JP5630676B2 - 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 type belt continuously variable transmission is under development in US Pat. Nos. 4,973,288 and 5,269,726, etc., but it does not lead to a satisfactory product. The idea is to pressurize the input / output vehicle simultaneously with hydraulic pressure in the latter and screw hoisting in the former. However, these ideas have decisive and significant functional or principle defects. The output horsepower P [W] transmitted to the load by the normal output vehicle is determined by a transmission relational expression P = 1.027 × N × T between the rotational speed N [rpm] and the torque T [Kgm]. The rotation speed is determined by the contact position between the belt pulleys, that is, the radius ratio, whereas the torque is determined by the contact friction pressure and the contact area between the two. This means that the rotational speed is determined only by the positioning control of the belt in the pulley, whereas the shaft torque is determined only by the area of the pulley and the variable pressure control of the constant friction pressure. Therefore, the above transmission relational expression itself indicates that the variable speed positioning control and the frictional pressure variable pressurization control should be discriminated and applied to each pulley in order to ensure the desired rotation speed and torque in the continuously variable transmission. Show. However, the above-mentioned US patent idea has no guarantee that the proper belt position is always maintained even if the positioning function of the pressurizing force synchronized with the input / output vehicle is provided, and there is no torque guarantee function for always applying a predetermined friction force to both the vehicles. This indicates that the above-mentioned patent ideas cannot secure and maintain an appropriate rotation speed and torque, and that constant horsepower transmission is impossible in principle.

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

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

A common problem to be solved by the present invention is that the transmission efficiency is different between the transmission applied to one vehicle side of the input and output vehicles and the transmission applied to the other vehicle side because the torque application form changes due to the elastic force supply. There is a difference in efficiency between the large-diameter side and the small-diameter side, but this is a variable transmission idea that is switched in the middle range of the variable range and only the high-efficiency transmission portions of both are selected and combined.

The first problem to be solved by the present invention is that the variable transmission requires a synchronous operation of the speed ratio and the torque. Since slip increases and efficiency deteriorates, the idea is to selectively switch high-efficiency transmission by arranging a switch in two transmission modes.

The second problem to be solved by the present invention is the supply of pressure to the variable diameter vehicle. When the belt contact diameter is large, the contact area is large and slipping is less advantageous than when the diameter is small. This is an idea for stably performing the switching operation of the pressure supply in the intermediate range of the variable range.

The third problem to be solved by the present invention is that the pressure supply to the movable vehicle is suitable for the belt positioning operation due to excessive frictional force, but if the pressure force is supplied simultaneously to the input and output vehicles, the positioning operation starts independently on both vehicles and the transmission is unstable or impossible This is the idea of switching in the middle of the variable range so as to supply pressure to only one vehicle.

The fourth problem to be solved by the present invention is how to incorporate a switch in the pressure supply path for the operation of stopping the supply of pressure within the input / output pressurizer, but the sliding device and the movable vehicle side centering on this Alternatively, it is a switching philosophy in which an abutment device made of two sliding materials is installed between the main body side and remote control is performed with or without a gap between the two materials.

The fifth problem to be solved by the present invention is that, in the speed ratio control, it is necessary to hold the sliding device of the sliding device in a predetermined position in order to maintain the predetermined speed ratio, but only the sliding device is removed when switching to the torque control. This is the idea of supplying pressure and elastic force at the same time in advance in order to prevent transmission failure due to loss of frictional force to the corresponding vehicle.

The common solution of the present invention is that the transmission efficiency is different between the input and output vehicles during torque and speed ratio operation and speed ratio and torque operation, respectively, and there is a difference in efficiency even when the belt contact diameter is large and small. Therefore, this is a variable transmission in which the operation is switched in the intermediate range of the variable range and the high efficiency range is combined so that the large-diameter side vehicle of the contact diameter functions as a reference vehicle function or the small-diameter vehicle functions as a follow-up vehicle function.

In order to improve the transmission efficiency of the variable transmission, the first solving means of the present invention is such that one of the input / output vehicles has a reference vehicle function when the belt contact diameter is larger than the other and a follower vehicle function when the belt contact diameter is small. This is a configuration in which a switch for switching the operation of the first and second transmissions in the intermediate range of the variable range is introduced into the transmission.

