JP2000145907A - Continuously variable transmission and shift control device for the transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the size of the whole apparatus while stable operation is guaranteed by winding a transmitting body between a main driving wheel and a driven wheel which are transmission wheels formed by a sliding disc and a fixed disc and having a variable effective diameter, and arranging side by side the transmission wheels with the shift instruction introducing ends thereof disposed on the same plane side. SOLUTION: This shift transmission device I comprises a transmitting body 11 wound between a main driving wheel 2 and a driven wheel 1, wherein sliding discs 2a, 1a of the respective transmitting wheels 2, 1 are axially slid and displaced by operating units 8, 6 to vary the winding diameter of the transmitting body 11, that is, very the change gear ratio. The shift transmission device I includes a shift control device II for synchronously driving the operating devices 8, 6 by a common driving source 9. The pressurizing devices 8', 5 constituting each operating device 8, 6 are arranged side by side and adjacent to each other to be operated for adjustment and replacement of the respective parts from the outside of the main body on the same plane side. The main driving operating unit 5 is taken as a reference wheel, the operating unit 8' is taken as a driven wheel, and the shift instruction introducing ends of both operating units 5, 8' are disposed on the same plane side of the main body.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a constant horsepower transmission type continuously variable transmission and a shift control device used for industrial machines such as machine tools, vehicles, motors, and the like, and more particularly, to secure stable transmission and high-speed response controllability. The present invention relates to a continuously variable transmission and a transmission control device for the same, which have a compact and integrated structure.

[0002]

2. Description of the Related Art A Japanese patent application is filed as a continuously variable transmission pursuing constant horsepower transmission; Japanese Patent Application Laid-Open No. 52-98861 (Fundall Nezu), and a Japanese patent application is issued as a transmission vehicle pressurizing device:
Japanese Patent Application Laid-Open No. 9-217819 (Fundall Nezu) is known. The sliding disc itself of the two discs constitutes a part of a hydraulically driven piston cylinder as a pressurizing device, which can directly press and slide the disc to reduce the radius of the transmission wheel and the transmitting body. This is a pressurizing device that changes and changes the speed. The direct pressurization device using hydraulic pressure has two advantages that an arbitrary pressure from large to small can be obtained in a small space and that a bearing as a consumable is not required. However, hydraulic control has two fatal and critical drawbacks for the transmission. The disadvantages are that, because the hydraulic pressure is not elastic, if the transmission vehicle is directly pressurized, elasticity absorption and self-alignment action cannot be ensured against impacts and errors, etc., hydraulic medium delays operation, oil temperature fluctuations, oil leakage, centrifugation In addition to disturbances in force, etc., the oil pressure becomes momentarily unstable for each shift command due to the control by the relief valve.
Both the driven vehicles are directly affected by the instability at the same time, so that the transmission operation of the most basic belt transmission itself is always exposed to instability factors.

[0003] The disadvantage is that the transmission originally corrects irregular factors such as errors and fluctuation factors which are generated internally or intrudes from the outside and automatically returns to the original stable transmission state. Cannot be held. That is, the internal factors include the wear of the transmission friction surface between the stretch belt and the pulley of the belt and the like, and when hydraulic pressure is used, the above-mentioned drawback factors are added to this. Further, as an external factor, there is an impact vibration that enters an input prime mover and an output load device due to an irregular situation. Further, the shift command itself supplied from the shift control device instantaneously causes a point contact state on the transmission friction surface, which becomes an irregular factor as disturbance. All of these factors adversely affect both output speed and shaft torque. Even if detection and correction are repeatedly performed in the electronic control unit for each factor, it is practically impossible to correct all the factors. Therefore, it is impossible to transmit the transmission by only the pressurization control using the hydraulic pressure.

Normally, the horsepower P transmitted by the transmission vehicle 1 to the load equipment
Is expressed by the following transmission relational expression as a relationship between the rotation speed N and the torque T. That is, P [W] = 1,027 × N [rpm] × T [kgm] (1) Therefore, in order to transmit the predetermined horsepower PO, the torque T of the transmission body is decreased when the rotation speed N increases. Conversely, when the rotational speed N decreases, the torque T needs to be increased. However, in the prior art described above, elastic means such as springs are provided in parallel with the disk of the driven transmission vehicle, but the compression force supplied to the sliding disk by the elastic means increases as the rotation speed increases. Conversely, the pressure is reduced as the rotation speed becomes lower. This is because the direction of the compression force of the elastic means is completely opposite to that of the transmission of the constant horsepower transmission, although it is necessary to increase the applied pressure as the rotation reaches the lowest speed. That is, the transmission vehicle pressing force is directly proportional to the output rotation speed. Accordingly, it is impossible to realize constant horsepower transmission in principle with this kind of elastic pressing device.

[0005]

SUMMARY OF THE INVENTION The present invention relies on an indirect pressurizing method using an elastic body selectively instead of a direct pressurizing method using hydraulic pressure when controlling pressurization of two transmission wheels. A transmission and a shift control that perform constant power transmission by constantly supplying both the pressing force and the elastic force to one of the two transmission vehicles while maintaining the inelastic force only by the pressing force. In particular, the present invention realizes constant horsepower transmission by variable pressurization control in a direction in which the relationship between the rotational speed of the power transmission vehicle and the sheave pressure is inversely proportional. The common problem of the present invention is that constant horsepower transmission requires an elastic body having a huge size and shape that is indispensable in the transmission, and the arrangement, configuration, control and various components of two complicated transmission vehicle pressurization control systems associated with a special pressurizing mechanism. It is an object of the present invention to solve the problems of efficiency and to downsize the entire transmission while maintaining and assuring stable power transmission.

A first problem to be solved is that, in a state where each pressurizing device is directly mounted on two transmission vehicles, the entire transmission can be shared in order to avoid unnecessary enlargement of the entire transmission. All or part of the first or second pressurizing device is centrally arranged as the main equipment part of the speed change control device such as a large size, or a consumable item or a device that requires frequent replacement to increase versatility and It is an object of the present invention to optimize transmission and reception of a pressing force or an elastic force between each pressurizing device and each transmission vehicle, and to enable various operations from or toward the outside of the transmission.

[0007] The second object of the present invention is to determine the detailed arrangement of each pressurizing device of the main / slave operating device after determining the layout concept of each main device of the main / slave operating device in the first solution. In particular, only the pressing force and elastic force are applied between the first pressurizing device and the driven transmission vehicle, and only the pressing force is applied between the second pressing device and the driven transmission vehicle. The basic transmission form, which is the major premise of stable transmission of constant horsepower in the entire speed range, is to make the inelastic state positive, to absorb irregular vibrations and error factors generated from inside and outside by applying each, elastically absorb and automatically align. The purpose is to centralize the shift control device while ensuring and maintaining the speed.

[0008] A third solution is to establish a basic type of constant horsepower stable transmission in the second solution, and then, the transmission control device guarantees stable transmission to the transmission, and at the same time, the output side driven transmission vehicle Providing a means to actually guarantee constant horsepower supply, ensuring a high degree of synchronism with the gearshift command to the master and slave actuators and providing a stable supply, reducing the time required for gearshifting from maximum to minimum speed ratio The purpose is to ensure stable transmission even when the length is reduced to a high degree.

A fourth object of the present invention is to provide a shift control device and a shift transmission after establishing the main parts of the shift control device, the detailed structure, and the main technical idea of high-speed shift control. In this case, the transmission is integrated into the main body and put together into a single transmission.At this time, consideration must be given to stable transmission when high-speed transmission control is performed for the transmission that consists of both transmission vehicles and transmission bodies. In addition to the above, it is an object of the present invention to thoroughly reduce the size of both the transmission and the transmission control device.

A fifth object of the present invention is to improve the assembling work machine and disassembly maintenance for mass production and to construct the continuously variable transmission as a single structure after the establishment of the fourth problem. At the same time, for example, the continuously variable transmission adapted to various transmission capacities can be instantaneously realized simply by replacing the elastic device on the side of the transmission control device and replacing the transmission wheel and the transmission body on the transmission side of the transmission. It is enough versatility and freedom to design.

