JP5095787B2 - Variable transmission - Google Patents

Description

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

The operation of the constant horsepower 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 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 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

A common problem to be solved by the present invention is that the first and second pressurizing devices are connected to the input vehicle, the output vehicle or the input vehicle by utilizing the property that the pressure supply to the variable diameter pulley is speed ratio control and the elastic force supply is torque control. A new control mode or transmission mode is realized in which the variable operation of the torque by elastic force is incorporated in both the output vehicles, and the servo control is performed by the pressurizing device, and the variable operation of the torque by the elastic force is realized. Provided is a variable transmission that servo-controls with a pressurizing device and performs stable torque transmission and high-efficiency broadband transmission according to the transmission load.
The first problem to be solved by the present invention is that, for selection of the function of each transmission vehicle of the input / output vehicle, a first pressurizing device for supplying pressure and a second pressurizing device for supplying elastic force are individually installed and the adjusting device This is the idea of selecting the speed ratio control of the pressure ratio or the simultaneous control function of the speed ratio and the torque by the pressure force and the elastic force.

The second problem to be solved by the present invention is that, for example, when performing speed ratio control on one side of an input / output vehicle and torque control on the other side, if torque control is performed with elastic force supply in addition to the speed ratio control of the one vehicle, As a result of applying an elastic force, the idea is to perform highly accurate and efficient torque transmission control with torque load.

The third problem to be solved by the present invention is that a transmission using an elastic body has an advantage of performing an appropriate torque control by an optimum frictional force when the elastic force is variable, while the high pressure application state is always an elastic body while the transmission is stopped. And belt pulleys have the disadvantage of accelerating deformation and deterioration, and the idea is to promote wide-band high-efficiency, high-load transmission, eliminate the shortcoming, and achieve long-term highly efficient and stable transmission.

The fourth problem to be solved by the present invention is that the switching operation is accurately performed between the pressurizing force supply system path and the elastic force supply system path for the corresponding movable vehicle by using the switching device. This is an idea that realizes two transmission modes, a mode in which the torque is controlled on the other side and a mode in which the speed is controlled on the other side with the torque.

The fifth problem to be solved by the present invention is that one control mode in which an applied force is applied to one of the input / output vehicles and an elastic force is applied to the other, and another control mode in which an elastic force is applied to the other are applied to the speed ratio versus transmission efficiency characteristics. This is a bumpless switching philosophy in which smooth torque transmission is performed when switching between both forms in the middle of the variable range using a gap.

The sixth problem to be solved by the present invention is that the input and output vehicles are switched between the first transmission that controls torque and speed ratio and the second transmission that controls speed ratio and torque, respectively, in the middle of the variable range. This is a transmission concept in which the former variable range and the latter variable range are connected to each other to ensure a broadband and high-efficiency transmission.

The seventh problem to be solved by the present invention is that, if the elastic force supply pressure to the corresponding movable vehicle is reduced, it can be substantially the same as the supply stop of the elastic force, but in the case of pressure supply, active supply and shut-off are necessary. Thus, a switching device is provided in the pressurizing force supply system, and the result is a concept of selecting a torque control function that controls the supply or stop of the pressurizing force to the corresponding movable vehicle by an external speed ratio command or control command.

The eighth problem to be solved by the present invention is that each pressurizing device is simplified and simplified as a whole when installing the second pressurizing device having a large elastic device around the corresponding movable vehicle or the first or second pressurizing device. It is an idea that is configured to be lightweight and that allows each pressure member to independently perform a pressure operation for torque control or speed ratio control.

A ninth problem to be solved by the present invention is that a single operation of either the speed ratio or the torque is performed even in a transmission that switches between a speed ratio and torque control mode for the input and output vehicles, respectively, and a torque and speed ratio control mode, respectively. It is the idea that various transmission modes are realized by commands of the adjusting device depending on the time and the synchronous operation of both.

  The tenth problem to be solved by the present invention is that the efficiency of the normal friction transmission is maximum when the speed ratio is near 1, but there is a slight deviation in the speed ratio vs. efficiency characteristics between when the torque control is performed with the input vehicle and when it is performed with the output vehicle. This is an idea that defines the region of the switching operation point when the variable regions of both efficiency characteristics are connected to each other by using the result.