The second solving means of the present invention is that one of the input and output pressurizing devices stops the supply of pressure to the one wheel having a large belt contact diameter and the other to the other wheel having a small diameter while the other is a one wheel having a small diameter. When the supply is stopped, the power is properly transmitted by a switching device which is supplied by the other large-diameter vehicle and which is synchronously switched in the intermediate range of the variable range.

The third solving means of the present invention is a sliding device that displaces between two sliding tools in response to a speed ratio command, a switching device that operates to supply and stop the applied pressure to a corresponding vehicle by a switching command, and simultaneous application to an input / output vehicle. This is a mechanism for switching the pressure supply in the middle of the variable range in order to prevent pressure supply and supply pressure to the side of the large-diameter wheel.

The fourth solving means of the present invention has a sliding device composed of two sliding tools and an abutting device composed of two sliding materials, one sliding material in which the sliding tools are connected in series or integrally formed, and each movable vehicle side. Alternatively, the configuration is such that the presence or absence of a gap with the other sliding material applied to the main body side is remotely operated by an adjustment device switching command in the intermediate range of the variable range.

The fifth solving means of the present invention is that the elastic body and the switch require consideration of the driving direction and the positional relationship for the simultaneous supply of the applied pressure and the elastic force. The other is concentrically arranged on each vehicle side or main body side so as to be slidable and displaceable in the compression displacement direction at the inner hole or outer periphery.

The variable transmission is an input / output vehicle, and the transmission efficiency is good at a position where the belt contact radius is substantially the same, that is, in the intermediate range of the variable range near the speed ratio ε = 1. In addition, there is a considerable difference in efficiency characteristics between when the speed ratio control or the output torque control is performed with the input vehicle and when it is performed with the output vehicle. Even within the same pulley, the belt contact diameter on the large diameter side tends to be affected by excessive friction force due to the increase in contact area, while the small diameter side is susceptible to friction force shortage due to the decrease in contact area. is there.
Therefore, in the present invention, if the pressure supply is selected for speed ratio control by belt positioning on the large diameter side of the belt contact diameter and the elastic force supply is selected for torque control by appropriate friction force on the small diameter side, the result is two. High-efficiency, wide-band transmission that greatly expands the practical band by connecting only the two high-efficiency transmission bands to each other. Can be realized. Moreover, the introduction concept of the switching device has the following derivative utility.

First, especially when the pulley on the large diameter side of the belt contact diameter is supplied with an elastic force, it is easy to cause braking heat generation due to the belt biting. However, when the pressure supply is applied, stable speed ratio control can be secured by smooth belt positioning operation without heat generation. Further, if the small-diameter pulley is supplied with pressure, it tends to cause slip heat generation after the supply of the speed ratio command is stopped, but if it is supplied with elastic force, it can stably apply shaft torque due to arbitrary frictional force. Accordingly, stable operation and stable transmission of both the variable speed ratio and the variable torque are always possible, and the followability of the speed ratio control and the torque control associated therewith is excellent, so that there is an advantage that a high speed variable response can be secured.

  Secondly, in the present invention, in addition to applying an applied pressure on one side of the input / output vehicle and applying an elastic force on the other side, it is only necessary to provide another elastic force supply path at the same time and in parallel on the applied pressure supply path side. It is possible to apply individual torque to both output cars at the same time, and the pulley friction force according to the load can be managed with high accuracy at both times regardless of whether the vehicle is at high load torque or low load torque. There is an effect that transmission capacity control according to demand can be maintained with high accuracy and high efficiency in the entire variable range.

Thirdly, as a single-type transmission mode, in the transmission in which the speed ratio control is performed by the input vehicle and the torque control is performed by the output vehicle, both the high speed ratio range excluding the variable range and the low speed ratio range are rapidly In addition, the efficiency deteriorates and the degree of deterioration differs between the high speed ratio range and the low speed ratio range. On the other hand, the same applies to the transmission mode in which the torque is controlled by the input vehicle and the speed ratio is controlled by the output vehicle, but the present invention can connect two efficient speed ratio regions with the intermediate region of the variable region as a boundary, and the efficiency characteristics in the entire variable region Since there is an advantage of averaging and flattening, in the fields of vehicles and power receiving facilities, etc., there is an effect of maintaining fuel consumption reduction and driving cost reduction for a long period of time.