[0011]

A solution common to the present invention is to control all or a part of the components of each operating device on the side of the shift control device when shifting the speed of both the driven and driven transmission vehicles. Instead of arranging the transmission gears separately according to the arrangement of the transmission vehicle, if necessary, collectively dispose them on the same plane side of one of the main body or the lid body, that is, the first or second main body, etc. However, the aim is to achieve stable control, high-speed shift control, and further improve maintainability and mass productivity.

[0012] The first means for solving the problem is that all or a part of one of the first and second pressurizing devices constituting the driven and driven actuators is arranged by the other pressurizing device. It is arranged on the same plane as the main body to be driven, and transmits and receives pressure mutually via a force transmitting device between a main driving or driven transmitting vehicle interlocking with one of the pressurizing devices, and By arranging them on the same plane side, the driven and driven actuators are arranged adjacent to each other on the same plane side as the main body so that operations such as adjustment and replacement of each part can be performed from outside the main body.

The second object of the present invention is to ensure stable transmission at the speed change transmission device even if the speed change control device is centrally arranged. A variable position control function of the contact diameter between the main transmission vehicle and the transmission body as a reference vehicle, and a variable operation control device for the driven transmission vehicle as a following vehicle for applying a predetermined shaft torque to the driven transmission vehicle. In order to perform the function, the driven and driven actuators are arranged such that the respective shift command introduction ends of the first and second pressurizing devices are arranged on the same plane side of the main body and are energized by the drive source. Things.

A solution to the third problem is that, in addition to the first transmission device for arranging the first and second pressurizing devices on the same plane side of the main body, the main driving unit and the driven operating unit are synchronized with each other. A second transmission device, and a main body in which the first and second pressure devices are arranged side by side on the same plane, wherein the first and second pressure devices are driven and driven by the first transmission device, respectively. By arranging on the same plane side of the main body on the same axis as each rotation axis of the car, and further supplying a shift command to the first and second pressurizing devices in synchronization with each other by the second transmission device, the output This is a synchronous control of the rotation speed and the output shaft torque.

[0015] A fourth means for solving the problem is that when the shift control device collectively arranged at a predetermined position of the main body is connected to the shift transmission device, either one of the first or second pressurizing device is operated. An internal through-hole is formed to form a ring column, and the rotating shaft of the driving or driven transmission wheel is coaxially penetrated through the through-hole, and the other is formed as a single structure in a lump shape through the force transmitting device. By being connected to a driven or driven transmission vehicle and being disposed on the main body, the transmission is integrally connected to the transmission.

The fifth object of the present invention is to solve the problem by consolidating a shift control device and supporting one of a main drive and a driven transmission vehicle between a lid and a main body base and the other between a main body and a lid base. The continuously variable transmission has a transmission control base, the transmission control device is centrally disposed on the outward side of the main body, and the transmission transmission device is centrally disposed on the inward side of the main body, and a cover is attached to and detached from the main body in which the transmission is stored. The lid is detachable while the transmission control device and the transmission are integrated.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention has been reconsidered from the basic principle of a constant horsepower transmission type continuously variable transmission system, so that it can be applied not only to dry transmissions but also to wet transmissions. It can be applied from such small horsepower to large horsepower of vehicles. In particular, when performing variable pressurization control on the first (driven) transmission vehicle, the present invention does not rely on the direct pressurization method using hydraulic pressure, but relies on the indirect pressurization method using an elastic body. It suffices that not only the variable pressure force is always applied to the body but also the elastic force is always applied.

Accordingly, the compression device of the combination of the elastic device and the compression device may be a hoisting sliding device or a hydraulic sliding device. Even if the sliding disk of the transmission wheel directly constitutes a part of the hydraulic cylinder, the indirect pressurizing method is used as long as the sliding disk has elastic force. Should just be interposed. When the compression device is a hoisting mechanism, the pressing force of the hoisting device is always only a reaction force from the elastic device, and the pressing force is supplied only during the shifting operation, so that the elastic device itself becomes a favorable variable pressurizing mechanism. Further, when the pressurizing device is hydraulically operated, the elastic device functions as a mere elastic member, and the hydraulic mechanism becomes a variable pressurizing mechanism. The elasticity of the former hoisting mechanism is better than that of the former, because the elastic force can be changed to a variable appropriate value according to the gear ratio.

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,
In order to obtain a large pressing force, it is necessary to increase the spring constant. Since the spring is likely to shrink and the size and shape are greatly increased, the spring may be divided into a plurality of elastic bodies.
The direction of arrangement of each elastic body does not need to be limited to concentric circles. If small and large pressing force can be secured, it is limited to a case where a plurality of springs are arranged in parallel and driven simultaneously to obtain continuous linear characteristics. Instead, the pressure device may be driven in a stepwise manner in response to a shift command, and may have a discontinuous stepwise characteristic or a non-linear continuous curve characteristic.

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 compressing device between the two can be arbitrarily changed according to the design. In order to make them non-rotating in operation, a rotation separating bearing may be arranged between any of the transmission wheel, the compression device, the elastic device, and the main body. It is not necessary to always place the elastic device and the compression device in the exact coaxial position with the transmission wheel rotating shaft. What is necessary is just to connect mutually. Therefore, here, the main body or the main body reference plane is
Regardless of the presence or absence of rotation, this is a place where the relative reference and position in the axial direction with respect to the transmission wheel do not change. When the pressing direction of the elastic body and the pressing direction of the transmission wheel are opposite to each other, the pressing direction may be reversed by a lever function such as a seesaw in the pressure transmitting means.

The responder and driven member of the elastic device, the driven member and the driven member and the driven member of the compression device have the same functions, and are merely in a back-to-front relationship. The portions are tentatively described as a driven body, a driven body, a driven tool, and a driven tool, but any of them may be referred to as a sliding body or a sliding tool. In addition to the above, further including levers, response devices, pressure transmitting means, etc., these members may be shared or shared by a single member depending on the design, or may be subdivided, further discs of transmission vehicles,
Various selections such as reversing or substituting with members such as the main body are performed, but these changes are within the scope of mere selection of members, and any changes are also included in the scope of the present invention.

In the case of using a hoisting sliding device as a compression device, a screwing means is most commonly used as a hoisting mechanism, but a rotary cam having a cam provided on a circumferential surface achieves the same function. In addition, since the hoisting mechanism needs to correspond one-to-one with the shift command, a well-known self-locking function in the hoisting mechanism, that is, a reverse rotation preventing brake function and an overrun prevention function based on the inertia of the rotor or the pulley pressure are required. . Therefore, a combination of various well-known techniques such as a combination of a trapezoidal screw and a worm transmitter, or a combination of a normal screw or a ball screw and a motor with a brake, and the use of a reverse rotation preventing step motor should be considered. Conversely, a worm transmission device or the like that can be used for both the driving vehicle and the driven vehicle pressurizing devices may be shared.

The main and driven actuators may be provided with reversible motors individually as drive sources.
Desirably, control should be performed by a single common drive source in order to ensure high-speed response and to reduce cost. There are various types of reversible motors, such as electric motors and hydraulic motors such as hydraulic motors, and any type of motor may be used. It is desirable to provide a reverse rotation prevention function and an overrun prevention function such as a braking function and a stepping operation function as described above. The gearshift command includes a gearshift signal corresponding to the gear ratio and gearshift power for driving each pressurizing device. However, if each operating device has a power source individually as a drive source, It is natural that a common transmission signal should be supplied to the individual power sources for maintaining synchronization on the driven side.

The amount of pressing movement of the compression device is the sum L0 of the shifting movement L01 of the first transmission wheel and the pressing movement L02 of the elastic device.
(= L01 + L02) is required. Therefore, the moving amount L
01 and the movement L02 may be constituted by separate hoisting mechanisms. In this case, the movement L0 on the driven vehicle side is necessarily different in the operation direction and the operation amount from the movement L1 on the main vehicle side, so that the pitch, the rotation direction, the number of rotations, or the screw groove of the screw means of the hoisting mechanism are changed. Well-known factors such as the machining direction (right-hand thread, left-hand thread) and the speed ratio of the transmitter may be selected according to the design. Therefore, in the first embodiment, the hoisting screw means of each of the main driving and the following operating devices is configured to have a reverse screw. However, depending on the supply method from the driving source, it is needless to say that the screw grooves may be in the same direction.

