 disposed through a gap 38. The compression device 14 applies both to each other according to the selection of an operation command. Supply and stop of pressurizing force are controlled by the operation command of the adjusting device 90 at the time of the contact operation in contact and at the time of release of contact to separate the two. 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, so that 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 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 is provided with a central through hole, and is composed of an elastic body 32 shown by 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 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 compression device 51 and compresses the elastic body 32 in series with a torque command, and simultaneously generates the 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. Accordingly, the pressurizing force of the first pressurizing device 11 and the elastic force of the second pressurizing device 51 can be supplied simultaneously, and the vehicle 1 is applied in parallel to each other via 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 the shafts 72, 72 are supported by the main body 10 d via linear ball bearings 75, 76 and added in the same direction as the sliding tool 56 in order to maintain the square even under high pressure. Press. In this example, the sliding body 33 and the pressure ring 74 are shared and the elastic device 31 is pressurized in series. Therefore, each operation device includes the elastic device or the contact device arranged around the pulley, the compression device, or the pressure device, and the compression device, the elastic device, or the contact device of the pulley separation. Alternatively, pressure is transmitted between the pulley bearings by the pressure transmission device.

  In this example, the output operation unit 8 in FIG. 3 has an output pressurization having a single compression device for supplying pressure to the output wheel 2 and supplying an elastic force to the second pressurization device. The device 21 identifies and supplies both in response to a single control command to the drive source 60c. Unlike the controller 9, the output elastic device 41 having an annular shape and the output device 45, which is an output switching device, on the inner side or the outer side of the output device 41 are arranged in parallel in a coaxial concentric circle. It has an output pressurizing device 21 which is a composite pressurizing device 40 assembled in series by a compressing device 24. 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 that is pressurized through the bearing 49 has a sliding body 43 formed in an annular mold frame or pan that is closed at one end, and an elastic body 42 that consists 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 is composed of two sliding members 46 and 47, and the gap between them is controlled by a command. In this example, the sliding member 47 is a pan-shaped outer edge of the sliding body 43 and the sliding member 46 is a sliding member. Each of the moving objects 44 is shared. FIG. 3 shows a gap 48 in the left half of the center line when the elastic device 41 is lightly loaded, and 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 contact released state. Reference numeral 45 denotes a state in which the pressure is discriminated 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 in which an elastic device 42 having an annular elastic body 42 and an abutment device 45 composed of sliding members 46 and 47 are configured to be capable of simultaneously compressing a main diaphragm 104 sealed, and one of the detection ends 101 The lead-out end 102 extends radially from the location and displaces the sub-diaphragm 106, the pressure-electrical signal conversion unit 103 having a semiconductor strain gauge disposed at the end, and the oil medium 105. 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 operating devices 8 and 9 are respectively provided with drive sources 60 a, 60 b and 60 c adjacent to the pressurizing devices 11, 51 and 21, respectively, and the speed ratio, torque and control command are received from the electronic control device 90. Supplied as pressure, elastic force and control commands to individual command supply paths. 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. The two controllers require servo control synchronized with each other, but the moving operation amounts of the compression devices 14, 54 and 24 are different, so the speed ratio, torque and control command to the corresponding shafts 18a, 58a and 28a are different. Is equipped with gear transmissions 61a, 61b, 61c with different speed ratios provided individually from the adjusting device 90, and with gears 68, 69 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 processing information, the memory 97a is synchronization and switching control information when the pulley 1 is operated by the following vehicle function and the pulley 2 is operated by the reference vehicle function, and the memory 97b is the pulley 1 by the reference vehicle function and the pulley. The synchronization and switching control information when the 2 is operated by the following vehicle function, the memory 97c is the synchronous operation information when switching the functions of both pulleys 1 and 2 and when the individual operating devices 8 and 9 are operated individually and individually. Control information for the constant torque type transmission and 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 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 as to operate in the transmission form of the second transmission device B which is individually operated. 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 the time of startup, the input wheel 1 is subjected to the maximum frictional force 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. On the input wheel side, the gap 38 of the abutment device 35 is stagnated but there is no effect, and the elastic body 32 is compressed. 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 remaining gap 38 of the contact device 35 is instantaneously erased by the operation command of the adjusting device 90, and the sliding members 36 and 37 enter the contact operation state, and the elastic force of the elastic body 32 is contacted. Switching is performed by fixing the speed ratio preferentially to the pressure applied by the device 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 controlled indirectly by the input operation unit 9 via the belt tension. The number 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. 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 of switching the command supply of torque and speed ratio command to each pressurizing device based on the speed ratio signal ε and torque signal calculated and calculated from 93 and the pressure detector 94 will be described. However, in order to prevent the hunting between the transmission devices A and B in the vicinity of the speed ratio ε = 1 in practice, each command is determined as shown in the speed ratio vs. contact radius / friction force characteristics in FIGS. 6A and 6B. ) To be controlled. 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 the supply of commands to the elastic body during that period, such as the left sliding body in FIG. 2, or may stop the external pressurization and wait in a certain compression state, or only at the time of switching. Instead, it is sufficient to always drive both at the same time. 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 high compression pressure for a long time, there is a possibility that the predetermined frictional force cannot be continuously maintained in each of the vehicles 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. The adjusting device may release the compression of each elastic device on the input / output vehicle side such as the second and composite pressurizing devices while the transmission is stopped. Also, each amplifier 98 can be switched quickly by switching the DC motor 65 by operating the supply voltage or pulse amount only when switching between the two operating devices, and switching the function by supplying an instantaneous speed command.