The common solution of the present invention is to use the speed ratio and torque control function properties of the first and second pressurizing devices for the movable vehicle, and to manage the speed ratio and the torque control form with high accuracy by the speed ratio and the torque command or control command. Provided is a variable transmission that realizes an idea or a control element switching idea for selecting various transmission modes.
In order to enhance the role of the control function of the input or output vehicle, the first solving means of the present invention is provided with a first pressurizing device that supplies pressure to the corresponding transmission vehicle and a second pressurizing device that supplies elastic force. The speed ratio control is selected by a substantial pressurizing force by switching the command of the adjusting device, and the simultaneous application control of the speed ratio and the torque is selected by the pressurizing force and the elastic force.

According to the second solving means of the present invention, one of the input / output pressurizing devices is torque-controlled by a second pressurizing device arranged in parallel with the first pressurizing device that controls the speed ratio, and the other is separately torque controlled by supplying elastic force. On the other hand, a pressurizing device is arranged so that the elastic force is variably applied to the input / output vehicle as the torque load increases or decreases.

The third solving means of the present invention includes a torque command that is servo-controlled with the torque calculated by the output friction pressure detector during transmission operation, and a depressurization command that releases the elastic force in a high pressurization state when the operation is stopped. It is the structure which maintains a highly efficient high load transmission stably for a long period of time by an adjustment apparatus providing to a 2nd pressurization apparatus.

The fourth solving means of the present invention is to select a speed ratio control and a torque control function for each corresponding movable vehicle, as well as to switch the supply command in the adjusting device and to change the first pressurizing device for supplying pressure and the second for supplying elastic force. It is the structure which provided with the switch which positively selects operation | movement between two pressurization apparatuses, and was controlled by the switch or the adjustment apparatus.

The fifth solving means of the present invention is that the transmission is made up of a control combination of speed ratio and torque, and the adjusting device gives priority to the speed ratio or output rotational speed on the first pressurizing device side in order to eliminate the transmission impact when switching between the two. The reference is fixed to the reference or the torque on the second pressurizing device side is preferentially fixed during the reference period.

According to the sixth solving means of the present invention, one of the input / output vehicles is elastic by switching operation between the first pressurizing device for supplying pressure to one of the input / output vehicles and the second pressurizing device for supplying elastic force to the other. In this configuration, the two high-efficiency variable regions of the two transmissions are connected to each other, the torque being applied by force, the other applying speed ratio by applying pressure, and one applying pressure by applying pressure and the other applying torque by elastic force.

The seventh solving means of the present invention is an operation in which the two sliding members of the switch arranged in series with the first pressurizing device slide in the pressurizing direction, transmit pressure when both come into contact, and stop transmission when separated. This is a configuration in which torque control is selected as a result when the supply of pressure is interrupted by the speed ratio command or control command of the adjusting device.

The eighth solving means of the present invention is the first or second sliding device in which the input or output pressurizing device is previously formed into an annular shape between the corresponding movable wheel or pulley rotating shaft and the elastic device arranged therethrough. The speed ratio and torque are individually operated independently by supplying pressure or / and elastic force by penetrating the pressure supply system path of the first or second slider, or the first slider and switch. This is the configuration.

According to the ninth solution of the present invention, when one of the speed ratio and the torque control is fixed to a constant value and the other is variably operated by the first and second pressurizing devices, the constant torque type transmission or the torque conversion type transmission is switched. When both are operated synchronously and variablely, the transmission form is selected by the operation of the adjusting device that performs the constant horsepower type transmission.

  The tenth solving means of the present invention is an intermediate between a low speed range where the first transmission transmits a higher efficiency torque than the second transmission and a high speed range where the second transmission transmits a higher efficiency torque than the first transmission. In this configuration, the low speed area and the high speed area of the high-efficiency transmission are interconnected with the speed ratio or output rotation speed of any one of the areas as the operating point.