The force transmitting means is means for transmitting pressure or power, and while the installation position of the first or second pressurizing device is arranged at a distance from the periphery of the transmitting vehicle, the first and second pressurizing devices mutually transmit pressure or elasticity. Any structure may be used as long as the force transmission can be performed. The structure is not limited to the case where two transmission levers are used, but may be a rigid link mechanism or a lever link mechanism having a reversing action centering on a fulcrum by a pivot function. Therefore, it is desirable that each pressurizing device is disposed at a coaxial position corresponding to each transmission wheel in principle, but it is not always limited to this. Note that the main body and the lid described in the embodiment of the present invention may be referred to as first and second main bodies, and the lid also has the meaning of the second main body with respect to the main body. It is not limited only to the form of support.

[0026]

(First Embodiment) FIGS. 1 to 4 show an overall structure of a continuously variable transmission for a vehicle in which a transmission control device according to a first embodiment of the present invention is applied to two transmission vehicles and a pressurizing device. It shows the characteristic of. The transmission 10 basically includes a second (driven) transmission vehicle or driven vehicle 2 and a first (driven) transmission vehicle or driven vehicle 1.
And a transmission I formed of a transmission 11 wound between the transmission vehicles, a driven operation device 6 on the driven vehicle 1 side, and a driving operation device 8 on the driven vehicle 2 side. Transmission control device I formed by a common drive source 9 for synchronously driving 6, 8
I. In the transmission of the present example, the lid 10b, which is a part of the first main body 10a that accommodates the vehicle transmission device, is entirely arranged as a second main body. Further, the driving operation device 8
The pressing device 8 'is actuated by urging the sliding device 15 with the urging device 12 from the drive source 9, and the driven operation device 6 is a pressing device composed of the elastic device 3 and the compression device 4 for compressing the elastic device 3. 5 is activated by the drive source 9. The compression device 4 is a sliding device 25
And an urging device 29 that drives and adjusts the elastic device 3. The transmission control device I of the present invention clearly separates the control unit and the transmission unit by using a transmission device 40 having a main transmission and a driven transmission vehicle 1 and 2 and a force transmission device 40 that performs pressure control in conjunction with each other. Things.

Each of the transmission wheels 1 and 2 has a sliding disk 1a,
2a and fixed disks 1b and 2b are opposed to each other, and the former is slidable in the axial direction with respect to the latter via a key,
The transmission wheels 1 and 2 are arranged opposite to each other. Both transmission vehicles 1,
The contact radius r of the transmission vehicles 1 and 2 with the transmission body 11 is continuously changed by controlling the balance of the pressing force from each of the operation devices 6 and 8 corresponding to 2, and the predetermined horsepower in the entire speed change region. Power transmission. In FIG. 1, the transmission body 11 is illustrated at the position of the maximum speed ratio, and in FIG. 2, the right half is illustrated as the maximum diameter and the left half is illustrated as the position of 60% of the rotation speed of the radius r0 for convenience of explanation of the operation. Further, the transmission 10 forms a sealed oil tank chamber by the first main body 10a and the second main body or the lid body 10b, and constitutes a wet transmission in which the transmission II is accommodated therein. It is connected to a load device and the like.

Further, since the transmission wheels 1 and 2 receive a large pressure from the operating devices 6 and 8, the first and second main bodies 10a and 10a
10b includes a body base 10f and a lid base 10 respectively.
g is arranged in two parts. A transmission 11 with a transmission 11 wound around transmission wheels 1 and 2 that are supported by respective shafts between the bases 10f and 10g and the main body 10a is disposed. Power outlet / inlet space 10h, 10 in first body 10a
i has a first pressurizing device 5 to be connected to the driven vehicle 1 as one of the transmission vehicles in order to secure a space area for disposing an input / output device (not shown) interlocked with the transmission II. 1 and a fixed disk 1 coaxial with the vehicle 1
b or the back side of the lid base 10g, the pressing force of the pressurizing device 5 interlocked with the sliding disk 1a via the force transmitting means 40 shown in FIG. A pressure of 10 g is applied from the back to the front.

The pressurizing device 8 ′ of the prime mover 8 includes a sliding device 15 and a biasing device 12. The former is a hoisting device composed of a ball screw, which comprises a responding device 16 provided with a pressing device 15 a and a driven device 17, and the latter is a biasing device 12 of a worm transmitter including a worm 18 and a wheel 19. The pressurizing device 8 ′ is shown as an example of a sliding device 15 configured by a rigid member excluding an unstable positioning factor such as elastic force in order to accurately reproduce a reference position at the time of variable diameter control. . The sliding device 15 includes a cylindrical wheel 19 and a cylindrical pressing device 15a.
a and 19a are provided, the sliding shaft portion of the driving power transmission wheel 2 is penetratingly arranged, and arranged collectively so as to be juxtaposed at the same position as the pressurizing device 5 of the driven operating device 5. The wheel 19 is connected to the cylindrical portion 19b, the response member 16 and the key 19c which are integrally formed.

The main drive shaft 20 is supported on both shafts by bearings 21 and 22, while the pressing device 8 'is connected to the main body reference surface 10c and the transmission
Between the bearings 13 and 23. When the responder 16 is rotated by the wheel 19, the driven member 17 is slid only in the axial direction by the rotation preventing guide rod 24a.
The screw of the hoisting device 14 is processed into a right-hand screw. Reference numeral 24 denotes a response device, which is shown as a thrust receiver acting as a pressure transmitting means in this example. The transmission wheel 2 is expanded and contracted by directly pressing the sliding disk 2a by a pressing device 8 'disposed between the main body reference surface 10c on which the radial and thrust bearings 13a and 13b are disposed and the taper roller 23. . Therefore, the pressurizing device 8 'controls the displacement of the contact diameter r1 of the transmission body 11 only by the pressing force directly from the main body 10c to the sliding disk 2a without any elastic force.

The pressurizing device 5 of the driven operating device 6 includes the sliding disk 1
Although a is slid under pressure, it is not installed around it, but is installed in a non-rotating state on the lid 10b on the same plane as the driving unit 8. In FIGS. 1 and 2, the pressurizing device 5 includes two transmission shafts 41 on the left and right around a rod-shaped screw body 26.
a, 41b, linear ball bearings 42, 43 and shifter 44
And transmission through the lid base 10b.
Pressure transmitting means 40 for transmitting a pressing force through a gimbal 47, a thrust receiver 46, and a bearing 45 disposed in
8 is connected. The internal configuration of the pressurizing device 5 is composed of an elastic device 3 and a compressing device 4, both of which are shown as an example in which bearings 31 are used as joining points and their pressing forces are joined in series with each other.
Accordingly, the pressing force of the elastic device 3 is applied as a compressive pressing force from the bearing 31 to the transmission wheel 1 via the compression device 4 and the transmission means 40 based on the bottom cover 36 as the main body reference surface 10c. The pressurizing device 5 is configured to be detachable coaxially with the transmission wheel 1 on the lid 10b as a single-unit structure 5 in a lump that can be separated along the line III-III in FIG.

The elastic device 3 is an example in which a single structure 30 in which a plurality of annular elastic bodies 33 are concentrically housed in a housing 35 in a predetermined pressurized state is formed. A special structure is adopted to secure a large pressing force in a narrow space which cannot be formed by a single elastic body alone. The four elastic members 33a to 33d are individually provided at one end with the main body 10 and at the other end with annular responsive members 37a to 37d provided with connecting portions 39a to 39d for engaging with adjacent responsive members, respectively. . On the inner wall of the case 35, three step contact portions 38b to 38d and a bottom cover 36 are provided as a locking device 32 of the elastic body 33. In this example, the contact portion 3 corresponding to the first-stage elastic body 37a is provided.
Although there is no 8a, this is because it is connected to the compression device 4 in order to select the minimum pressure Pmin from the beginning in the initial pressurized state. It may be applied in advance as shown by a dotted line 38a. Since the innermost diameter of each step contact portion 38 is larger than the corresponding innermost diameter of each responding body 37, the adjacent step contact portion 38 of the preceding stage is adjacent.
Projecting from. Accordingly, with the response of the compression device 4, the response member 26 is guided by the respective response members in the order of the response members 37a to 37d, and is sequentially elastic members 33a, 33b, 33c and 3c.
This is a structure in which 3d is pressed, and the pressing force is added side by side in a stepwise manner.

