JP4221099B2 - Shift control device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a constant horsepower transmission type continuously variable transmission used for industrial machines such as machine tools, vehicles, motors, etc.To apply toTwo transmission vehiclesIndividuallyAdditionPressureEach toControllerHigh speed response controllability and high efficiency with pressurizerStable transmissionThe present invention relates to a speed change control device for realizing a high quality, high quality continuously variable transmission.
[0002]
[Prior art]
  Japanese Patent Application No. 9-217819 (Van Doll Nezu) is well known as a transmission wheel pressurizing device. Of the two disks, the sliding disk itself forms part of a hydraulically driven piston cylinder as a pressure device.Using a hydraulic cylinderThis is a pressurizing device that changes the radius of the transmission wheel and the transmission body by directly pressurizing and sliding the same disk to change the speed. The direct pressurizing apparatus using hydraulic pressure has two advantages: (1) an arbitrary pressurizing force from large to small can be obtained in a narrow space, and (2) a bearing as a consumable is unnecessary. However, hydraulic control has two fatal and decisive drawbacks for the transmission. Disadvantages are: (1) When the transmission wheel is directly pressurized because the hydraulic pressure is inelastic, it is impossible to secure elastic absorption and self-alignment action against impacts, errors, etc. (2) Hydraulic medium is delayed in operation, oil leakage, centrifugal The most basic transmission operation that is directly influenced by force is always an unstable factor.
[0003]
  The horsepower P that the normal transmission wheel 1 transmits to the load device is expressed by the following equation as the relationship between the rotational speed N and the torque T. That is
          P [W] = 1,027 x N [rpm] x T [kgm]
Therefore, to transmit the predetermined horsepower P0,CommandTransmitter torque when N increasesCommandDecrease T and reverse rotation speedCommandTorque as N decreasesCommandT needs to be increased. However, in the above-described prior art, elastic means such as a spring is arranged in parallel with the disk of the driven transmission wheel, but the elastic means supplies the sliding disk.ElasticityThe applied pressure is a direction in which the pressure is increased as the high-speed rotation state is reached, and the pressure is reduced as the low-speed rotation state is reversed. This is because, in the transmission of the constant horsepower transmission type, it is necessary to increase the applied pressure as the low speed rotation is reached.ElasticityThe direction of the applied pressure is completely opposite. Therefore, in principle, constant horsepower transmission cannot be realized with this type of elastic pressure device.
[0004]
[Problems to be solved by the invention]
  The present inventionfirstWhen controlling transmission wheel pressurization, it does not depend on the direct pressurization method using hydraulic pressure.InIt depends on the indirect pressurization method that uses an elastic body selectively. One of the two transmission wheels remains inelastic with only the applied pressure, and the other has both the applied pressure and elastic force in series. JoinedProducedSupplying elastic pressure force and transmission wheelAnd pressurizing deviceEverySpeed ratio and torque control functionroleIndividualThis invention relates to a transmission control device that guarantees constant horsepower transmission to a transmission and realizes constant horsepower transmission by variable pressurization control in a direction in which the relationship between the rotational speed on the output transmission vehicle side and the sheave pressure is in inverse proportion. . The common problem of the present invention is thateachBiographyCarofVariable control functionDivision of roles andThe elastic and inelastic pressureHigh-speed shift response and high efficiency by further progressing to a constant horsepower transmission type transmission established by both ideas of pressurization controlStableIt is an object of the present invention to provide a speed change control device that contributes to transmission and leads to high reliability and high durability.
[0005]
  The first solution is the transmissionStable transmission andIt is a precondition to guarantee each function of high speed response and high efficiency transmissionfirstandsecondEach controller isCorrespondingIt is to realize a shift control device having a highly accurate reproducibility with respect to a shift command. In particular, the reproducibility of shift control is the application of pressure to both transmission wheels.beltPositioning accuracyPressure sliding with belt holding pressure accuracy and elasticityReproducibility and at the same timeeachStabilization of gear ratio and torque value by pressureSupplyIs the basic conditioneachIt is an improvement of the pressurization device, and it is highly stable in the constant horsepower transmission function corresponding to repeated shifting operations.TransmissionIs to secure.
[0006]
  The second solution isfirstandsecondEven if the actuator has the specified high-precision and stable pressurization capability for the corresponding transmission vehicle, it is highly synchronized with the pressurization operation of both actuators in order to operate properly as a single transmission. It is essential to maintain sex for a long time. However, in a constant horsepower transmission type transmission, an unbalanced pressurization in which the pressure applied to each actuator is extremely large and applied to one of the two actuators and small to the other.PowerTheEssentialEssentialWhenTo dofirstA controller,secondPrevent the mutual interference of the applied pressure between the actuator and the drive source or prevent the error signal from propagating to each other.High reliability and durabilityTo maintain a high degree of synchrony.
[0007]
  The third problem is that the shift control device is highly accurate.Pressurization operationEven if the synchronism can be maintained, it is necessary to suppress deterioration of parts or heat generation due to wear, abrasion or the like in both the speed change operation or the transmission operation. That is, the speed change operation is used as an inching or a speed change command to increase / decrease speedOr pressure increase / decreaseIn order to give sufficient abrasion resistance to various operating conditions such as use where each command of the above is repeated alternately and frequently.firstandsecondIt is an object of the present invention to provide a shift control device that can be controlled with higher efficiency on the premise of stable pressurization by an operating device.
[0008]
  The fourth problem to be solved is that the shift control device itself isA higher quality, high quality continuously variable transmission is realized by utilizing the role of variable control function between torque control by the first actuator and speed ratio control by the second actuator.In order to improve the transmission efficiency of the transmission and to adjust the safety factor, torque application according to the actual load capacity applied to the transmission is subjected to variable pressurization control. In particular, the output capacity on the continuously variable transmission side should be as close as possible to the actual load capacity required on the output load equipment side.Improve transmission efficiency,FurthermoreThe pressure characteristics of the elastic device and the pressure characteristics required for actual loadbetweenDeviationTo haveBy changing the pressurization characteristics of the elastic device as necessary so that the safety factor and service factor of the transmission can be set or changed according to the transmission capacity, the transmission transmission device can be improved.TransmissionefficiencyOr safety factorIs to provide power transmission.
[0009]
[Means for Solving the Problems]
  The common problem of the present invention is that one of the two transmission wheels is in an inelastic pressure state.Speed ratio controlThe other is in the state of elastic pressureTo achieve torque controlActivelyThe roles of both control functions are shared individuallyAlthough it is dividedeachPressurevariableThe points to be given are common. At this time, both pressures themselves are slightlyInElasticityPowerOrAdditionPressure stateButMay be disturbed by unstable elements. For example, in pressurization control by hydraulic pressure such as a relief valve, there is a case where both pressures themselves become unstable with the start of the operation of the relief valve at the moment when a shift command is supplied. At this time, the balance condition of the applied pressure in the transmission body collapses and the transmission is disturbed. Therefore, the present inventionIt ensures stable transmission and high-speed shift response, and also maintains high transmission efficiency operation.In order to prevent this transmission disturbance from being excessively expanded or to provide a highly stable value for both applied pressures supplied to both actuators, respectively.PressureCentering on the screw bodySlidingIt is to provide a speed change control device constituted by a mechanism.