    The present invention applies at least one of a first pressurizing device for supplying pressure to an input vehicle or an output vehicle and a second pressurizing device for supplying elastic force, and in particular, an adjusting device for variable operation of torque by elastic force. It is an idea that produces many utilities by servo control. That is, firstly, if the first and second pressurizing devices are installed in the input or output vehicle, individual operation or simultaneous operation of the applied pressure and the elastic force becomes possible. Secondly, if a second pressurizing device is installed on both the input and output vehicles, torque control by elastic force is possible on both sides. Thirdly, if a switching device contact device is installed in the first pressurization device on both the input and output vehicles, it is possible to synchronize switching between supply and stop of the pressurization in both vehicles. Torque control is realized. Fourth, if the first and second pressurizing devices are installed on both the input and output vehicles, two transmission modes are created by synchronous switching between the speed ratio control and the torque control between the two vehicles, and the transmission function can be selected. Fifth, even when the input / output vehicle has the first pressure device on one side and the second pressure device on the other side, it promotes the advantages resulting from the installation of the elastic device, eliminates the disadvantages, and maintains long-term stable transmission. There is utility.

  That is, as for the first utility, if the first and second pressurizing devices are present in the corresponding movable vehicle, naturally the speed ratio control and the torque control can be simultaneously controlled in addition to the individual selection of the speed ratio and the torque control. Therefore, the conventional transmission has only the first pressurizing device, and even if the pressure is supplied at the time of shifting, there is substantially only the non-pressurizing state at the time of non-shifting, but in the present invention, during the speed ratio control by the first pressurizing device. At the same time, there is an advantage that the torque control by the installation of the second pressurizing device can be separately given separately according to the command of the adjusting device.

  The second effect is that both the input and output vehicles can manage the elastic friction force with high accuracy. Therefore, the optimum output torque value is always selected according to the load requirement at both high load torque and low load torque. Can be granted. Therefore, as shown in Fig. 7, the transmission efficiency in the low speed range and the high speed range is deteriorated mainly in the highest efficiency range, but the efficiency in both ends is greatly improved by the elastic frictional force management in both vehicles. The variable speed range that can be used is greatly expanded. In particular, since the self-alignment function by the elastic body works in both the input and output vehicles, the problem that the transmission becomes impossible due to the entanglement phenomenon that the belt bites into the pulley is solved.

  The third effect is that if a switch is connected in series to the pressurization supply path of the first pressurization device on both the input and output vehicles, the supply and stop of the pressurization can be operated simultaneously on both sides simultaneously. There is an advantage that the synchronous switching control of the control mode such as the pressure supply on the vehicle side and the supply stop on the other vehicle side can be realized, and as a result, the torque control by the elastic force supply is selected by stopping the pressure supply. .

  The fourth effect is that the speed ratio control and the torque control can be simultaneously switched on both the input and output vehicles, so that the input and output vehicles respectively control the torque and speed ratio, and the operation mode of the first transmission and the speed control respectively. By switching between the operation mode of the second transmission that controls the ratio and torque in the middle of the variable range, as a result, only the higher efficiency transmission range of both operation modes is coupled to each other, resulting in a significantly wider shift range Has the effect of realizing. Therefore, in the fields of vehicles, power receiving facilities, etc., there is an effect that it is possible to provide a broadband high-efficiency transmission with low fuel consumption, low price, and low operating cost.

The fifth effect is that in the transmission using the elastic device, the elastic force always performs appropriate torque control during operation, but during the stop, the high pressure application state of the elastic force continues for a long time and promotes deformation deterioration of the belt pulleys. In order to eliminate this drawback, in the present invention, a compulsory depressurization command for releasing the high pressure application state at the time of stopping is given to the second pressurizing device in addition to the torque command at the time of normal operation. As a result, there is an advantage that the transmission can be provided with a guarantee function for maintaining a high-speed transmission response at the same time as a high-efficiency transmission which is always stable.