The compression device 4 includes a reaction device 26 and a driven device 2.
7 and a sliding device 2 composed of a hoisting device as a pressing device 25a composed of a ball screw provided on the contact surface between the two.
5 and worm 4 as a self-locking mechanism for preventing reversal
And an urging device 29 formed of a speed change power transmission device including a wheel 8 and a wheel 49, and the elastic device 3 is disposed between the two. The response device 26 includes a screw portion 26a and a connecting portion 26b.
, A sliding portion 26c, and a pressing portion 26d. The sliding portion 26c forms a spline shaft and the wheels 49
Only the rotational power is transmitted to the screw portion 26a so as to be slidably engaged in the axial direction. With this configuration, the compression device 4
Are supported integrally with the elastic device 3 fixed to the main body 10 while being floating with respect to the elastic device 3. In this example, the ball screw of the response device 16 of the sliding device 15 of the main operating device 8 is a right-hand thread, whereas the ball screw of the response device 26 of the driven operation device 3 is subjected to a left-hand screw press. You. As shown in FIG.
7 is provided with a connecting lever 28 having two levers 28 a and 28 b as a response device, and is connected to the transmission means 41. The response device 26 of the sliding device 25 is a tip 32 of a response body 37a.
And the transmission means 41 connected to the transmission wheel 1 are supported in a floating state at two intermediate positions, and slide so as to absorb the elastic force of the transmission wheel 1 and the elastic device 3, so that the sliding portion 26c has a predetermined length. With

As the common drive source 9, a DC servomotor is used as a reversible motor 53 with a brake shown in FIGS. 3A and 3B, two transmission devices 55 and 60 are provided, and the main drive and the driven actuators 8 and 3 are respectively provided. Are simultaneously driven synchronously. The shifting power as the shifting command is gear 5
6 and 57 to the shaft 58 from the shaft 54, further to the operating device 8 from the shaft 58 to the shaft 18 a by gears 59 and 60, and to the operating device 3 via the gears 59 and 62 including the idler wheel 61 to the shaft 5.
8 to the shaft 48a. The gear 60, the gear 63,
The difference in the number of teeth 62 is that the moving displacement L1 of the pressing device 5 of the driven vehicle 1 is different from the moving displacement L1 of the sliding device 15 of the driven vehicle 2.
0 (= L01 + L02) is larger and the sliding disk 1a
This is because it is necessary to move and press both the elastic body 33 and the elastic body 33 at the same time. If the idler wheel 61 is unnecessary according to the arrangement of the motor 53, the rotational force to the transmitter 29 is in the same direction, so that the responders 16 and 26 may be screw grooves in the same direction.

Next, the operation of the transmission 10 will be described focusing on the pressurizing devices 5, 8 'together with FIG. As shown in FIG.
0 and the transmission body 11 is in the position of the maximum speed ratio and the input / output shaft 2
It is assumed that 0,50 is transmitted and is rotating at a constant speed at a constant speed ratio. It is assumed that the reversible motor 53 starts driving in the direction of decreasing the speed ratio, that is, receiving a speed increase command. As shown by the arrow in FIG. 3A, the shifting power is transmitted to the shaft 18a and the shaft 48a and rotates in opposite directions. In this example, since the screw body 15a and the screw body 25a are reversely threaded with each other, the sliding device 15 is
When a is pressed, the radius of the transmission body 11 starts to increase from r10 to r11. At the same time, the pressurizing device 5 that has been pressing with the maximum pressing force Pmax operates in a direction to decrease the pressing force of the sliding device 25 of the compression device 4. Accordingly, the responsive member 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 time, the responsive member 26 of the sliding device 25 rises by the amount released and the driven member 27 descends. I do. This lowering amount is reduced by reducing the pressure applied to the transmission vehicle 1 via the lever 28 and the pressure transmission means 40 in FIG. To r01.

This is shown in the characteristic diagram of FIG.
This shows that the characteristic point (a) shifts from the characteristic point a1 to the characteristic point a2 on the staircase line (IV) with the transition of the output rotational speed a1 from the output rotational speed n1 to n2. At the same time, it means that the pressure P1 applied to the transmission vehicle 1 is also reduced to P2 in accordance with the supply of the speed increase command. Thus, it is shown that the pressure and the rotation speed in the transmission vehicle 1 are in inverse proportion to each other. Similarly, when a speed increase command is further provided from the reversible motor 53, the same operation is repeated. Assuming that the output rotation speed is n60, which is approximately half, the elastic bodies 33c and 33d abut on the locking device 32 and do not contribute to pressurizing the transmission wheel 1, as depicted in the left half of FIG. Stair characteristics (I
At the position of the characteristic point a60 of I), the elastic bodies 33a and 33
Only b shows that it has the function of compression and pressurization. Similarly, as the response member 26 of the sliding device 25 rotates, the pressurizing characteristic decreases stepwise as the number of rotations increases, and reaches the minimum pressing force Pmin at the highest rotation speed. Conversely, to return to the deceleration state again, the reversible motor 54 is rotated in the reverse direction to return to the original position according to the reverse operation described above.

In the conventional elastic body, the rotation speed N of the driven vehicle 1
As the characteristic line (D) in FIG. 4 increases, the pressing force also increases.
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 related art in which the compression pressure increases as the compression amount increases, so that the compression The most characteristic feature is that the characteristics are inversely proportional or inversely proportional to each other and a negative inclination characteristic is secured. In the substantially horizontal characteristic line (C0 to C2), the pressing force per unit area is almost the same in the entire shift range, but when the contact area between the belt and the pulley of the driven vehicle 1 is at the lowest speed, compared with the highest speed. Reaches several times. Therefore, even with this characteristic, the shaft torque T received by the transmission body 11 is
Can be increased even if the rotational speed N decreases. Even if the characteristic line (C2) in FIG. 4 is slightly inclined, the constant horsepower can be substantially transmitted by the increase in the contact area. The “substantial inverse proportion” of “Claim 1” is a concept including a slight positive slope characteristic C2 and further includes a stepwise or non-linear curve characteristic.

Next, the automatic alignment function of the transmission of the present invention will be described. Power transmission of the transmission includes internal error factors and external intrusion factors, both of which hinder normal transmission. As a typical example, the former includes elongation in the longitudinal direction and abrasion in the width direction of the transmission body 11, and the latter includes supply of a shift command, penetration of an impact load from an input / output device, and the like.
According to the invention, in each case the elastic device 3 has the function of automatically compensating for each of the detrimental factors during operation and automatically returning to normal transmission again. That is, the elastic device 3
Has a self-aligning function that guarantees only stable transmission of irregular factors that occur inside and outside, as well as a tension adjusting function that absorbs irregular disturbances in the transmission body tension that occurs during the gear shifting process.

Now, it is assumed that the circumferential length of the transmission body 11 gradually increases during the operation at the maximum speed ratio ε1. At this time, the main and driven actuators 6, 8 are not biased, so that the contact radius of the driving vehicle 2 remains unchanged. However, in the driven vehicle 1, the radius increases in accordance with the extension. The output rotation speed is reduced by that much, and the disc 1a and the elastic device 3 move slightly, but the pulley clamping pressure P changes only slightly, and the clamping pressure on the transmission body 11 maintains the state of the maximum load. Keep doing. This indicates that the transmission function of the predetermined horsepower is not affected at all while the rotation speed is slightly changed, and the normal transmission is maintained by performing automatic alignment. Next, consider a case where the thickness of the transmission body 11 due to wear in the width direction is reduced. At this time, the operating devices 3 and 8 are stopped, but the contact radius of the driven vehicle 2 is automatically reduced by the pressing of the elastic device 3 by the driven vehicle 1, and the radius of the driven vehicle 1 is similarly increased by that amount. As a result, the output rotational speed slightly decreases, but self-alignment is performed while maintaining the normal transmission horsepower.