[0010]
  In the solution of the first problem, the compression control device is provided with a sliding device composed of two sliding tools and the sliding device so as to constantly supply a stable pressure and maintain high reproducibility. With a biasing device,firstActuator andsecondThe operating device has a transmission body contact radius on the second transmission wheel side by means of a stable pressure control according to a shift command for the first transmission wheel, the second transmission wheel and the elastic device.Positioning controlSpeed ratio byOrOutput rotation speed and first transmission wheel sideWhatofElasticityWith pressureTransmitter holding pressure controlThis guarantees high-precision reproducibility of torque due to
[0011]
  The solution to the second problem is that the transmission control deviceDisguiseThe device is composed of a sliding device composed of two sliding tools and an urging device for urging the sliding device, and each urging device is composed of a worm transmission device to each transmission vehicle.WhatSelf-locking function for preventing reverse rotation transmission of the pressurizing force and the driving source has a brake device or a clutch devicereversiblecontrolDriving sourceBy installing the overrun transmission blocking function, error transmission is blocked in the shift command between the first transmission vehicle, the second transmission vehicle and the drive source.
[0012]
  The solution to the third problem is as a shift control device.variableHigh efficiency of the control mechanism itselfStable pressurizationFor the purpose ofeachPressureDisguiseThe device consists of a sliding device that displaces the relative position of the two sliding tools and a biasing device that biases the sliding device.eachThe sliding device and biasing device of the compression device are cylindrical in the direction of the axis of rotation and coaxially.ControllerCoaxially connected to each other with through holes, or at the coaxial position of the first or second transmission wheelAxis of rotationA through-hole is provided, and pressure control is performed by a speed change command from the outside or the inside of the rotating shaft through any of the through-holes.
[0013]
  The solution to the fourth problem is that the shift control device is a shift transmission device.With two transmission wheelsAs the roles of individual control functions are differentiated in the transmission mechanismThe drive source is also divided into a common drive source or an individual drive source, and the first and second shift commands applied to the first and second actuators are supplied as torque and speed ratio commands, respectively.,When operating with the common drive source, the shift power is mechanically branched or supplied via the individual drive source when operating with the individual drive source, and the first and second shift commands are individually applied as torque and speed ratio commands, respectively, and Selectable to increase or decrease the shaft torque value to select the transmission efficiency or safety factor of the above-mentioned speed change transmission device when operating with an individual drive sourceIt is a thing.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
  Since the present invention reviewed the constant horsepower transmission type continuously variable transmission system from the basic principle, it can be applied not only to the dry transmission but also to the wet transmission, and the field of use is for small horsepower such as machine tools. It can be applied to large horsepower for vehicles. Especially variable pressure control to the first (driven) transmission wheelAxial torque applied by elastic forceI doSo thatIn this case, the present invention does not depend on the direct pressurization method by hydraulic pressure, but by relying on the indirect pressurization method by an elastic body.InelasticPressurevariableNot only grant, but always elasticPressurizationPower toovariableWhat is necessary is just to realize grant. Winding compression deviceSlidingIf the mechanismSoThe pressure force is merely a reaction force from the elastic device, and the elastic device itself is a good variable pressure mechanism. MoreSlidingAs long as the device is usedthisElectric driveMechanismOr hydraulic driveMechanismYouRuThis is a problem on the drive source side, and the present invention may be any. The former drive method is better because the speed change command speed increase / decreaseOr pressure increase / decreaseAlternating frequentReversibleswitchingoperationIt is because it can follow high speed.
[0015]
  The elastic body is not limited to a coil spring, but may be another form such as a leaf spring or a spiral spring. A single spring may be used, but in order to obtain a large pressure, it is necessary to increase the spring constant, the spring tends to shrink, and the size and shape is greatly expanded. May be. A plurality of leaf springs may be combined in series and parallel. The arrangement direction of each elastic body is not limited to a concentric circle, and if it is small and a large pressure can be secured, it is not limited to the case where a plurality of springs are arranged in parallel and these are simultaneously driven to obtain a continuous linear characteristic, Depending on the gear shift command of the pressurizing device,Improving transmission efficiency orIn order to increase the draft rate, a stepwise drive may be used to make a non-continuous step characteristic or a continuous curve characteristic.
[0016]
  In addition, since the compression force of the pressurizing device may be applied between the transmission wheel and the main body, the arrangement order and location of the elastic device and the compression device between them can be arbitrarily changed according to the design. When these are set in a non-rotating state, a rotation separation bearing may be disposed between any of the transmission wheel, the compression device, the elastic device, and the main body. It is not necessary to place the elastic device and the compression device at the same coaxial position as the transmission wheel rotation shaft.apparatusIt only has to be connected to the transmission vehicle. Therefore, here, the main body or the main body reference plane is a relative reference in the axial direction relative to the transmission wheel regardless of the presence or absence of rotation.LevelIt is a place where the position does not change. When the pressure direction of the elastic body and the pressure direction of the transmission wheel are opposite to each other, pressure transmissionapparatusAlternatively, the pressurizing direction may be reversed by a lever function such as seesaw.
[0017]
  Furthermore, the elastic device and the compression device have the same members as the responder, the responder, the driven object, the driven tool, and the pressure transmission.apparatusThese members may be referred to as sliding members, sliding bodies, or sliding tools that transmit pressure to other members, and may be shared with each other as a single member depending on the design. Various selections such as reverse or substitute with a member such as a disk or main body of a transmission wheel are performed, but these are only within the scope of the selection design of the member, and any changes can be made Even if it goes, it is included in the scope of the present invention.
[0018]
  When using a hoisting and sliding device as a compression device,SlidingMechanism is screwbodyIs the most common,7B as well as the sliding camEven a rotating cam with a cam on the circumferential surfaceBecause it uses an inclined surfaceReach equivalent function. AlsoSlidingThe mechanism needs to correspond one-to-one with the shift command,SlidingWell-known self-locking function in the mechanism, that is, a brake function for preventing reverse rotation andReversible control drive sourceThe overrun prevention function that occurs in the motorOn the drive source sideis necessary. Therefore, a combination of various well-known technologies such as a combination of a trapezoidal screw and a worm transmission machine, a combination of a normal screw or ball screw and a motor with a brake, a clutch device installed in a transmission command transmission system, and a reverse rotation prevention step motor is considered. Should be. Further, the amount of pressing movement of the compression device needs to be the sum L0 (= L01 + L02) of the shifting movement L01 of the first transmission wheel and the pressing movement L02 of the elastic device. Therefore, the movement amount L01 and the movement amount L02 are set separately.SlidingYou may comprise by a mechanism. On this occasionFirst transmissionThe amount of movement L0 on the car side is inevitablySecond transmissionWhat is L1 on the car side?Requires synchronous driveBecause the operating direction and operating amount are different,SlidingMechanism screwbodyWell-known factors such as the pitch, rotation direction, rotation speed, thread groove processing direction (right screw, left screw), speed ratio of the transmitter, etc. may be selected according to the design.