  Furthermore, in the present invention, when the input and output operation devices are switched synchronously between the first transmission mode and the second transmission mode, high efficiency constant horsepower transmission is achieved, but only one of the speed ratio and torque is variably operated and the other is There is an advantage that it can be operated even if it is fixed, and as a result can be used for both a constant torque transmission and a torque conversion transmission. At that time, a depressurization command may be given to the input or output pressurization device in order to release the elastic device in a high pressurization state when the transmission is stopped. Further, when switching between the two transmission modes, the rotational speed or friction pressure of the input / output vehicle is detected and the operation is switched based on the speed ratio or the output rotational speed or based on the output torque to preferentially fix the reference value. Since the operation switching operation is completed during the operation, there is no impact in the switching during transmission, and stable and safe transmission bumpless switching control according to the load is realized.

In addition, since it is necessary to install both the second compression device having the giant elastic device and the first and second compression devices in a narrow area around the corresponding movable vehicle, the present invention provides a slide of the first or second sliding device formed in an annular shape. The moving tool and the elastic device can be added to each other by positioning the coaxial device on the same axis as the movable wheel or pulley rotation axis, and the sliding tool passes through the central through-hole of the elastic device or positions the outer periphery of the elastic device. The pressure device has been guaranteed stable operation and simplified weight saving. In addition, the first and second compression devices themselves can be used as a single unit, thus further reducing the size and weight of each pressure device.

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, but switching may be performed at an arbitrary speed ratio, and the reference of the switching operation is based on the speed ratio. Alternatively, the output speed or output torque may be switched to a priority standard. In this case, it is desirable that both the output rotational speed and the torque be safely switched to bumpless without instantaneous impact. Further, when the input power is changed in the output rotational speed, such as an internal combustion engine or a DC motor, only the output torque is controlled according to the rotational speed while the speed ratio control of the variable transmission is kept at a certain constant speed ratio. A torque converter may be provided by performing variable torque control by a single operation. Since the pulley for the standard vehicle function performs the rotational speed control and that for the following vehicle function performs the torque control, the control command that is also the speed ratio and torque command supplied from the adjusting device when the operation device is switched to each function. It is obvious that 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. The control motor of the input / output drive source showed an example of individual arrangement for each pressure device on the input and output side, but the drive source is shared by using a switch such as a known transmitter or gear synchronous fitting device Alternatively, 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 stable transmission to prioritize high speed response of gear shifting operations, the belt circumference or elastic body deterioration error is periodically detected, and each command for rotation speed or torque is given according to the amount of deterioration. In addition, the compensation amount is calculated by the CPU so as to be a value determined in advance in the memory, and given to the input / output operating device, the detected value of the actual rotational speed or friction pressure is fed back, and the servo control is performed in a closed loop. You may do it. 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. As a result, long-term operation with extremely high efficiency is achieved even for high-load transmission.

  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. The input operating device 9 is connected to the input wheel 1 with the first and second input pressurizing devices 11 and 51, the adjusting device 90 is individually provided, and the output operating device 8 is the output wheel 2 with a single pressurizing device 21 and the speed ratio is adjusted. Each has the ability to identify 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 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 composed of 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, they perform a self-locking function that maintains the position even when the supply of control commands 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 arranged via a gap 38. The supply and stop of the applied pressure are controlled by the control 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 abutting 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 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 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.

  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 storage device 97 is composed of three pieces of processing information. The memory 97a is control information when the pulley 1 is operated as the following vehicle function and the pulley 2 is operated as the reference vehicle function. The memory 97b is the pulley 1 as the reference vehicle function and the pulley 2 is the following vehicle. The memory 97c stores the control information when the function is activated, the synchronous operation information when the functions of the pulleys 1 and 2 are switched, the constant torque type transmission when the actuators 8 and 9 are individually operated independently and the torque Control information of the 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 left gap 38 of the abutting device 35 is instantaneously erased by the command of the adjusting device 90, and the sliding members 36 and 37 enter the abutting operation state, and the elastic force of the elastic body 32 is changed to the abutting device. Switching is performed with the speed ratio fixed to the pressure of 35 preferentially. At the same time, 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 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. Furthermore, when the transmission members such as the elastic bodies 31 and 41, the pulleys 1 and 2 and the belt 3 are worn out or deteriorated due to a long period of high compression pressure, there is a risk 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, 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, elastic force is not applied at all except during gear shifting operation, or only variably controlled elastic force is applied, so there is no friction coefficient fluctuation or excessive friction force destabilization. Transmission failure due to the belt winding phenomenon due to pressure is eliminated. Therefore, in the present specification and claims, “substantially non-pressurized” means that the elastic force may be positively variably controlled within a range that does not adversely affect the frictional transmission. As a result, as shown in FIG. 7, the maximum efficiency range between the first transmission device A in the high speed ratio region and the second transmission device B in the small speed ratio region is obtained by using the difference between the two maximum efficiency ranges of the two efficiency characteristics. In addition to the stable connection in the middle area, it is shown that both speed change areas can be greatly expanded while remaining stable, and a wider band can be achieved. In addition, high-efficiency transmission is also achieved at both ends of the low-speed range and the high-speed range. However, the greatest advantage is that not only the conventionally known push-type belt but also a tension-type belt can be applied without any adjusting device such as a cam mechanism because the belt winding phenomenon is eliminated. The function switching position of each operating device is not necessarily limited to the speed ratio ε = 1 and can be arbitrarily changed.