Further, it is considered that sudden impact vibration enters the input / output shafts 20 and 50. In this case, the self-centering function works similarly. On the driven transmission vehicle 1 side, turbulent vibration for expanding or reducing the radius r0 of the transmitting body 11 occurs only for a moment, but this vibration is conversely transmitted from the pressure transmitting means 40 to the compression device 4. At this time, the compression device 4
However, since the spline sliding shaft 26c at the tip of the response device 26 is also slidably engaged with the wheel 49 of the urging device 29 in the axial direction, the compression device 4 is Except for the engagement with the connector 32 at 37, the whole is arranged in a floating state. Therefore, only the elastic device 3 elastically absorbs the turbulent vibration that has entered. The turbulence is terminated within a short time, and the pressurizing device 5 automatically returns to the original stable transmission state again.

Next, the pressurizing device 5 of the driven vehicle 1 supplies both the variable pressurizing force and the elastic body as indirect pressurization to the transmission vehicle while the pressurizing device 8 'of the driven vehicle 2 transmits the transmitted pressure. The reason why only the variable pressure is supplied directly to the car as pressurization will be described. The reason is that the driven vehicle 1 and the driven vehicle 2 separate the respective functional roles of the rotation speed and the shaft torque of the continuously variable transmission. In other words, while the driven vehicle 1 has a transmission shaft torque of a predetermined horsepower for the load device to be connected, and has an automatic alignment function of returning to a stable state by itself due to turbulence from inside and outside, This is because the main drive vehicle 2 provides a reference for the rotational speed control by guaranteeing the stable positioning of the disk 2a at all times to back up each role of the driven vehicle 1. This is because the main drive vehicle 2 operates as a reference vehicle for the rotational speed of the transmission and the driven vehicle 1 performs the function of a following vehicle that operates based on the rotational speed of the reference vehicle 2.

The pressurizing device 5 of the driven vehicle 1 has the elastic device 3 integrally assembled in a lump between the urging device 29 and the sliding device 25 of the compression device 4 to form a single structure as a whole. Outside the lid base which is a part of the main body 10, it is arranged coaxially with the shaft 50 of the transmission wheel 1 and detachably from the outer line III-III. On the other hand, the pressurizing device 8 ′ of the driving vehicle 2 includes a cylindrical sliding device 15 including a sliding device 15 and an urging device 12 and a lid 1.
0b and integrally with the lid 10b.
Accordingly, by releasing a number of bolts 10e from the main body 10a to the lid base 10b shown in FIG. 3A, the operating devices 6 and 8 constituting the shift control device 7 can be driven and driven by the driven and driven transmission vehicles at the line IV-IV. Bearing 2 with 1, 2
, 45 and bearing 52 to cover 10 as body 10
b is detachable as an integral transmission.

(Second Embodiment) FIGS. 5 and 6 show a sectional configuration of a second embodiment of the present invention used in a continuously variable transmission for machine tools such as a milling machine and a drilling machine. Pressurizing device 5 of the present invention
Is applied to the left driven transmission vehicle 1. Since all the embodiments after this embodiment have substantially the same basic operations and functions, the same reference numerals as those in the above-described first embodiment will be used, and only the main differences will be described. The first difference is that a driven device 27 in which the sliding device 25 of the compression device 4 is connected to the transmission wheel 1,
Each of the response tools 26 connected to the elastic device 3 is formed by a feed nut of a female screw body, and is interlocked with a single male screw body 26 'having two male screw grooves 26b and 27b which are reversely threaded with each other. And the relative position between the responder 26 and the driven member 27 is controlled by the rotation of the single male screw body 26 '.
Second, the male screw body 26 'itself functions as the pressure transmitting means 40 for the sliding disk 1a via the coaxial through hole 65 formed in the rotating shaft 50 of the transmission wheel 1.

Thirdly, the sliding device 25 includes a first sliding device 25a for driving the transmission wheel 1 for the shift sliding amount L01 and a second sliding device 25b for driving the elastic device 3 for the compression movement L02.
And the two are male screw body 26 ′ and urging device 29.
Are arranged on the front side and the back side of the transmission vehicle 1 while sharing the same. As shown individually on the right and left sides of the figure, the disc 1a of the transmission wheel 1 is also pressed at the same time as the elastic device 3 is pressed, so that the pressure characteristic on the transmission wheel 1 is the same as the characteristic line (A) in FIG. become. Although the rotating shaft 50 has a cantilever structure using a bearing, the idea of the present embodiment can be applied to a dual-bearing supporting structure as in the first embodiment.

Fourth, as shown in FIG. 6, the elastic device 3 accommodates all of the plurality of elastic bodies 33, and only the elastic body 33a for determining the initial pressure is substantially equal to the compression pressure to be applied at the time of the maximum rotation of the driven vehicle. Is housed in the single housing 35 so as to be in a pressurized state. As shown in the figure, the elastic device 3 is detachably configured as a single structure storing energy. The housing 35 for determining the reference position of the slide 27
, The rotation stopper 24a 'is guided to the guide groove 34. The responsive body 37 of the elastic device 3 is urged by the responsive body 26 of the sliding device 25b. This example is different from the previous example in that a step-like locking device 3 is provided.
2 is that the initial contact portion 38a is provided. However, when the responsive body 26 is adjusted to the minimum pressure Pmin at the time of the initial adjustment, the elastic body 37a is separated from the elastic body 37a and is initially pressurized. Fifth, the urging device 29 of the worm transmitter is constituted independently. Sixth, each nut 26, 27 is provided with a rotation stopper 24a, 24a '.

(Third Embodiment) In the third embodiment of FIG. 7A,
Further, this is an example in which the elastic device 3 and the compression device 4 shown in the second embodiment of FIG. 5 are all disposed on a lid 10b which is a part of the main body 10 on the side of the sliding disk 1a of the transmission wheel 1. 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 the above are that the first is a single elastic body, the second is that the responsive means 28 of the compression device 4 also serves as the pressure transmitting means 40, and the third is that the lid 10b is Body 1
When removed from 0, the bearing 45 and the response device 28 can be separated,
The elastic device 3 and the pressurizing device 5 with the compressing device 4 can be attached to and detached from the main body 10 as an integrated structure, and provided for belt replacement maintenance.

(Fourth Embodiment) The embodiment of FIG. 7B is an example in which the elastic device 3 of the second embodiment of FIG. In this case, the difference from the embodiments of FIGS. 1 and 5 other than the above is that first the casing 35 is directly attached to the transmission wheel 1 and the disc 1a itself is a part of the casing 35 and the sliding body 36 To form A single spring or a plurality of springs may be driven simultaneously rather than a plurality of springs, and in this embodiment, a configuration of a plate spring series-parallel configuration may be employed. Secondly, the sliding body of the elastic device 3 is divided into five sliding bodies 37 in which a plurality of sliding bodies are interlocked with each other. This is also because a bearing is provided between the sliding member 28 and the sliding member 37. The bearing 45 is composed of the disk 1a and the elastic body 33
And may be applied between them. The operation of the pressurizing device 5 is the same as that of the embodiment of FIG. 1, and the urging device 29 of the compressing device 4 is the same as that of each of the examples of FIGS. Thirdly, unlike the other embodiments, the transmission wheel 1 and the elastic device 3 are directly connected without the need to slide between the shaft 26 and the urging device 29 because they are directly connected.

(Fifth Embodiment) The fifth embodiment shown in FIG. 8A is similar to the embodiment shown in FIG.
This is an example. This example is different from the other embodiments mainly in that a plurality of elastic members 33 arranged concentrically in parallel are first used.
Are always simultaneously compressed by the compression device 4. Unlike the embodiments of FIGS. 1, 5 and 7B, the pressure characteristic does not have a step-like shape, and a linear characteristic is obtained as shown by a characteristic line (A ') in FIG. Elastic body 33a,
The elastic body 33b and the elastic body 33c are made of a right-handed spring and a left-handed spring, and cancel the compressive strain. Second, the housing 35 of the elastic device 3 is provided with the dual-purpose locking device 32 by the input-side sliding member 37 and the output-side responder 36 so that the whole is in a floating state. Third, the urging device 29 is not a worm transmission but a bevel transmission.