[0019]
【Example】
(First embodiment)
  1 to 4 show a first embodiment of a speed change control device of the present invention.ITheFirst (subordinateMovement)andSecond (mainMovement)Variable speed transmission device constructed by winding a transmission body around a transmission wheelIIThe structure of each part of the continuously variable transmission for vehicles applied to and the characteristics of the pressure device are shown. The transmission 10 is basically composed of a second (primary) transmission vehicle or main vehicle 2, a first (driven) transmission vehicle or driven vehicle 1, and a transmission body 11 wound between the two transmission vehicles. Variable speed transmissionIIWhen,first(Follow) TransmissionA first (driven) actuator 6 on the vehicle 1 side;second(Main movement) TransmissionOn the car 2 sidesecond(Main movement)Operation device 8 and both operationsvesselDrives 6 and 8 synchronouslyRudeShift control device formed with the power source 9IIt consists of. Moresecond(Main movement)The operating device 8 is supplied from the driving source 9 to the urging device 12.WhenSliding device 15WhenConsist ofSecond pressureSecond pressurizing device energizing the compression device 147Havefirst(Follow)The operating device 6 compresses the elastic device 3 and the elastic device 3.firstA first pressurizing device 5 constituted by the compression device 4 is energized by a drive source 9.firstThe compression device 4 is formed by a sliding device 25 and an urging device 29 that drives the transmission wheel 1 and the elastic device 3. The speed change control device I of the present invention includes:first(Follow)Transmission wheel 1,second(Main movement)Variable pressure control of transmission wheel 2firstandsecondPressure device 5,7Havefirst(Follow)andsecond(Main movement)The operation device and the drive source 9 will be described in detail below.
[0020]
  In the transmission wheels 1 and 2, the sliding disks 1a and 2a and the fixed disks 1b and 2b are opposed to each other, and the former is opposed to the latter through a key.Of each rotary shaft 20, 50It is configured to be slidable in the axial direction.On the input shaft 20 and the output shaft 50 respectively.They are arranged opposite to each other. By controlling the balance of the applied pressure from the operating devices 6 and 8 corresponding to both transmission wheels 1 and 2, the contact radius r with the transmission body 11 in both transmission wheels 1 and 2 is continuously changed. Power transmission of a predetermined horsepower is achieved in the speed change region. 1, the position of the maximum speed ratio is drawn in FIG. 1, and the right half is drawn at the maximum diameter and the left half is drawn at the position of the rotation speed 60% with the radius r0 in FIG. In addition, the transmission 10 forms a sealed oil tank chamber with the main body 10a and the lid body 10b, constitutes a wet transmission, and is connected to an internal combustion engine such as a vehicle, a transmission device, and the like. Meanwhile, the shift control deviceIAre centrally arranged on the side of the lid 10b which is a part of the main body 10.
[0021]
  Of the main actuator 8secondPressurizing device7IsSecond pressureA sliding device 15 as a contracting device 14 and an urging device 12 comprising a main transmission;soComposed. The former is a ball screw pressing device 15.cTwo decoratedFirst and secondIt consists of a sliding tool or responder 16 and a driven tool 17, the latter consisting of a worm 18 and a wheel 19.Self-locking function that prevents reverse rotationThis is a worm transmission machine 12. Pressurizing device7IsPositioning control of the transmission bodyAccurate reproduction of reference position for variable diameter controlSpeed ratio controlTherefore, in order to remove unstable positioning factors such as elastic force, the sliding device 15 made of a rigid member is shown. As shown in FIG., HoEel 19InMade of the same material as thisCircleTubularForming a part therePress device 15cConfigured and pressurizing device7 centerAre provided with through holes 16a and 19a, and the sliding shaft portion of the main transmission wheel 2 is arranged to pass through.first(Follow) Actuator6offirstIt is arranged in a concentrated manner so as to be juxtaposed at a position equivalent to the level of the pressure device 5.
[0022]
  While the main drive shaft 20 is supported on both shafts by bearings 21 and 22,secondPressurizing device7Is communicated with the main body reference surface 10ccarThe pressure is applied through bearings 13 and 23 between the two. When the response tool 16 is rotated by the wheel 19, the driven tool 17 does not rotate and slides in the axial direction only by the guide rod 24a.PressureThe screw of the contracting device 14 is processed into a right-hand screw. 24 is a response device, in this exampleHaShown as last receiving tool. Pressurizing device of FIG.7Therefore, the displacement of the contact diameter r1 of the transmission body 11 is controlled by direct pressure only from the main body 10c to the sliding disk 2a without any elastic force.
[0023]
  Of the driven actuator 6firstThe pressurizing device 5 is not installed in the periphery of the sliding disc 1a even though the sliding disc 1a is slid and pressed.second(Main movement)It is installed in a non-rotating state on the lid 10b on the same plane as the operating device 8.Axis torque control is performed together with the elastic device 3. 1 and 2, the pressurizing device 5 is provided on the left and right sides of the screw body 26.Arranged at a non-coaxial position with the transmission wheel rotation shaft via the connecting levers 28a and 28b.Two transmissionsmeans41a, 41b, linear ball bearings 42, 43 and shifterlever44, and a pressure transmission that transmits the applied pressure via a gimbal 47, a thrust receiver 46, and a bearing 45 disposed in the transmission wheel 1.apparatus40. The internal structure of the pressurizing device 5 includes an elastic device 3 andSecond pressureThe same function as the compression device 14firstThe compression device 4, both of which use the bearing 31 as a joining pointElastic force andAn example of elastic pressing force in which the pressing force is joined in series with each other is shown. The pressing force of the elastic device 3 is based on the bottom cover 36 as the main body reference surface 10c, from the bearing 31 to the compression device 4,pressureTransmissionapparatusAfter 40, to transmission wheel 1ElasticityApply as pressure. The pressurizing device 5 is transmitted to the lid 10b as a single structure 5 along the line III-III in FIG.ReachIt is configured to be detachable on the same axis as the car 1.