  Fourthly, if the pressure supply selection switching concept is introduced so that the large diameter side of the belt contact diameter is always the speed ratio determining factor, it is natural that a step impact or a bump is likely to occur in the speed ratio at the time of switching, and it is easy for an operator such as a vehicle. There is a risk of danger due to vibration of transmission shock. However, in the present invention, even if elastic force is supplied to both the input and output vehicles, pressure should not be supplied to both of them simultaneously. Therefore, during the switching operation, elastic force is supplied to the input and output vehicles at the same time or the current speed ratio and torque are maintained. However, since the pressure supply is shifted from one vehicle to the other, the adjustment device also avoids an operation that gives a shocking change to the speed ratio with respect to the elastic force supply. There are advantages you can do.

Fifth, if the contact device is individually installed in the input / output pressurization device as a transmission mode switch, there is no need to prepare two transmission modes in advance, and the input / output contact device is simply switched from the adjusting device. Since two transmission modes can be realized with a time difference by simply supplying commands synchronously, there is an advantage of realizing an inexpensive and simple high-performance variable transmission that is reduced in size and weight.

  In addition to the above, even the tension type belt where the so-called belt entanglement phenomenon, where the belt bites into the pulley, is not affected by the instability or impossibility of transmission due to such entanglement, the material of the belt pulley, wet dry type, etc. Since a stable friction torque can be created regardless of changes in lubricity and ambient temperature conditions, a highly stable friction transmission form can be created without any conventional measures to prevent entrainment.

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

The idea of the present invention is not limited to the wet type in which both the transmission gear and the transmission control device are housed in the oil layer, but may be a dry type in which both are housed in the air, or may be individually housed. As a transmission form, the present invention is particularly effective for a constant horsepower transmission type variable transmission, but it may be applied to a constant torque transmission type variable transmission by operating only the speed ratio control alone. As the control mode, the operation device of the speed change control device has disclosed the individual pressurization method composed of the first and second pressurization devices and the composite pressurization method by the composite device in distinguishing the applied pressure and the elastic force. Both of the operating devices may be of a pressurizing method using an individual pressurizing device, or the input side may be a pressurizing method using a composite pressurizing device, and the output side may be of various pressurizing methods such as using an individual pressurizing device. A pressure detector may be provided on the input side to detect the friction pressure. At this time, the preliminary pressure 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 pressure 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 reference of the switching command operation is the speed ratio. Instead, the output rotation 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 a screw or other inclined hoisting machine or a hydraulic jack using an inclined portion 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 high-speed response of variable speed and variable torque operation is prioritized by maintaining high accuracy and stable transmission, the belt circumference or elastic body deterioration error is periodically sensed and the rotation speed or torque according to the amount of deterioration. Each command is given a compensation amount calculated by the CPU so that it becomes a reference value determined in advance in the memory, and given to the input and output operating device, and an operation value of a substantial rotational speed, friction pressure or torque value is given. Servo control may be performed in an open loop. When further precise management of torque and speed ratio is required, negative feedback control is performed by substantially comparing the detected values of the input / output vehicle speed, friction pressure or torque value with a reference value set in advance in memory. Is supplied to the input or output side actuators to achieve a long-term operation with extremely high efficiency even for high-load transmission by closed-loop servo operation.

1 to 6, a variable transmission 10 for a vehicle includes a transmission 10A composed of a belt 3 provided between an input vehicle 1 and an output vehicle 2, and an input operation unit 9 and an output operation on the same plane side. 4 is configured with a shift control device 10B that adjusts the adjusting device 8 with an adjusting device 90 shown in FIG. In this example, the input operating device 9 has an individual pressurizing device 50 composed of the first and second input pressurizing devices 11 and 51, and the output operating device 8 has a combined pressurizing device 40 composed of the output pressurizing device 21. It is energized by the drive source 60 shown in FIG. Each pressurizing device 11, 51, 21 has a compression device 14, 54, 24, respectively, and operates the input elastic device 31, the input contact device 35, and the output composite device 20, respectively. The input operating device 9 is connected to the input wheel 1 by the first and second input pressurizing devices 11, 51.
Thus, the adjusting device 90 is individually provided, and the output operation unit 8 has the ability to identify and supply the elastic force and the pressurizing force to the output wheel 2 according to the speed ratio with a single pressurizing device 21. In addition, since there are substantially equivalent functional parts on the input / output side, in this specification, when it is necessary to distinguish between “input” and “output” for each part name, it is omitted when it is understood by the preceding and following descriptions and drawings.