(Sixth Embodiment) The embodiment of FIG.
This is an example in which the elastic body 33 is directly pressurized similarly to the examples of FIGS. The difference from the other embodiments is that the sliding device 26 of the sliding device 25 of the compression device 4 moves on the main body 10a in the horizontal direction, and the sliding device 27 which also serves as the pressure transmitting means 40 presses in the vertical direction. . The point is that the cam inclined connecting surfaces 26c and 27c are provided so that the sliding member 26 and the sliding member 27 can slide in the direction perpendicular to each other, and the elastic device 3 is compressed and pressed. In this example, the urging device 29 may be constituted by a hoisting device using a screw body.

(Seventh Embodiment) FIG. 9 shows a state in which the driving vehicle 2 and the second pressurizing device 8 'of the driving device 8 of the seventh embodiment of the present invention are mounted on the lid 10b on the back side of the fixed disk 2a. An example is shown below. The structure of the force transmitting device 40 is exactly the same as that of the first embodiment shown in FIG. The difference is that the main driving vehicle 2 side does not include an elastic body as a reference wheel for controlling the output rotational speed so that an elastic force or an unstable pressurizing factor is positively eliminated, and the sliding device 1 is not provided.
5 and the urging device 12 are locked so that the key 1
6d. Therefore, the slide 16
Does not move up and down with respect to the gear 19. Note that the driven vehicle 1 is shown in FIG.
A, 8B and the other embodiments may be adopted, and the operations of the transmission control device I and the transmission II are substantially the same, and therefore description thereof will be omitted.

(Other Embodiments) Since an elastic body is not interposed in the prime mover 8, a point contact transmission phenomenon between the belt and the sheave at the beginning of the supply of the shift command (Japanese patent application: Japanese Patent Application No.
257448). Since power is transmitted in a point contact pressurized state on the order of several tons for an instant, the frequency of damage to both friction surfaces of the instantaneous belt and the sheave is extremely high. The transmission 11 of the speed change transmission II to which the present invention is applied for stable transmission is also elastically contracted in the width direction in accordance with the magnitude of the clamping pressure received from the two disks, thereby avoiding instantaneous point contact. In order to receive pressure in a wide range of surface contact in the longitudinal direction, it is necessary to apply a metal elastic body to the transmission body 11. It is necessary to determine the elastic constant of the elastic body of the transmission body according to the pressing force of the elastic device 3.

Various embodiments other than the above are conceivable.
For example, the casing 35 of the elastic device 3 may be made of the same material as the lid 10b, and the first and second pressurizing devices 5, 8 'may be collectively installed on a single lid. Conversely, the wheel 19 in FIG.
By changing the design of the inner diameter of the through hole 19a to be larger than the outer diameter of the outer ring of the bearing 22, only the second pressurizing device 9 may be separated from the main driving vehicle 1 and made detachable independently. At this time, the cylindrical portion 19b and the slide 16 may be integrally formed, and the key 19c may be omitted. Further, the common nine drive sources of the transmission control unit are not limited to electric motors, and various types of motors such as hydraulic motors such as hydraulic pressures may be employed. Further, the sliding devices 15 and 25 are each provided with a non-rotating hydraulic cylinder. You may comprise. Finally, in this specification, the procedure for transmitting the pressurizing force between the transmission wheel and the pressurizing device is mainly described. Can be selected and arranged with common sense. Therefore, within the scope of the present invention, various changes or modifications in accordance with design specifications are included in the scope of the claims within a range that can be easily created by those skilled in the art from the claims.

[0053]

In the constant horsepower transmission type continuously variable transmission, the above-described transmission relational expression (1) between the rotation speed and the shaft torque is always used on the side of the driven (output) transmission vehicle that supplies power to the load equipment. It is indispensable to make it stable. At this time, the present invention performs variable control of each quantity of the rotation speed control function and the shaft torque control function,
In such a manner that the former is performed by a main (input) transmission vehicle and the latter is performed by a driven transmission vehicle, the respective roles are divided into a main operating device and a driven operating device, and synchronous control is performed by a shift command. A common problem at this time is that since the transmission and the transmission control device need to fulfill the above-mentioned functions, it is indispensable to use members of huge dimensions or to combine a large number of members which are difficult to deliver special effects. . Therefore, it is an object of the present invention to achieve stable transmission control while dividing and distributing members by sorting and integrating them, thereby reducing the size and consolidation and simplifying them in common. A common effect is that the control unit and the transmission unit can be individually improved and improved or various operations such as adjustment and replacement can be performed from the outside.

In the transmission control device, all or a part of each pressurizing device, which is separately arranged in each transmission vehicle, can be collectively arranged in a certain area of the main body by the force transmitting means. In addition, the space around the transmission can be opened to allow room, and the dimensions can be changed arbitrarily, such as increasing the wall thickness to improve the durability of both transmission vehicles. There is an advantage that the maintenance, the interlocking design with other input / output transmission members, the provision of heat dissipation measures, and the like are significantly facilitated. The shift control device is centrally arranged at one location, and various adjustment portions such as fine adjustment of the number of revolutions and pressing force can be arranged on the outer wall surface, thereby improving productivity.

The main operating unit variably controls the input side contact diameter of the transmission body only by the pressing force without actively interposing an elastic body with the main operating vehicle side as a reference wheel, and the driven operating unit follows the driven vehicle side with the following vehicle. As a result, the elastic body self-aligns the contact diameter on the output side by itself and finds out by automatically interposing the elastic body and applying both the pressing force and the elastic force. Therefore, the advantage of securing the predetermined shaft torque by the above is guaranteed. In addition, even if disturbances such as irregular shock vibrations enter the transmission from external input / output devices, the floating support structure always supplies not only the pressing force but also the elastic force between the transmission vehicle and the externally provided elastic body. In addition, the elastic body instantaneously absorbs the elasticity and returns to the original stable transmission, so that there is an excellent advantage due to the automatic centering function of always maintaining the tension of the transmission body appropriately.

Further, when stable transmission is ensured by the self-centering function of the elastic body, a high degree of synchronism can be provided to both the main and driven actuators by the second transmission means connecting the first and second pressurizing devices to each other. Since the maintained shift command can be supplied, the responsiveness of the shift control from the maximum value εmax of the gear ratio to the minimum value εmin can be significantly shortened. In particular, since the synchronism and reproducibility can be maintained by the transmission means made of a steel material regardless of the oil pressure, there is an advantage that sufficient followability can be imparted to a sudden start and a sudden stop in a vehicle or the like.

Next, after establishing a control operation that promotes stable transmission and high-speed response on the side of the transmission control device, the transmission control device itself is closely connected to the transmission device while maintaining the form of a centralized arrangement. There is an advantage that the whole machine can be made into a single module and ultra-miniaturized. Particularly, on the shift control device side, FIG.
The elastic body is selected so that the pressurizing characteristic (B) required for the actual load of the vehicle is as close as possible to the pressurizing characteristic (A) of the actually equipped elastic body, and the speed change transmission device promotes high-efficiency shift control. Along with
By guaranteeing stable transmission by the transmission body on the transmission transmission side as well, ultimate reliability and durability of the continuously variable transmission can be improved.

Finally, in order to connect the input / output side transmission devices such as the internal combustion engine and the speed change transmission of the continuously variable transmission, the speed change control device requiring external adjustment is directed outward and the speed change transmission is set inside. The lids and the lid base are integrally arranged on the lid body and the lid base. This enables mass production of assembly and disassembly by making the main body that houses transmission equipment such as vehicles detachable from the first main body and the continuously variable transmission integrally with the second main body consisting of the lid and the lid base. Therefore, there is an effect that expansion of versatility by replacing the transmission body or the elastic body and expansion of maintainability such as replacement of consumables are achieved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a continuously variable transmission for a vehicle using a transmission control device according to a first embodiment of the present invention;

FIG. 2 is a longitudinal sectional view of the continuously variable transmission shown in FIG. 1 taken along line II-II,

3 shows a part of a synchronous drive source of the operation device of the continuously variable transmission shown in FIGS. 1 and 2, FIG. 3A shows a configuration of a second transmission, and FIG. 3B shows a configuration of a first transmission. In partial cross-section,

FIG. 4 is a characteristic diagram showing a relationship between a pressing force and a rotation speed of the driven actuator used in the first embodiment.