[0024]
  As is obvious to those skilled in the art from FIGS. 1 and 2, the elastic device 3 is provided with a plurality of annular elastic bodies 33 coaxially and concentrically with the rotational axis of the transmission wheel 1 and pressable in the axial direction. This is an example in which a single structure 30 that is stored in advance in a predetermined pressure state in 35 and can be detached independently is formed. A special structure is adopted in order to secure a large pressing force in a narrow space that cannot be formed by a single elastic body. The four elastic bodies 33a to 33d are individually attached to the main body 10 at one end and annular responders 37a to 37d respectively provided with connecting portions 39a to 39d for engaging the other responders at the other end. . In order to effectively operate each elastic body, it is common technical knowledge for those skilled in the art to support elastic vibration transmission at one end but not at the other. Three step contact portions 38b to 38d and a bottom lid 36 are applied to the inner wall of the casing 35 as a locking device 32 for the elastic body 33. In this example, there is no abutting portion 38a corresponding to the first-stage elastic body 37a, but this is to connect with the compression device 4 in order to select the minimum pressure Pmin from the beginning in the initial pressurization state. You may give beforehand, as shown by the dotted line 38a. Since the innermost diameter of each step contact portion 38 is larger than the innermost diameter of each corresponding responding body 37, it protrudes from the adjacent step contact portion 38 in the preceding stage. Accordingly, as the compression device 4 responds, the responding tool 26 is guided by the responding bodies in the order of the responding bodies 37a to 37d and sequentially presses the elastic bodies 33a, 33b, 33c and 33d, and the applied pressures are arranged in a stepwise manner. It is a structure to add.
[0025]
  The compression device 4 includes a ball screw pressing device 25.cGivenTwo first and second sliders, i.e.A sliding device 25 composed of a response tool 26 and a driven tool 27; and a biasing device 29 composed of a worm transmission 48 for shifting power composed of a worm 48 and a wheel 49 as a self-locking mechanism for preventing reversal. The elastic device 3 is arranged between them. The response tool 26 is formed of a screw body portion 26a, a connecting portion 26b, a sliding portion 26c, and a pressing portion 26d. The sliding portion 26c forms a spline shaft and receives only turning force from the wheel 49 and is transmitted to the screw body portion 26a so as to be slidable in the axial direction. With this configuration, the compression device 4Part of the sliding device 25While being integrally assembled with the elastic device 3 fixed to the main body 10,Can transmit elastic vibrationNot floatingShiSupported in a floating state (floating). In this example, the ball screw applied to the responding tool 16 of the sliding device 15 of the main operating device 8 is right-hand thread processing, whereas the driven operation device6The ball screw of the actuating tool 26 is subjected to left screw pressure. The direction of the thread groove may be changed as necessary. As shown in FIG. 2, the driven tool 27 is provided with a connecting lever 28 having two levers 28 a and 28 b and is connected to the transmission means 41. The response tool 26 of the hoisting device 25 is supported in a floating state at two intermediate positions between the distal end portion 31 ′ of the response body 37 a and the transmission means 41 connected to the transmission wheel 1.Transmits elastic vibrationTherefore, the sliding part 26c has a predetermined length.
[0026]
  DrivingThe power source 9 is a reversible with a brake shown in FIGS. 3A and 3B.controlA DC servo motor is used as the motor 53, and the two transmitters 55, 6 are used.6Is applied to the main and driven actuators 8,6These drive shafts 18a and 48a are simultaneously driven synchronously. Shift power as a shift command is transferred from the shaft 54 to the shaft 58 via gears 56 and 57.At this point, the first and second shift commands are branched.Further, the operating device 8 is moved from the shaft 58 to the shaft 18a by gears 59 and 64.Second gear changeAs a command, the operating device 6 includes the idler wheel 61 and the gears 59 and 62 to move from the shaft 58 to the shaft 48a.First gear changeIt branches as a command and is transmitted to each. The difference in the number of teeth between the gear 64 and the gears 63 and 62 is that the movement displacement amount L0 (= L01 + L02) of the pressurization device 5 of the driven vehicle 1 with respect to the movement displacement amount L1 of the sliding device 15 of the main vehicle 2. This is because it is necessary to move and press both the sliding disk 1a and the elastic body 33 simultaneously. The pressure applied to both transmission wheels 1 and 2 is small when one is large and the other is small.Reversible control drive sourceThe motor may have a small capacity.
[0027]
  Next, the operation of the transmission 10 will be described with reference to FIG.BothPressure device 5,7I will focus on. As shown in FIG. 1, it is assumed that the input / output shafts 20 and 50 are transmitted at a constant speed ratio at a constant speed ratio while the transmission body 11 is in the maximum speed ratio position in the transmission 10. reversiblecontrolMotor 53As rotation speed or speed ratio commandDirection to reduce gear ratioGear shift commandIn other words, receiving a speed increase commandPositiveStart rotatingthingAnd As indicated by the arrows in FIG. 3A, the speed change power is transmitted to the shaft 18a and the shaft 48a and rotates in opposite directions. In this example, the screw body 15 as each pressing device.cAnd screw body 25cSince the reverse screw processing is performed on each other, the radius of the transmission body 11 increases from r10 to r11 when the sliding device 15 pressurizes the disk 2a.Output speed increases and speed ratio decreasesstartBecause,Second gear shift command works as speed ratio command or rotation speed command. At the same time, the pressurizing device 5 that has been pressed with the maximum applied pressure Pmax operates in a direction to reduce the applied pressure of the sliding device 25 of the compression device 4. Therefore, each responder 37 of the total pressure applied to the elastic device 3 also rises to the position shown by the dotted line, and at the same timeSlidingOf the device 25MeetMovementIngredients26 rises and conversely the driven tool 27 descends by the amount of unwinding. This drop isLinkingLever 28 and pressure transmissionapparatusThe pressure applied to the transmission wheel 1 is reduced through 40.Therefore, the shaft torque is reduced, and the second shift command works as a torque command. ThatAt the same time, the pressure device on the main vehicle 2 side7As a result, the radius of the transmission body 11 in the transmission wheel 1 of FIG. 1 decreases from r01 to r02.
[0028]
  This means that the characteristic point (A) on the step line (IV) shifts from the characteristic point a1 to a2 along with the shift from the output speed n1 to n2 of the maximum speed ratio εmax on the characteristic diagram of FIG. Show. At the same time, the pressure P1 is also reduced to P2 to the transmission wheel 1 according to the supply of the speed increase command.Shaft torque also decreasesMeans that. Therefore, it is shown that the pressurizing force and the rotation speed in the transmission wheel 1 are in an inversely proportional relationship. Similarly reversiblecontrolWhen a speed increasing command is further given from the motor 53, the same operation is repeated. Assuming that the output rotational speed is n60, which is substantially half, as shown in the left half of FIG. 2, the elastic bodies 33c and 33d abut against the step contact portions 38c and 38d, respectively, to pressurize the transmission wheel 1. It indicates that only the elastic bodies 33a and 33b are acting at the characteristic point a60 of the staircase characteristic (II) without contributing. Similarly, the pressurizing characteristic decreases stepwise as the rotational speed increases with the rotation of the responding tool 26 of the sliding device 25, and reaches the minimum pressure Pmin at the highest speed.The shaft torque to the transmission wheel 1 is also minimized.. Conversely, to return to the deceleration state again, reversiblecontrolMotor 53TheWith deceleration commandReverseTimesBy rolling, it returns to the original position according to the reverse operation described above.