The transmission 10A is a variable-diameter pulley 1 and 2 in which the movable wheels 1a and 2a and the fixed wheels 1b and 2b are opposed to each other, and the former is slidable in the axial direction relative to the latter via a key.
Are arranged in opposite directions on the input shaft 1c and the output shaft 2c, respectively. The pulleys 1 and 2 rotate while being supported by a pair of bearings 7 and 6, respectively, while further separating the rotational force between the main body 10 and the movable wheels 1a and 2a by the pair of bearings 5 and 4, respectively. The pressurizing devices 11, 51 and 21 respectively pressurize the pulley movable wheels. The main body 10 is assembled so that a first main body 10a that houses other transmission devices such as a vehicle and a second main body 10b that houses the variable transmission 10 are separable.

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

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

  In this example, the input operating unit 9 includes a first input pressurizing device 11 for supplying pressure to the input wheel 1 and a second input pressurizing device 51 for supplying elastic force, respectively. It consists of an input pressurizing device and drive sources 60a and 60b. The first pressurizing device 11 has a series structure of the contact device 35 of the input switching device and the first compression device 14, and the second pressurization device 51 has a serial structure of the elastic device 31 and the second compression device 54, respectively. Both are configured to press the movable wheel 1a of the pulley 1 in parallel with each other in the direction of the rotation axis through the common sliding body 36 and the bearing 5. The contact device 35 and the elastic device 31 are coaxially arranged on the outer periphery of the shaft 1c of the input wheel 1 and are arranged in parallel on the concentric circle and parallel to the axial direction, and the compression devices 14 and 54 are arranged in cascade on the same axis. The Therefore, the pressurizing form of each pressurizing device is that the device 14 transmits pressure to the elastic device 31 from the inner wall of the second main body 10b and the device 54 from the outer wall to the elastic device 31 via the pressure transmitting device 70 of FIG.

  The compression devices 14 and 54 of the pressurizing devices 11 and 51 are both composed of sliding devices 13 and 53 and biasing devices 12 and 52 for biasing the sliding devices 13 and 53. Each sliding device 13, 53 has two sliding tools 16, 17, 56, 57 and a pressing device 15, 55 that slides between both, and is a ball screw in this example. The sliding device 13 is formed in a tubular shape, and the sliding device 53 is formed in a rod shape around the input wheel 1 and is spaced apart on the extension of the shaft 1. The urging devices 12 and 52 are both worm transmissions including worms 18 and 58 and wheels 19 and 59 in this example, and 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 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 and supplies the elastic force generated simultaneously through the sliding body 34 and the bearing 5. At this time, the vehicle 1 performs the function of the following vehicle of the variable pressurization control. Accordingly, the pressure applied by the first pressurizing device 11 and the elastic force of the second pressurizing device 51 are applied in parallel to each other through the common sliding body 34 and the bearing 5.

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

  In this example, the output operating device 8 shown in FIG. 3 is configured such that a single output pressurizing device 21 supplies a pressing force supply of the first pressurizing device and an elastic force supply of the second pressurizing device to the output wheel 2 by a drive source 60c. Both are identified and supplied in response to the control command. Unlike the operation device 9, a composite pressurizing device 40 in which the composite device 20 in which the output elastic device 41 and the output contact device 45 as an output switching device are assembled in parallel is further assembled in series by a single output compression device 24. It has an output pressurizing device 21. The compression device 24 includes a sliding device 23 including two sliding tools 26 and 27 and a pressing device 25 for the ball screw 26a, and further includes a worm transmitting device urging device 22 including a worm 28 and a wheel 29 and having a self-locking function. . The difference between the compression devices 24 and 54 is that the sliding device 53 is pressurized with a right-hand screw but the sliding device 23 is pressurized with a left-hand screw, and the sliding tool 56 moves up and down without rotation. Since the moving tool 26 rotates and moves up and down, a bearing 49 is arranged, and the entire compression device 54 is installed in the main body 10b so as not to vibrate. In the compression device 24, only the sliding device 23 is a transmission wheel. 2 and the elastic device 41 are supported in an interlocking state or floating state capable of transmitting elastic vibration, and the sliding tool 26 is slidable in the axial direction between the wheel 29 of the urging device 22 and a spline coupling 26c. Has been extended to enable rotational transmission.