FIG. 5 is a cross-sectional view of a continuously variable transmission for a machine tool using a device according to a second embodiment of the present invention.

FIG. 6 is an enlarged sectional view of a portion of the elastic device of the device according to the second embodiment of the present invention.

FIG. 7 is a second pressurizing device for a transmission wheel supported by a single bearing, FIG. 7A is a sectional view of a device according to a third embodiment of the present invention, and FIG. 7B is a fourth embodiment of the present invention. 1 shows a cross-sectional view of the device. Further

FIG. 8 is a second pressurizing device for a transmission vehicle supported by dual bearings, FIG. 8A is a sectional view of a fifth embodiment of the present invention, and FIG. 8B is a sixth embodiment of the present invention. 1 shows a cross-sectional view of the device.

FIG. 9 is a sectional view of a second pressurizing device of the device according to the seventh embodiment of the present invention.

[Explanation of symbols]

 Reference Signs List 1 driven vehicle, driven transmission vehicle or first transmission vehicle 2 main vehicle, driven transmission vehicle or second transmission vehicle 3 elastic device 4 compression device 5 pressurizing device or first pressurizing device 6 driven operating device 7 speed change control device 8 main driving Actuator 8 'pressurizing device or second pressurizing device 9 common drive source 10 transmission 10a main body or second main body 10b lid or first main body 10c reference plane 10f main body base or second main body base 10g lid base or One body base 11 Transmission body 12, 29 Biasing device or speed change power transmission device 14 Telescopic device 15, 25 Sliding device 15a, 25a Pressing device or hoisting device 16, 26 Responder, slide, or first slider 17 27, a driven member, a sliding member or a second sliding member 32 a locking device 33 an elastic body 35 a housing 36 a driven member, a sliding member or a second sliding member 37 a responding member, a sliding member or a first sliding member 40 Pressure transmission means

Claims (35)