[0029]
  In the elastic body according to the prior art, as the rotational speed N of the driven vehicle 1 increases, the applied pressure increases as shown by the characteristic line (D) in FIG. On the other hand, in the present invention, the elastic device 3 is made to cooperate with the compression device 4 while using an elastic body of the same quality as that of the prior art in which the compression pressure increases as the compression amount increases.outputThe characteristics between rotational speeds are inversely proportional or inversely proportional to each other.BecomeTo ensure negative slope characteristicsAlso, between the applied pressure and the speed ratio, a positive slope characteristic is used.There is the biggest feature. In the substantially horizontal characteristic line (C0 to C2), the applied pressure per unit area is almost the same in the entire speed range, but the contact area between the belt and the pulley of the driven vehicle 1 is lower than that at the highest speed at the lowest speed. Reach several times. Therefore, even in this characteristic, the shaft torque T received by the transmission body 11 can be increased conversely even if the rotational speed N decreases. Even if the characteristic line (C2) in FIG. 4 has a slight positive inclination, the constant horsepower can be transmitted substantially by the increase in the contact area.. AntiProportional is a concept including a slight positive slope characteristic (C2), and further includes a stepped or non-linear curve characteristic.
[0030]
  Next, the automatic alignment function of the transmission of the present invention will be described. Transmission power transmission has an internal error factor and a variation factor entering from the outside, both of which are obstacles to regular transmission. As a typical example, the former includes elongation in the longitudinal direction of the transmission body 11 and wear in the width direction, and the latter includes supply of a shift command, intrusion of an impact load from an input / output side device, and the like. In any case, the present invention has a function in which the elastic device 3 automatically compensates for adverse effects during operation and automatically returns to the normal transmission operation again. The elastic device 3 has a tension adjusting function that absorbs irregular disturbances in the transmission body tension that occurs in the speed change process, and has an automatic alignment function that guarantees a stable transmission state between the radius and the applied pressure for internal and external irregular factors.
[0031]
  Assume that the circumference of the transmission body 11 gradually increases during operation at the maximum speed ratio ε1. At this time, each actuator 8 of the main drive and the follower,6Is not biased, the contact radius on the main vehicle 2 remains unchanged. However, the radius of the driven vehicle 1 increases according to the extension.Displace the pinching positionTo do. The output speed is decelerated by that amount, and both the disk 1a and the elastic device 3 move slightly. However, the pulley holding pressure P has only a slight change, and the holding pressure on the transmission body 11 is maintained at almost the maximum load. Keep doing. This means that even if the rotation speed changes slightly,StableThe transmission function itself does not receive any obstacles, and indicates that it continues to maintain normal transmission by automatic alignment. Next, consider a case where the thickness of the transmission body 11 due to wear in the width direction is reduced. Also at this time6, 8 is stopped, but the contact radius on the main vehicle 2 is automatically reduced by the pressing of the elastic device 3 on the driven vehicle 1, and at the same time, the radius of the driven vehicle 1 is increased accordingly. Although it decreases slightly, automatic alignment is performed while properly maintaining the normal transmission horsepower.
[0032]
  Further, let us consider the sudden intrusion of shock vibration into the input / output shafts 20 and 50. In this case, the automatic alignment function works in the same manner. On the driven transmission wheel 1 side, a turbulent vibration that expands or contracts the radius r0 of the transmission body 11 occurs only for a moment.ElasticityVibration is reverse pressure transmissionapparatus40 to the compression device 4. At this time, the compression device 4 moves from the driven tool 27 to the response tool 26.pressureBiographyReachHowever, the spline slide shaft 26c at the tip of the response tool 26 is also engaged with the wheel 49 of the biasing device 29 so as to be slidable in the axial direction.StateTherefore, the whole of the compression device 4 is arranged in a floating state except that the compression device 4 is engaged with the connector 32 of the responding body 37 of the elastic device 3. So intruding turbulenceElasticityOnly the elastic device 3 directly absorbs the vibration. The disturbance ends within a short time, and the pressure device 5 automatically returns to the original stable transmission state again.
[0033]
  Next, the pressurizing device 5 of the driven vehicle 1 applies both variable pressure and elastic body as indirect pressurization to the transmission wheel.Elastic pressure generated by series pressurizationWhile supplying, the pressurizing device of the main vehicle 27The reason why only the variable pressurizing force is supplied to the transmission wheel as direct pressurization will be described. This is because the driven vehicle 1 and the main vehicle 2 have the function roles of the transmission vehicles 1 and 2 as continuously variable transmissions.IndividuallyIt is for classification. That is, the follower 1 isBy changing the holding pressure with the constantly applied elastic pressureFor transmission of specified horsepower to the connected load deviceVariable toShaft torqueControl functionAnd self-aligning function of elastic body that returns itself to stable state against internal and external turbulenceIt is. thisOn the other hand, in the main vehicle 2, in order to back up each role of the driven vehicle 1, the always stable disk 2a.Is the transmitter 11PositioningcontrolbyVariable speed ratio orThis is to provide a rotation speed control function. This is because the main car 2Speed ratio orThis is because the vehicle 1 operates as a reference vehicle for rotational speed control, and the driven vehicle 1 performs the function of a follower vehicle for torque control that operates in response to the rotational speed of the reference vehicle.
[0034]
  The pressurizing device 5 of the driven transmission wheel 1 is configured by integrally assembling the elastic device 3 between the urging device 29 of the compression device 4 and the sliding device 25 in the form of a lump, constituting a single structure as a whole, and the main body 10. It is arranged outside the lid body 10a, which is a part of the transmission wheel 1, coaxially with the shaft 50 of the transmission wheel 1 and detachable from the outer III-III line. On the other hand, the pressurizing device for the main transmission wheel 27The sliding device 15 composed of the sliding device 15 and the biasing device 12 is integrally assembled inside the lid body 10b and together with the lid body 10b. Therefore, by releasing the large number of bolts 10e from the main body 10a shown in FIG.IAll pressurizing equipment5and7Is detachable as a transmission integrated with the lid body 10b as the main body 10 from the bearings 21 and 45 and the bearing 52 together with the driven and main transmission wheels 1, 2 along the IV-IV line. It should be noted that the tip of the screw shaft 26 is not connected to the shaft 50 and is accommodated by borrowing an opening 50a for preventing contact.soSeparated and detachable.