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

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

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

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

  The storage device 96 has basic information for the arithmetic processing unit 95 to execute programmable control. The storage device 97 is composed of three pieces of processing information. The memory 97a is control information when the pulley 1 is operated as the following vehicle function and the pulley 2 is operated as the reference vehicle function. The memory 97b is the pulley 1 as the reference vehicle function and the pulley 2 is the following vehicle. The control information when the function is activated, the memory 97c stores the synchronous operation information when the functions of the pulleys 1 and 2 are switched, and the constant torque type transmission and torque when each of the actuators 8 and 9 is operated individually and asynchronously. Control information such as a conversion type transmission, simultaneous operation of input / output elastic force and command operation for depressurization 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, and the gap 38 of the abutment device 35 is reduced on the input vehicle side, but there is no influence, and the elastic body 32 is compressed by the compression device 54. As a result, the compression is reduced to P11 as shown in FIG. 6A, so that the supply elastic force as the torque command is reduced and the input friction force is also reduced. On the output vehicle side, the frictional force due to the belt tension decreases, so the output frictional force is also reduced to P01, and the simultaneous compression device 21 keeps the composite device 20 as it is, and the relative displacement is only between the sliding tools 26 and 27 of the compression device 21. Then, the movable vehicle 2a is forcibly moved by the supply pressure as a speed ratio command through the pressure transmission device 80, and the belt radius is reduced to r01. At the same time, the radius r10 of the input wheel 1 increases and moves to r11 regardless of the reduced pressure by the action of the elastic force. This series of operations is performed simultaneously and synchronously. Similarly, when the speed increasing command is applied again, the same operation is repeated and repeated until the speed ratio ε = 1 is reached.

  Further, when the speed increasing command reaches ε = 1, the contact devices 35 and 45 function as both switching devices, and the operations of the two operating devices 8 and 9 are switched instantaneously. That is, on the input side, the slightly remaining gap 38 of the contact device 35 is instantaneously erased by the switching 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 switched by indirect control via the belt tension by the input operation unit 9 to form one pressurizing device on both sides. After that, in the second transmission device B, the output rotational speed is indirectly controlled by the speed ratio command of the operating device 9 and the output torque is directly controlled by the torque command of the operating device 8 to form the other pressurizing device. Therefore, thereafter, stable transmission is continued in exactly the same manner except that each control command by the adjusting device 90 and the supply switching of each compensation signal are performed. The left half of FIG. 3 shows the compression state of the output wheel 2 and the pressurizing device 21 with the speed ratio ε s at the output rotational speed when a speed increasing 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 supply of torque and speed ratio command and switching command to each pressurizing device 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 the supply of the control command during that period by the switching command as in the left sliding body in FIG. 2 and may stand by in a compressed state. It may be driven. Further, 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, the predetermined frictional force may not be maintained continuously 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, the decompression or forcibly canceling or pressurizing the high pressurization of the pressurization devices 51 and 21 from the adjustment device 90 to the low pressurization or A command for pressurization can be given to prevent aging 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 supplying a switching command for instantaneous speed movement.

  Further, in this example, there is a case where the output torque is achieved by indirect or direct pressurization control of the input and output operation devices 9 and 8, but when the elastic bodies 32 and 42 are deteriorated, a high-precision desired friction force is input and In order to guarantee the output wheels 1 and 2, a pressure detector is used for torque calculation. Even when the input / output wheels 1 and 2 work 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 it is only necessary to perform servo control. Torque compensation control at the time of reduction of each frictional force or torque is performed in accordance with the frictional force or torque reference value previously determined according to the load by the CPU 95 and the memory 97a that know the detected frictional pressure value or torque detection value of the elastic body 31 and the like. Servo control can be performed by applying closed loop control to the input or output operation devices 9 and 8 so as to be suitable for the control, and variable torque control with predetermined friction force supply can be arbitrarily controlled by open loop control or the like. it can. 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 is different from the first embodiment only in the configuration of the input operation unit 9, and the variable torque control and the variable diameter positioning control operation by switching the functions of the first and second transmission devices A and B are substantially performed. Is exactly the same. Therefore, members having the same or similar functions are denoted by the same reference numerals as in the first embodiment, and the differences are described. The structural difference is that 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, one of the operating devices 8 and 9 is an individual pressurizing device or a combined pressurizing device, and the other is an elastic pressurizing device in which the compressing device compresses the elastic device in series. Therefore, it is possible to perform variable torque control according to impossibility. Accordingly, at this time, it is not necessary for each pressurizing device to have a switching device such as a contact device as in the third embodiment, etc. Further, a constant speed ratio not shown in FIG. Even if the pulley is applied, the idea of the present invention for adjusting the output torque with the input operation unit can be achieved and included in the scope of the present invention.
Therefore, the present invention includes various changes and modifications within the scope that can be easily created by those skilled in the art from the claims.