[Claims] 1. An arrangement in which the discs are arranged in opposite directions to each other between a driving power transmission wheel and a driven transmission wheel each constituted by a pair of sliding and fixed discs, and a transmission body is wound around the discs. A transmission control device for a continuously variable transmission that transmits constant horsepower, wherein a main driving device that controls a second pressurizing device that supplies a pressing force with no elastic force from the main body to the driving power transmission vehicle in accordance with a shift command. And a driven operating device that controls a first pressurizing device that supplies a pressing force by which an elastic force is interposed from the main body to the driven transmission vehicle in accordance with a shift command, and further includes a driven operating device that controls the first or second pressing device, respectively. And a force transmission device for transmitting a pressing force to the driven or driven transmission vehicle, wherein the driven and driven actuators are all or a part of one of the first or second pressing devices. On the same plane as the main body on the side where the other pressing device is disposed. In addition, by transmitting the pressure via the force transmission device between the driven or driven transmission vehicle that is interlocked with the one pressurizing device, it can be operated from outside the main body on the same plane as the main body. Transmission control device for a continuously variable transmission, which is arranged adjacent to and adjacent to each other. 2. The driving device according to claim 1, wherein the driving device and the driven operation device each include a telescopic device in the second pressing device and a compression device and an elastic device in the first pressing device. A speed change control device for a continuously variable transmission, wherein the expansion and contraction and compression device provided with a shift command introduction end for biasing a pressure device is disposed on the same plane side of the main body. 3. The sliding device according to claim 2, wherein the main driving and driven operating devices are a sliding device including a pressing device that presses and slides the expansion / contraction device and the first and second sliding members. A shift control device for a continuously variable transmission, wherein the shift control device comprises an urging device for driving the device, and the urging devices are arranged on the same plane side of the main body. 4. The main body according to claim 1, wherein the first pressing device of the driven operating device has an elastic device, and the elastic device is connected to the second pressing device. A transmission control device for a continuously variable transmission, which is arranged on the same plane as the above. 5. The method according to claim 1, 2, 3, or 4,
The above-described force transmission device is for a continuously variable transmission having a transmission lever that transmits a pressing force from inside the transmission wheel to the transmission wheel through a through hole formed in one of the transmission wheel rotation shafts in the axial direction. Transmission control device. 6. The method according to claim 1, 2, 3, or 4,
The above-mentioned force transmission device is a transmission control device for a continuously variable transmission, comprising a transmission lever that straddles the outside of any one of the transmission wheel disks and transmits a pressing force to an advanced transmission vehicle from outside the shaft. 7. The power transmission device according to claim 6, wherein the force transmission device is arranged between one of the pressurizing devices disposed on the same axis as the transmission wheel rotation center and the transmission wheel and the transmission wheel around the axis. A transmission control device for a continuously variable transmission, comprising: two transmission levers arranged side by side in parallel with each other; and a bearing for slidingly guiding each of the levers. 8. An arrangement in which the respective discs are arranged in mutually opposite directions between a driving transmission wheel and a driven transmission wheel, each of which is constituted by a pair of sliding and fixed discs, and a transmission body is wound around the transmission discs. A transmission control device for a continuously variable transmission that transmits constant horsepower, comprising: a main operating device having a second pressurizing device for supplying a pressing force from a telescopic device that operates from a main body to the main power transmission vehicle in accordance with a shift command; A driven operating device having a first pressurizing device for supplying a pressing force and an elastic force from a compression device and an elastic device which act on the driven transmission vehicle from the main body to the driven transmission vehicle in accordance with a shift command; and further, the first or second pressing device And a force transmission device for transmitting a pressing force to the driven or driven transmission vehicle, respectively, wherein the driven actuator serves as a reference wheel for controlling the rotation speed of the driven transmission vehicle so that the contact diameter between the transmission body and the transmission vehicle can be varied. The position control function is provided and the driven actuator is In order to apply a variable pressure control function to the driven transmission vehicle as a follower vehicle of the shaft torque control to the power transmission vehicle, the driven and driven actuators respectively introduce a shift command to the first and second pressurizing devices. A shift control device for a continuously variable transmission, the end of which is arranged on the same plane side of the main body and urged by a drive source. 9. The driving device according to claim 8, wherein the main driving device and the driven operating device each include two sliding members each of which extends and contracts and the compression device, and a pressing device that presses and displaces a relative position between the two sliding members. A shift control device for a continuously variable transmission, which is a cam link device having a sliding device, wherein the pressing device converts horizontal sliding into vertical sliding on an inclined surface applied to each of the sliding tools. 10. The driving device according to claim 8, wherein the main and driven actuators each comprise two sliding members, and a pressing device for pressing and displacing the relative positions of the two sliding members. A shift control device for a continuously variable transmission, which is a hoisting device having a sliding device, wherein the pressing device is pressed and slid by a screw body provided on each of the sliding tools. 11. The driven operating device according to claim 8, wherein the driven operating device is configured to apply the elastic body to the housing in a pressurized state substantially equal to a pressing force applied to the elastic device during the highest speed rotation of the driven transmission vehicle. A shift control device for a continuously variable transmission, which is configured to be housed in advance under pressure. 12. The driven operating device according to claim 8 or 11, wherein the driven device comprises a plurality of annular elastic members arranged concentrically in the elastic device, and the plurality of elastic members are simultaneously linearly responsive to the compression device. Control device for a continuously variable transmission, which is controlled in a pressurized state. 13. The driven operating device according to claim 8, wherein the driven device includes a plurality of annular elastic members arranged concentrically in the elastic device, and the plurality of elastic members are sequentially arranged in response to the compression device. A shift control device for a continuously variable transmission controlled by stepwise pressurization. 14. The driven operating device according to claim 8, 11, 12 or 13, wherein the driven operating device is configured to fix the elastic device to the main body in a non-rotating state and to connect the compression device between the driven transmission wheel and the elastic device. A shift control device for a continuously variable transmission supported in a floating state. 15. An arrangement in which the respective discs are arranged in opposite directions to each other between a drive transmission wheel and a driven transmission wheel, each of which is constituted by a pair of sliding and fixed discs, and a transmission body is wound around the discs. A transmission control device for a continuously variable transmission that transmits constant horsepower, comprising a second pressurizing device that supplies a pressing force from an expansion device that operates in accordance with a shift command from a main body to the main power transmission vehicle with an inelastic force. A driven actuator having a main operating device, a first pressurizing device that supplies a pressing force and an elastic force from a compression device and an elastic device that act according to a shift command from the main body to the driven transmission vehicle, Or a first transmission device for transmitting a pressing force from the second pressurizing device to the driven or driven transmission vehicle, respectively, a second transmission device for interlocking the driven and driven operating devices with each other, and further, the first and second transmission devices All or part of the pressurizing device is placed side by side on the same plane And the first and second pressurizing devices are arranged on the same plane side of the main body on the same axis as the respective rotational axes of the driven and driven transmission wheels by the first transmission device. Further, the transmission command is synchronously supplied to the first and second pressurizing devices by the second transmission device, so that the output rotation speed and the output shaft torque are synchronously controlled with each other. . 16. The driven operating device according to claim 15, wherein the driven operating device is configured to perform variable pressurization in response to a shift command such that a pressure applied to the driven transmission vehicle is substantially inversely proportional to a change in the rotational speed. A shift control device for a continuously variable transmission that is controlled. 17. The driven operating device according to claim 16, wherein the driven operating device increases a pressure applied to the driven transmission vehicle as a speed change command in accordance with a deceleration command of an output rotation speed and decreases the pressure in accordance with a speed increase command. A shift control device for a continuously variable transmission, which controls the driven transmission vehicle and the elastic device. 18. The driving device according to claim 17, wherein the main driving device and the driven operating device each have a sliding device in the expansion / contraction and compression device, and the main driving device displaces a shift L1 of the driving power transmission vehicle. On the other hand, the driven operating device comprises a shift movement L01 of the driven transmission vehicle and a compression movement L of the elastic device.
A shift control device for a continuously variable transmission, wherein the total movement amount L0 (= L01 + L02) of No. 02 is synchronously displaced by the respective sliding devices. 19. The apparatus according to claim 18, wherein the main drive and the driven actuator each have a reversible motor for individually controlling each of the sliding devices by a single shift command, and the second transmission device includes A shift control device for a continuously variable transmission, which is a command synchronous interlocking means. 20. The power transmission device according to claim 18, wherein the second transmission device is a power transmission device of a speed change command comprising a rigid member between the first and second pressure devices. A transmission control device for a continuously variable transmission, wherein a common drive source for the main and driven actuators is connected to the position (1). 21. The main driving and driven operating device according to claim 20, wherein the main driving device and the driven operating device are mounted on the main body on the same plane where the first and second pressurizing devices are arranged while being connected to the common driving source. Transmission control device for a continuously variable transmission. 22. A transmission in which the respective discs are arranged in opposite directions between a driving power transmission wheel and a driven transmission wheel, each of which is constituted by a pair of sliding and fixed discs, and a transmission body is wound therearound. In a continuously variable transmission that transmits constant horsepower by a transmission, a main actuator that controls a second pressurizing device that supplies a pressing force with no elastic force from the main body to the main power transmission vehicle in accordance with a shift command. And a driven operating device that controls a first pressurizing device that supplies a pressing force by which an elastic force is interposed from the main body to the driven transmission vehicle in accordance with a shift command; and A force transmission device for transmitting a pressing force to a driven or driven transmission vehicle, and a transmission control device including the main body for arranging the first and second pressurizing devices on the same plane side of the main body, and The speed change control device is connected to the speed change transmission device. Sometimes, one of the first and second pressurizing devices is provided with an internal through-hole and formed into a ring-shape, and the rotating shaft of the driven or driven transmission wheel is coaxially penetrated through the through-hole, and the other is By forming in a lump shape as a single structure and being connected to the driven or driven transmission vehicle via the force transmission device and centrally arranged on the main body,
A continuously variable transmission which is integrally connected to each other while being separately separated from the transmission. 23. The sliding device according to claim 22, wherein each of the expansion and contraction and compression devices has a sliding device constituted by a pressing device comprising a screw body on each of the first and second sliding members. A continuously variable transmission in which one is formed in a cylindrical shape having a through hole and the other is formed in a non-open shaft shape. 24. The continuously variable transmission according to claim 23, wherein each of the expansion and contraction and compression devices includes a ball screw as a pressing device of each of the sliding devices. 25. The urging device according to claim 24, wherein the expansion and contraction device and the compression device each include a worm transmission device including a worm and a wheel for urging the sliding devices in response to a shift command. A continuously variable transmission. 26. The continuously variable transmission according to claim 25, wherein the elastic device is configured to drive the first sliding member of the compression device, which is disposed through the center of an annular elastic body, by the urging device. . 27. The elastic device according to claim 25, wherein the elastic device has one end of the elastic body disposed on the main body, and the expansion and contraction device has a coupling between the wheel and the first sliding member, respectively. A continuously variable transmission fixedly connected on the expansion device side and slidably connected on the compression device side. 28. The speed change transmission device according to claim 22, wherein the transmission body elastically contracts in a width direction of the transmission body in accordance with a value of a clamping pressure received by the two disks of each of the transmission wheels. Continuously variable transmission having an elastic metal body. 29. A transmission in which the respective discs are arranged in opposite directions between a driving transmission wheel and a driven transmission wheel, each of which is constituted by a pair of sliding and fixed discs, and a transmission body is wound around the transmission discs. A continuously variable transmission that transmits a constant horsepower with a transmission, a main operating device having a second pressurizing device that supplies a pressing force from an expansion and contraction device that works from a main body to the main driving transmission vehicle in accordance with a shift command; A driven operating device having a first pressurizing device for supplying a pressing force and an elastic force from a compression device and an elastic device that act on the driven transmission vehicle from the main body to the driven transmission vehicle in response to a shift command; and the first or second pressurizing device. A force transmission device for transmitting a pressing force from the device to the driven or driven transmission vehicle, a common drive source for synchronously supplying a shift command to the first or second pressure device, and further, the first and second pressure devices. Are supported side by side on the same plane and have a lid base The shift control device having a body,
And the speed change transmission device, wherein one of the driven and driven transmission wheels is shaft-supported between the lid and the main body base and the other is supported between the main body and the lid base, respectively. The shift control device is disposed on the outward side of the main body, and the shift transmission device is centrally disposed on the inward side of the main body, and the lid is attached to and detached from the main body housing the shift transmission, whereby the lid is A continuously variable transmission which is detachable with the shift control device and the shift transmission device integrated. 30. The continuously variable transmission according to claim 29, wherein the main operating device is integrally formed with the lid and the lid base, and the driven operating device is detachably disposed on the lid base. . 31. The continuously variable transmission according to claim 29, wherein the driven operating device is formed integrally with the lid and the lid base, and the main driving device is detachably disposed on the lid base. . 32. The driving device according to claim 29, wherein the main driving unit and the driven operation unit are integrally formed in the lid and the lid base, and the housing for accommodating the elastic body of the elastic device is also used as the lid. A continuously variable transmission formed. 33. The driving device according to claim 32, wherein the driving device and the driven operation device are configured such that one of the first and second pressurizing devices can be detachably attached to the main body separately from the lid. A continuously variable transmission. 34. The apparatus according to claim 29, wherein the common drive source includes first and second transmitters for supplying a shift command to the first and second pressurizing devices, respectively, and a reversible drive for synchronously driving the transmitters. A continuously variable transmission comprising a motor and a brake device for preventing overrun of the reversible motor. 35. The vehicle transmission according to claim 34, wherein the transmission is a vehicle transmission integrally concentrated on the lid, which is a part of the main body, accommodating a power transmission device interlocked with an internal combustion engine. Step transmission.