[0035]
(Second embodiment)
  FIG. 5 shows a cross-sectional structure of the second embodiment of the present invention used in a continuously variable transmission for a machine tool such as a milling machine or a drilling machine. Of the present inventionShift controlapparatusIIs leftAnd right~ sideInFollowAnd main driveTransmission wheel 12Has been applied. Since all the embodiments after the present embodiment have substantially the same basic operations and functions, the same reference numerals as those in the first embodiment described above are used, and only the main differences will be described. The first difference is the screw shaft of the urging device 29 of the compression device 4.The first sliding tool26 isPressure transmission to the sliding disk 1a via a coaxial through hole 65 provided on the rotating shaft 50 of the transmission wheel 1apparatusIt has 40 functions. Second, the sliding device 25 drives the transmission wheel 1 for the variable speed sliding portion L01.1Sliding device 25aAnd the first driving device for the compression movement L02 of the elastic device 3.2The sliding device 25b is divided into two parts, both of which are screw shaftsThe first sliding tool26 andThat is, the urging device 29 is shared and arranged on the front side and the back side of the transmission wheel 1. And screw shaftThe first sliding tool26Is two types of screw bodyPressing deviceThe screw grooves 26a and 26b are mutually subjected to reverse screw pressurization.Second of two nutsSlidingIngredients27a, 27bScrewed togetherOperate in opposite directionsing. Accordingly, as shown separately on the left and right of the drawing, the disk 1a of the transmission wheel 1 is also pressed at the same time as the elastic device 3 is pressurized. ). Although the rotary shaft 50 has a cantilever structure with a bearing, the idea of this example can also be applied to a double-bearing support structure as in the first embodiment. Third, the responding body 37 of the elastic device 3 slides on the sliding device 25b.IngredientsIt is energized by 27. Fourth,The first embodiment is the same as that between the wheel and screw shaft.For example, the urging device 29 composed of a worm transmission device is configured independently.
[0036]
(Third embodiment)
  In the third embodiment shown in FIG. 6A, the elastic device 3 and the compression device 4 shown in the second embodiment shown in FIG. 5 are all part of the main body 10 on the sliding disk 1a side of the transmission wheel 1. 10b is an example of arrangement. Also in this case, the operation function of the transmission wheel pressurizing device 5 is substantially the same as that of the second embodiment. The main differences other than those described above are that the elastic body is single in the first place, and the response tool 26 of the compression device 4 is the pressure transmission of the second embodiment.apparatus40ShrinkThird, when the lid 10b is removed from the main body 10, the bearing 45, the responding device 28,BetweenThe pressure device 5 with the elastic device 3 and the compression device 4 can be detached from the main body 10 as an integral structure, and has been subjected to belt replacement maintenance.
[0037]
(Fourth embodiment)
  The embodiment of FIG. 6B is an example in which only the elastic device 3 in the second embodiment of FIG. In this case, the difference from the embodiments of FIGS. 1 and 5 other than those described above is that the housing 35 is directly attached to the transmission wheel 1 and the disk 1a itself forms a part of the housing 35. It is. Rather than sequential driving of a plurality of springs, a single spring or a plurality of springs may be driven simultaneously. In the case of a leaf spring, it is easy to ensure a dynamic balance. Secondly, the responding body of the elastic device 3 is divided into five responding bodies 37 in which a plurality of responding bodies are interlocked with each other, and the responding means 28 on the compression device 4 side is also used as the driven member 27 of the hoisting device 25. And responder 27 and responderbodyThis is that a bearing is arranged between 37. The bearing 45 may be provided between the disc 1a and the elastic body 33. The operation of the pressurizing device 5 is the same as in the embodiment of FIG.Since the elastic device 3 is installed directly on the transmission wheel 1Biasing device 29 of the compression device 4Is fixed to the screw shaft 26Others are the same as the examples of FIGS. 5 and 6A.soWell-known commercial warMudenSince it is a master machine, illustration is omitted.
[0038]
(5th Example)
  The embodiment of FIG. 7A is an example of a transmission wheel pressurizing device 5 in which the transmission wheel 1 is supported by both bearings as in the embodiment of FIG. The main difference from the other embodiments is that a plurality of elastic bodies 33 arranged in parallel concentrically are always compressed simultaneously by the compression device 4. Unlike the cases of the embodiments of FIGS. 1, 5, and 6B, the pressurization characteristics are not stepped, but linear characteristics can be obtained as shown by the characteristic line (A ′) in FIG. The elastic bodies 33a and 33b and the elastic body 33c are made of a right-handed spring and a left-handed spring, and cancel the compressive strain to the bearing 45. Secondly, the housing 35 has an input side response body 37 and an output side response body.body36 and the combined locking device 32 is applied, and the whole is in a floating state. Third, the urging device 29 is not a worm transmitter but a bevel transmitter.
[0039]
(Sixth embodiment)
  The embodiment of FIG. 7B is an example in which pressure is directly applied by the elastic body 33 similar to the embodiment of FIG. 6A. Other examplesWhenIs different from the sliding device 25 of the compression device 4 in thatWith horizontal camThe movable tool 27 moves horizontally on the main body 10a.Vertical cam slideThe moving tool 28 presses in the vertical direction. In this case, the pressing device 25c isSlidingMotion tool 26,SlidingCam inclined joint surfaces 26c and 27c are slidable in the direction perpendicular to each other.soThere is a difference in that the elastic device 3 is compressed and pressed by horizontal / vertical conversion sliding of both cams. Further, in this example, the urging device 29 is a hoisting composed of screw bodies 48 and 49.Screw transmission machineThere are points made up of
[0040]
(Other examples)
  In the present invention,During pressurization control of the first (driven) transmission wheel, Elastic body, not hydraulic direct pressurization methodInterventionDepends on the indirect pressurization method, but “direct” means only the supply of applied pressure, and “indirect” means both applied pressure and elastic force.Elastic pressure generated byMeans supply. Therefore, in this specification, the drive source of the shift control unit isAs a reversible control drive sourceElectrical reversiblecontrolAlthough described with a motor, it is not limited to this.pumpSuchTheVarious motors such as fluid motorsDriven byIndividually for each actuatorThe drive sourceEven if you arrangeAlsoIt may be shared, and in that casefirstandsecondEach sliding device of the compression device andeachHoisting with a screw body such as a ball screw or trapezoidal screw on the pressure deviceSlidingapparatusBesides hydraulic cylinderCan be used to change the transmission of a large capacity transmission at a high speed. In addition, the main actuator 8 transmits pressure from the main vehicle 2.apparatusIt may be installed at a remote position via 40, and further on one or both of the main and driven actuators.ControllerYou may give a through-hole and arrange | position a rotating shaft through.