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

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

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

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

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 (7)

The input and output pressurization device has an elastic force and pressurizing pressure supply path to control the torque and speed ratio, respectively, and the input and output car has an input and output pressurization device with pressurization and elastic force. A second transmission that controls the speed ratio and torque on the supply path, and a reference vehicle function when one of the input and output cars has a larger belt contact diameter than the other, and a follower function when the smaller diameter. A variable transmission having a switching device for switching the operation of the first and second transmissions by switching the functions of the reference vehicle and the following vehicle of each vehicle in the intermediate range of the variable range for application to the one-way vehicle. . The input and output wheels, the pressure supply path for speed ratio control by the pressure of the first sliding device, the elastic force of the elastic device, or the elastic force obtained by the second sliding device by the series pressurization of the elastic device An elastic force supply path for applying torque, an input and output pressurizing apparatus that applies the pressure and elastic force supply paths in parallel or one and the other of the two vehicles, respectively, and one of the pressurizing apparatuses has a belt contact diameter. However, when the pressure is supplied by the large-diameter side of the two cars, the other is stopped by supplying the pressurizing force by the other side of the small-diameter side. For this purpose, a variable transmission comprising a switch for synchronously switching the two vehicles in an intermediate range of the variable range, and an adjusting device for giving a switching command to the switch. An input and output pressurization device, and an input and output pressurization device that forms a pressure supply path that is applied to one or both of the two vehicles by a sliding device that relatively displaces between the two sliding tools in response to a speed ratio command; A switch that stops supply of pressure on the other vehicle when the pressure is supplied to the one vehicle in accordance with a switching command, and further, the switch prevents simultaneous supply of pressure to the two vehicles and the belt contact diameter is larger A variable transmission comprising: an adjustment device that switches the supply of pressure to the input or output vehicle in an intermediate region of the variable region in order to perform speed ratio control on the vehicle. An input and output vehicle; a sliding device that relatively displaces between the two sliding tools; a switching device that includes a contacting device in which the two sliding materials are arranged in series so as to be capable of contacting and separating; and one of the sliding tools; An input and output pressurizing device that applies a pressure supply path to the input and output vehicles, respectively, in which one of the sliding members is integrally connected in series and the other of the sliding members is disposed on each vehicle side or main body side; Further, the adjusting device is configured to switch the presence / absence of a gap between the sliding materials in an intermediate range of the variable range, and the adjusting device passes the above switch when the sliding material comes into contact with the belt contact diameter on the large diameter side vehicle. This is a variable transmission that is supplied with pressure and cut off the pressure supply with a small-diameter side vehicle when separated. An input and output vehicle, a first sliding device and a contact device are connected in series, and a pressure supply path for speed ratio control by the applied pressure, and an elastic force of the elastic device or the second sliding device is connected in series to the elastic device. An elastic force supply path for applying torque with an elastic force obtained by pressure, an input and output pressurizing apparatus in which the both supply paths are arranged in parallel, an adjusting apparatus for instructing each sliding apparatus, and two sliding materials And a switching device comprising the abutting device arranged concentrically with each vehicle on the vehicle side or the main body side. When the two sliding members are in contact with each other, the belt contact diameter is switched in the middle range of the variable range in order to apply pressure and elastic force to the one wheel on the large diameter side and only elastic force to the other wheel on the small diameter side when separating. Variable transmission. In Claim 1, 2, 3, 4 or 5, The said input or output pressurization apparatus has the input or output elastic device which supplies elastic force in parallel with the said pressurizing force supply path, or during the transmission of the said transmission, or the said A variable transmission in which the input and output vehicles are torqued by individual elastic forces during operation of the switch. 6. The one-sliding member of the switching unit according to claim 1, wherein the switching unit is integrally assembled with one of sliding tools of a sliding device constituted by an inclined hoisting machine or a hydraulic jack. A variable transmission in which the presence / absence of a gap between the vehicle and the other sliding material applied to the movable vehicle side or the main body side of each vehicle is switched by a switching command.

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