8 and 9 show a second embodiment variable transmission. The second embodiment 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 multi-block 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. Therefore, the variable pressurization control for torque is carried out by both the operating devices 8 and 9 as the individual pressurizing device or the composite pressurizing device and the other as the elastic pressurizing device in which the compression device compresses the elastic device in series. Therefore, variable torque control according to the load is possible. Accordingly, at this time, it is not necessary for each pressurizing device to have a switching device such as a contact device as in the third embodiment, etc. Further, a constant speed ratio not shown in FIG. Since the idea of the present invention in which the output torque is adjusted by the input operation device can be achieved even if the pulley is applied, both are 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 (11)

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,
At least the input or output pressurizing device is a first pressurizing device that applies pressure to the corresponding movable vehicle by the first compressing device and provides a speed ratio control function by variable diameter positioning control of the belt, and the second compressing device is an elastic device. And a second pressurizing device for applying a torque control function by variable pressurization control of the friction surface by applying an elastic force generated by serial compression of the adjusting device or the first control device according to the speed ratio and the torque command or the control command. And a variable pressure transmission in which the second pressurizing device selectively gives one or both of pressure supply and elastic force supply to the corresponding movable vehicle. 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,
One of the input and output pressurizing devices applies torque to one of the input and output cars by applying an elastic force generated by compressing one elastic device in series with one compression device, the second pressurizing device, and the other The other vehicle is provided with the other second pressurizing device that applies the elastic force generated by the other compression device compressing the other elastic device in series and performs the torque control by the variable pressurizing operation of the friction surface. A variable transmission in which elastic force is variably supplied to the input / output vehicle simultaneously from the one and the other second pressurizing devices in accordance with the increase and decrease. 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,
A first pressurizing device that supplies pressure to one of the input and output vehicles to control the speed ratio, and an elastic force obtained by serially compressing an elastic device to the other of the input and output vehicles to control torque. A second pressure device, a first detector for obtaining a detected friction pressure value of the output vehicle, and a torque command for servo-control by an adjusting device that calculates torque from the detected value during operation of the transmission, and The adjusting device that applies to the second pressurizing device a forced depressurization and pressurizing command for releasing the high compression of the elastic device in a high pressurizing compression state when the operation is stopped and pressurizing when starting A variable transmission comprising: 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,
At least the input or output pressurizing device applies torque to the corresponding movable vehicle to perform speed ratio control, and applies the elastic force obtained by serially compressing the first pressurizing device and the elastic device to perform torque control. A pressure device, and a switch for selecting one or both of the first and second pressure devices, and the switch or adjusting device is variable in accordance with the speed ratio and torque command or control command. A variable transmission in which the transmission mode is switched by discriminating and selecting the supply of pressurizing force and / or elastic force during the operation. 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 above inputs having a first pressurizing device that applies pressure to the corresponding movable vehicle and performs speed ratio control and a second pressurizing device that performs torque control by applying elastic force obtained by serially compressing the elastic device An output pressurizing device, a switch for selecting one or both of the first and second pressurizing devices, a detector for knowing the detected values of the input and output rotational speeds and / or the output friction pressure, and An adjustment device that performs bumpless switching of the speed ratio and torque servo control between the input and output pressurizing devices between the input and output pressurizing devices in the middle of the variable range based on the speed ratio or output rotational speed or on the basis of torque. Variable transmission made of A variable transmission in which an endless V-belt is arranged between the input and output wheels of a variable diameter transmission vehicle that performs speed ratio control when supplying pressure and torque control when elastic force is supplied, and an input and output pressurizing device variably controls friction transmission. In