[0041]
  Furthermore, as the speed change control device divides the roles of the control function of the drive gear and the driven vehicle of the speed change transmission device, the drive source can be divided into individual drive sources according to each operation device. Separately from the two actuators, only torque adjustment can be performed, and the value of the shaft torque can be set arbitrarily.In particular, it is possible to improve the transmission efficiency by controlling the output capacity on the continuously variable transmission side closer to or away from the actual load capacity required on the output load device side, and to control the safety factor with respect to the actual load capacity. That is, by providing a predetermined deviation between the pressure characteristic A of the elastic pressure force of the elastic device and the pressure characteristic B required for the actual load, the transmission has a safety factor and a service factor corresponding to the transmission capacity. By changing the pressurization characteristic A by the elastic device as necessary so that it can be set or changed, it is possible to provide the transmission device with high transmission efficiency or safety factor. In order to increase the safety factor in a part of the gear ratio range, a non-linear pressurizing device having a negative inclination with respect to the rotational speed of the driven vehicle may be provided. Also, the transmission efficiency of the transmission may be selected by optimizing the shaft torque while suppressing heat generation due to the holding pressure between the transmission body and the transmission wheel.Therefore, the present invention is included in the scope of the right even if various modifications or changes are made in accordance with the design specifications within the scope that can be easily created by those skilled in the art from the “claims”.
0042]
【The invention's effect】
  In the present invention, one of the two transmission wheels is accompanied by an inelastic pressure state, and the other is accompanied by an elastic pressure state.Control functionRoleIndividual shareSeparated into both carsTheA further improvement in both applying pressure and applying an inversely proportional force between the applied pressure and the rotational speed to the other side, resulting in a high-quality continuously variable transmission.Establishment of stable transmissionIn addition, the shift control device for a constant horsepower continuously variable transmission that achieves high speed response and high efficiency operation has been realized. That is, both pressurization devices for main and driven actuatorsWindingUpOr hydraulic slidingBelt positioning on both transmission wheels by adopting the deviceSpeed ratio by operationControl andBy belt clamping pressure operationThis means that high-precision reproducibility can be given to shaft torque control. In particular, as is conventionally done with hydraulic control, detection and electronic detection are individually performed for each factor such as hydraulic oil operation delay, oil temperature change, oil spill, centrifugal force, and poor response due to valve control. There is an effect that it is not necessary to repeatedly perform circuit compensation.
0043]
  In the present invention,SlidingReproducibility of belt positioning control and torque control of each transmission wheel by the device is a basic component requirementAs well asIn addition, the following components are added for high speed response and high efficiency.Stable transmissionRealized. That is,(1)The high speed response of the shift control is secured by adding the high degree of synchronism of the shift command between the main actuator, the driven controller and the drive source.(2)Next, both controllersExample of operating the compressor with an individual drive sourceBy adopting the shift control device sideOnly torque can be operated individuallyofsoWith high efficiency operationSafety factor adjustmentEnable further(3)The linear or non-linear pressurization characteristics are configured so that the compression and pressurization characteristics A by the elastic device match the optimum conditions as much as possible to the actual load pressurization characteristics B that are optimal for the actual load capacity, and transmission efficiency or safety factor is required. By selecting and adding accordingly, high efficiency or safety factor operation on the side of the transmission is realized. In particular, in order to increase the transmission efficiency or the safety factor in a part of the shift range, a pressure characteristic having a negative slope with respect to the rotation speed or the gear ratio of the first transmission wheel may be selected and added.
0044]
  Therefore, according to the idea of (1) above, it is possible to respond to the speed change control within a very short time from the maximum speed ratio εmax to the minimum speed ratio εmin, and for a machine that repeats sudden start and stop like a vehicle.MechanicallyIt is optimal with sufficient follow-up ability. Moreover, when the drive source is an electric servo motor or the like, it operates only at the time of shifting operation, and it is not necessary to maintain a constantly operating state like a hydraulic pump.However, each pressurizing device may be a hydraulic cylinder if it does not always maintain the operating state.. Furthermore, it is obvious to those skilled in the art that the two operating devices do not need to apply a large pressing force at the same time, and when one is large, the other becomes small, so that the drive source can be sufficiently handled by a small single shared motor. .
0045]
  Further, according to the above-mentioned ideas (2) and (3), not only can the deterioration and wear due to frictional heat generation of the members be reduced in both the speed change control device and the speed change transmission device constituting the continuously variable transmission, It is also obvious to those skilled in the art that a significant reduction in fuel consumption can be achieved and that it is effective for environmental conservation when applied to both vehicles.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a continuously variable transmission for a vehicle using a speed change control device according to a first embodiment of the present invention;
FIG. 2 is a longitudinal sectional view taken along line II-II of the continuously variable transmission shown in FIG.
3 shows a part of the synchronous drive source of the controller of the continuously variable transmission shown in FIGS. 1 and 2, FIG. 3A shows the configuration of the second transmission device, and FIG. 3B shows the configuration of the first transmission device. In the partial cross-sectional view shown,
FIG. 4 shows the apparatus of the first embodiment.First biographyCarWhatofElasticityIt is a characteristic view which shows the relationship between applied pressure and rotation speed.
FIG. 5 is a sectional view of a continuously variable transmission for a machine tool to which a second embodiment of the present invention is applied.
[Fig. 6] Fig. 6 shows a single bearing support.First biographyTo the carSuitablefordidFIG. 6A is a cross-sectional view of the third embodiment of the present invention, and FIG. 6B is a cross-sectional view of the fourth embodiment of the present invention.
[Fig. 7] Fig. 7 shows the support of both bearings.firstFIG. 7A is a sectional view of a fifth embodiment of the present invention, and FIG. 7B is a sectional view of a sixth embodiment of the present invention.