  Further, in this example, the output torque may be achieved by indirect or direct pressurization control of the input and output operation devices 9 and 8, but even when the elastic bodies 32 and 42 are deteriorated, a high-precision desired friction force is output. 2 is used to calculate torque. 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. In the torque compensation control when the frictional force is reduced, the torque is obtained from the detection value of the deterioration of the elastic body 31 in advance, and the input or output operating devices 9 and 8 are servo-controlled so as to be suitable for the frictional force determined by the CPU 95 and the memory 97a. The variable torque control with a predetermined frictional force supply can be arbitrarily used by performing open loop or closed loop control. 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, 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 between the two maximum efficiency regions in the middle region between the two maximum efficiency regions. In addition to a stable connection in the middle range, it has been shown that both shift regions can be greatly expanded while remaining stable, and a wider band can be achieved. In addition, high-efficiency transmission is 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 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. The composite pressure device is a closed type in which one of the two sliding members is slidable between the mold sliding member and the other is slidable between the elastic member and the one sliding member, and is sealed in advance with the minimum compression pressure Ps1. Or an open type actuator that supplies the maximum compression pressure Ps0 of the elastic body when one of the two sliding members is shared by the mold sliding body and the other is shared by the main body and the sliding members are in contact with each other. To place. 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 closed, the elastic body 32 for preventing the deterioration of the transmission member cannot be depressurized while the transmission is stopped. However, even if the compression pressure of the elastic body 32 changes over time, the output torque is controlled. Since the CPU 95 and the memory 97c constantly adjust the predetermined frictional force in the output wheel 2 because the detector 94 is used, the obstacle can be overcome by the compensation operation for increasing the operation amount of the input operation unit 9 for the decrease in the elastic force. 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, it is possible to apply an elastic force to the input and output vehicles at the same time and apply torque to balance the frictional force between the two vehicles, but the pressure supply state should not be set at the same time. Therefore, one of the operating devices 8 and 9 is individually pressurized or combined pressurizing device and the other is an elastic pressurizing device in which the compressing device compresses the elastic device in series. Therefore, variable torque control according to the load is possible. At this time, it is not necessary for each pressurizing device to have a switching device such as an abutting device as in the third embodiment, etc. Further, the operating device 9 of FIG. Even if the speed ratio pulley is applied at a constant belt contact radius, the idea of the present invention in which the output torque is adjusted by the input operating device can be achieved and is naturally 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)

In a variable transmission that performs friction transmission control with an input and output vehicle that is wound around a belt and is made of a variable-diameter vehicle, and an input and output pressurization device that applies pressure to one of the input or output vehicle according to a command,
A first pressure device in which a first compression device performs speed ratio control with the applied pressure; a second pressure device in which a second compression device performs torque control with an elastic force obtained by serial compression of the elastic device; The input and output pressurizing devices having first and second drive sources connected to the second compression device, and further, the speed ratio and torque command are identified and supplied to the first and second drive sources, respectively. A variable transmission having an adjustment device that individually controls servo so that it can be operated independently and compensates for an error in the output torque in a low speed range or a high speed range. In a variable transmission having an input and output vehicle that is wound around a belt and made of a variable diameter vehicle, and an input or output pressurizing device that applies pressure to the input or output vehicle by a command through a drive source,
An input and output elastic device that applies an elastic force to the input and output wheels, a first pressurizing device that the first compression device performs variable speed ratio control using the applied pressure, and a second compression device that is one of the two elastic devices. A second pressurizing device that performs variable torque control with a compression elastic force obtained by serial pressurization, a first and second drive source that are connected to the first and second compression devices, respectively, and the input or output vehicle. The input or output pressurizing device in which the first and second pressurizing devices for applying pressure and the compression elastic force are arranged in parallel, and the speed ratio and the torque command are separately supplied to the first and second drive sources, respectively. A variable transmission having an adjusting device. In a variable transmission having an input and output vehicle that is wound around a belt and made of a variable diameter vehicle, and an input or output pressurizing device that applies pressure to the input or output vehicle by a command through a drive source,