A first pressurizing device for supplying pressure to one of the input and output vehicles and controlling the speed ratio; a second pressurizing device for controlling the torque by supplying elastic force via an elastic device in series; and the input and output In the middle of the variable range between the first transmission that feeds friction by supplying elastic force and pressure to the vehicle and the second transmission that feeds friction by supplying pressure and elasticity to the input and output vehicles, respectively. A variable transmission comprising a switching device for switching operation, and an adjusting device for variably controlling the speed ratio and the torque, respectively, before and after switching between the first and second transmissions. Motivation. 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,
A first pressurizing device that performs presence / absence of speed ratio control according to the pressure applied via a switch to the corresponding movable vehicle in series and a second pressurizing device that performs torque control according to the elastic force obtained by serially compressing the elastic device The input and output pressurizing device having the input and output in parallel is constituted by an input and output switching device made of two sliding materials that are slidable in the direction of the rotation axis of the corresponding movable vehicle and are capable of contacting and separating from each other. The switch has a switching device, and both switching devices are composed of an input and output contact device that synchronously switches each other so that when one is in contact and the other is in a release state, the speed ratio command or control command of the adjusting device Variable transmission that is controlled by switching. 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 first sliding device of the first compression device applies pressure to control the speed ratio, and the second sliding device of the second compression device applies the elastic force obtained by compressing the elastic device in series. The first pressurizing device and the second pressurizing device, which are arranged on one side and the other side of the input / output vehicle or arranged in parallel with each other, are separately provided for the input vehicle and the output vehicle, respectively. The input or output pressurizing device arranged is the first or second sliding device formed in an annular shape between the corresponding movable wheel or the pulley rotation shaft and the elastic device penetratingly arranged on a coaxial concentric circle. The first or second sliding tool or a pressure supply system path in which a switching device is connected in series to the first sliding tool is concentrically arranged in the through hole of the elastic device, and the adjusting device corresponds to the above. A variable transmission that variably applies pressure or elastic force to a movable vehicle. 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 above input and output pressurization devices individually having first and second pressurization devices that respectively perform speed ratio and torque control by elastic force supply via pressurizing and elastic devices connected in series to the corresponding movable vehicle, and in the middle of the variable range And a selector for selecting the first or / and the second pressurizing device, and further, one of the input and output vehicles is set to one of the torque control and the speed ratio control at a constant value, and the other is set independently on the other vehicle side. A variable transmission comprising a constant torque type transmission or a torque conversion type transmission that is variably operated, or an adjusting device that constitutes a constant horsepower type transmission by synchronously variably operating both the input and output vehicles. 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 above input and output individually having a first pressurizing device that supplies pressure to the corresponding movable vehicle and performs speed ratio control and a second pressurizing device that supplies elastic force obtained by serially compressing the elastic device and performs torque control A pressure device, a switch for selecting operation of the first or / and second pressure device, and a first transmission for controlling the speed ratio on the other side of the input / output vehicle on the other hand and a speed on the other hand. Between the maximum efficiency range between the high speed ratio range where the efficiency is higher than that of the second transmission which controls the torque on the other side and the small speed ratio range where the second transmission is higher efficiency than the first transmission. A variable transmission comprising: an adjusting device that synchronously switches the switching device based on an arbitrary speed ratio or output rotational speed. The operation according to claim 1, 2, 4, 5, 6, 7, 8, 9 and 10, wherein the adjusting device releases the high compression of the elastic device in a high pressure compression state when the transmission is stopped. A variable transmission in which a depressurization and pressurization command for forcibly switching between high pressurization and low pressurization to be started sometimes is applied to the input or output pressurization device.