[Explanation of symbols]
    I Shift control device
    II transmission
    1 Driven vehicle, driven transmission vehicle or first transmission vehicle
    2 Main vehicle, main transmission vehicle or second transmission vehicle
    3 Elastic device
    4 Compression deviceOr first compressor
    5 Pressurizer or first pressurizer
    6 Followed actuatorOr the first actuator
    7 Pressurizer or second pressurizer
    8 Main actuatorOr second actuator
    9 Drive source
  10 Transmission
  10a Body or body reference plane
  10b Lid
  11 Transmitter
  12, 29 Energizing device, Worm transmission machineOr variable speed power transmission
  14 Compression deviceOr second compression device
  15 Sliding deviceOr second sliding device
  15c, 25c  Press device
  16, 26 Response tool, screw body, Cam bodyOrfirstSlider
  17, 27 Driven tool, screw body, Cam bodyOrsecondSlider
  25a, 25b Driven tool, screw body, Cam bodyOrsecondSlider
  25 Sliding device or first sliding device
  25a First sliding device
  25b Second sliding device
  32 Locking device
  33 Elastic body
  35 body
  36 Driven body or sliding body
  37 Responsive body or sliding body
  40 Pressure transmissionapparatus

Claims (12)

In a transmission control device for a transmission that wraps a transmission body that is displaced in the holding position by each sliding disk between the first and second transmission wheels and pressurizes and controls both the sliding disks ,
A first operation device that variably applies an elastic pressure obtained by the first compression device of the first pressure device to the elastic device in series , and a second compression device of the second pressure device . A second operating device that variably applies inelastic pressure to the second transmission wheel, and a drive source that synchronously supplies first and second shift commands to the first and second pressurizing devices, respectively. The first and second actuators include a sliding device that displaces the relative position of each compression device between the two sliding tools and an urging device that inputs the corresponding shift command and urges the sliding device. configuration to Rutotomoni, the second compression device and a variable control function of the transmission member contacting a radial positioning control to the number of output rotation to the second transmission wheel or speed ratio at the non-elastic pressure force the first the transmission body holding pressure compressor is in elastic pressure to control a variable pressurization facilities variable control function of the output shaft torque to the first transmission wheel , Formed by the transmission control Teibariki power by being operated individually each pressure device shift control device. In a transmission control device for a transmission that wraps a transmission body that is displaced in the holding position by each sliding disk between the first and second transmission wheels and pressurizes and controls both the sliding disks ,
A first manipulator which first compression device of the first pressurizing apparatus applying a variable shaft torque By applying an elastic pressurizing force obtained by applying series pressure to the elastic device to the first transmission wheel, the second pressing device A second compressor applies a non-elastic pressure to the second transmission wheel to apply a variable speed ratio , and further sends first and second shift commands to the first and second pressurizing devices, respectively. Each of the first and second actuators is configured to displace the relative position between the two sliding tools. and the corresponding shift command is input the configuration to Rutotomoni by a biasing device for biasing said sliding device, the reverse transfer of the said respective pressure gave constituted by warm transfer machine in the biasing device the self-locking function of preventing and installed the brake device or the clutch device to the drive source overrun reversible control drive source By performing reaches blocking function, Teibariki power by preventing mutual propagation of said first and second pressure device or between the respective pressure device and the false signal to the first and second shift command between the drive source A transmission control device that controls transmission. The first or second operating device according to claim 2, wherein a shift command corresponding to a worm gear of the worm transmission device is input, and a transmission wheel rotation shaft corresponding to the wheel gear is disposed so as to penetrate therethrough. A speed change control device comprising a cylindrical portion integrally formed of the same member as the wheel gear and having a cylindrical through hole, and one pressing device of the two sliding tools arranged on the cylindrical portion . In a transmission control device for a transmission that wraps a transmission body that is displaced in the holding position by each sliding disk between the first and second transmission wheels and pressurizes and controls both the sliding disks ,
A first manipulator which first compression device of the first pressurizing apparatus applying a variable shaft torque By applying an elastic pressurizing force obtained by applying series pressure to the elastic device to the first transmission wheel, the second pressing device A second compressor applies a non-elastic pressure to the second transmission wheel to apply a variable speed ratio , and further sends first and second shift commands to the first and second pressurizing devices, respectively. Each of the first and second actuators is configured to displace the relative position between the two sliding tools. configuration to Rutotomoni, the corresponding transmission wheel to the first and manipulator holes applied to the center one of the second compression device rotates at and entered a shift command corresponding biasing device for biasing said sliding device coaxial position or the rotational axis and non-coaxial position of the rotating shaft through hole for performing other through arranged axis coaxially direction corresponding transmission wheel axle The first shift command that is disposed linked disposed pressure transmitting device or the both compression device each corresponding transmission wheel rotating shaft subjected to a respective operating device through hole penetrating arranged, axially torque control from outside or inside the respective rotation axis And a second gear shift command for speed ratio control are separately provided to control transmission of constant horsepower power. 5. The first operating device according to claim 4, wherein the first operating device is separated from the inner axis of the rotating shaft through hole in the axial direction applied to the first transmission wheel or the outer side of the rotating shaft, coaxially or non-coaxially. A speed change control device comprising the pressure transmission device comprising a transmission means for transmitting pressure or power to the bearing and a bearing for supporting and guiding the sliding movement of the transmission means in the axial direction. 6. The compression device of the first pressurizing device according to claim 4 or 5, wherein the compression device of the first pressure device transmits elastic vibration between the first transmission wheel and the elastic device when the elastic device is disposed on the main body side. A shift control device that is supported in a fixed state so that elastic vibration can not be transmitted between the main body and the elastic device when the elastic device is arranged on the first transmission wheel side in a floating state. In a shift control device for a transmission that pressurizes a shift transmission device that is wound around a transmission body that is displaced in the holding position by each sliding disk between the first and second transmission wheels,
A first manipulator which first compression device of the first pressurizing apparatus applying a variable shaft torque By applying an elastic pressurizing force obtained by applying series pressure to the elastic device to the first transmission wheel, the second pressing device A second compressor applies a non-elastic pressure to the second transmission wheel to apply a variable speed ratio , and further sends first and second shift commands to the first and second pressurizing devices, respectively. Each of the first and second actuators is a sliding device for displacing the relative position between the two sliding tools. and the corresponding shift command is input the configuration to Rutotomoni by a biasing device for biasing said sliding device, said at the time of operating the transmit power at the time of operation by a common drive source mechanically branched supply or separate drive source The first and second speed change commands supplied via the individual drive sources are individually given as torque and speed ratio commands, respectively, and Another drive sources comprising a Teibariki power changeable so chosen granted to only the value of the shaft torque in order to select the power transmission efficiency or the safety factor of the speed change transmission apparatus transmission control and when operating the shift control device. According to claim 1, 2, 4 or 7, the first operating unit may increase a torque command to the elastic pressure applied to said first transmission wheel to pressure increase with the deceleration command output rotational speed by the rotational speed command said first transmission wheel to reduce the torque command for depressurizing with the Shimada acceleration command and formed by controlling the elastic device shift control device. 8. The drive source according to claim 1, wherein the drive source has a reversible control drive source composed of an electric control motor or a fluid drive motor, and does not always maintain an operating state and is corrected according to a corresponding shift command only during a shift operation. A shift control device comprising the reversible control drive source that performs reverse switching operation . 11. The first and second operating devices according to claim 10, wherein the first and second compressors are formed by using the two sliding tools of the sliding devices of the first and second compression devices as screw bodies of male and female screws, horizontal cams and vertical cams. A shift control device comprising a cam body or a hydraulic cylinder of a piston and a cylinder . 8. The first operating device according to claim 7, wherein the pressurizing characteristic A in which the elastic pressing force of the elastic device is inversely proportional to the output rotational speed is applied, and the pressurizing characteristic A is applied to the elastic pressing force at an actual load. A transmission control device that adjusts the transmission efficiency or the safety factor by giving a predetermined deviation amount close to and away from the pressure characteristic B. 8. The shift control device according to claim 1, wherein the transmission is applied to a transmission for a vehicle or a machine tool in order to shift the power of an internal combustion engine or a motor .

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