An input and output elastic device that applies an elastic force to the input and output wheels, a first pressurizing device that the first compression device performs variable speed ratio control using the applied pressure, and a second compression device that is one of the two elastic devices. A second pressurizing device that performs variable torque control with a compression elastic force obtained by serial pressurization, a first and second drive source coupled to the first and second compression devices, respectively, and one of the input and output vehicles The input and output pressurizing devices having the applied pressure applied to the other and the compression elastic force applied to the other, and the adjusting device for identifying and supplying the speed ratio and torque command to the first and second drive sources, respectively, and servo-controlling them. Variable transmission with In claim 1, 2, or 3, the adjusting device is a depressurization command to pressurize at the time of start-up while keeping the high pressurization of the elastic device in the high pressurization state during suspension of the transmission operation in the forced release state, A variable transmission that is applied to a corresponding drive source of each of the pressure devices that compresses the elastic device. In a variable transmission having an input and output vehicle applied to the input and output shafts, a belt applied between the two vehicles, the input or output vehicle having a movable vehicle, and an elastic device for applying an elastic force to the movable vehicle,
A pressurizing device that performs torque control on the movable vehicle by supplying a compressive elastic force generated by superimposing the elastic device in series with a compression device is independent of the compression device from the adjusting device via a drive source during the transmission operation. A variable transmission that receives a torque or control command or a torque compensation command and is given a depressurization command to keep the high pressurization state of the elastic device in a released state and pressurize at the time of start-up during a stop. In the variable transmission in which the input and output vehicles applied to the input and output shafts and the belt applied between the two vehicles are controlled by frictional transmission variable by the input and output pressurization devices according to the commands through the drive source,
One compression device performs torque control with the elastic force obtained by serially compressing one elastic device with one of the input and output vehicles, and the first pressure ratio control with the pressure of the first compression device on the other The other pressurizing device in which the pressurizing device and the second compressing device are arranged side by side with the second pressurizing device that controls the torque by the elastic force obtained by compressing the other elastic device in series, and the first compressing device during the transmission operation A speed ratio command is connected to the first drive source connected to the first and second compression devices, respectively, and a torque command is individually supplied to the one and second drive sources, and the high pressure state of the elastic device is set during the stoppage when stopped. A variable transmission having an adjustment device that issues a depressurization command that keeps the release state and pressurizes when starting. 7. The control device according to claim 1, wherein the adjusting device increases or decreases the shaft torque of the input or / and output vehicle in accordance with a torque load that changes during a high load torque or a light load torque. A variable transmission having a pressure detector for output friction pressure in a pressurizing device.   7. The input or output pressurizing device according to claim 1, wherein the input or output pressurizing device is configured such that the sliding tool of the first or second compression device is attached to the inside or the outside of the one or the other elastic device having an annular shape. A variable transmission with concentric circles.   9. The input or output pressurizing device according to claim 8, wherein the input or output pressurizing device is coaxially centered around the input or output wheel rotation axis in a through hole of one or the other elastic device of the sliding tool or the receiver formed in an annular shape. A variable transmission with a core circle. 7. The first and second pressure devices according to claim 1, wherein both the sliding devices of the first and second compression devices are arranged coaxially with the input or output wheel rotation shaft and both A variable transmission in which at least one of the sliding devices is formed in an annular shape and the rotary shaft is disposed therethrough.

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