WO2015139502A1 - 一种锥盘式无级变速器 - Google Patents

一种锥盘式无级变速器 Download PDF

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Publication number
WO2015139502A1
WO2015139502A1 PCT/CN2014/095737 CN2014095737W WO2015139502A1 WO 2015139502 A1 WO2015139502 A1 WO 2015139502A1 CN 2014095737 W CN2014095737 W CN 2014095737W WO 2015139502 A1 WO2015139502 A1 WO 2015139502A1
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WIPO (PCT)
Prior art keywords
cone
shaft
cam
driven
pressing
Prior art date
Application number
PCT/CN2014/095737
Other languages
English (en)
French (fr)
Inventor
程乃士
Original Assignee
程乃士
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201420129364.5U external-priority patent/CN203770563U/zh
Priority claimed from CN201410106539.5A external-priority patent/CN103867678B/zh
Application filed by 程乃士 filed Critical 程乃士
Priority to EP14886159.4A priority Critical patent/EP3128207B1/en
Priority to JP2017500112A priority patent/JP6507225B2/ja
Priority to US15/127,278 priority patent/US10024404B2/en
Publication of WO2015139502A1 publication Critical patent/WO2015139502A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66254—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means

Definitions

  • the present invention relates to a transmission, and more particularly to a cone-and-disc type continuously variable transmission.
  • the cone-and-disc type continuously variable transmission is widely used in vehicles, construction machinery and other power machinery by a flexible transmission component held between the cones, such as a rubber belt, a steel belt, a chain, etc., which transmits power and motion in a frictional manner.
  • the pressurizing system and the speed regulating system of the cone-and-disc type continuously variable transmission are the key parts of the continuously variable transmission.
  • the friction system between the cone and the flexible transmission component is realized by the pressurizing system, and the shifting function is realized by the speed regulating system.
  • the pressurization and speed control are controlled by a hydraulic system set on the moving cone.
  • the hydraulic system presses the cone according to the preset control mode.
  • the disc applies pressure and speeds up.
  • the pressure of such a continuously variable transmission is fixed and cannot be adjusted in real time as the load on the transmission changes.
  • the designed pressurizing pressure is generally much larger than the actual required pressure.
  • the transmission efficiency of the continuously variable transmission is low; the load of each component is increased, the system life and reliability are reliable.
  • the method is that in the hydraulic system, one slope surface constituting the end cam is rigidly connected with the transmission shaft of the moving cone, the other slope surface is connected with a hydraulic piston, and two slope surfaces are provided with rollers, two slope surfaces A torque-related thrust is generated by the rollers between them, which is added to the hydraulic pressure by a hydraulic piston.
  • the pressurizing pressure can be adjusted in time with the change of the transmission torque, and reacts to the sudden load, so that the design pressure of the hydraulic system can be appropriately reduced, the energy consumption can be reduced, and the performance requirement of the hydraulic pump can be reduced.
  • the stroke of the end cam cannot satisfy the axial stroke (about 15 to 20 mm) required for the speed of the moving cone, it can only be used as an auxiliary component for use with the hydraulic system, and cannot be used as a pressurizing mechanism alone.
  • a space cam structure for directly pressing a moving cone is disclosed in the patent document DE 0000 10 139 119. This kind of structure is still placed on the side of the moving cone due to the space cam, and there is also an axial movement space that cannot provide the speed of the moving cone. The problem. The only way to solve this problem is to increase the axial dimension of the cam structure.
  • the increase in size is a great drawback; at the same time, the angle of the slope of the space cam in the radial direction is smaller than the friction self-locking angle, and the movement of the moving cone away from the pressure cone In the middle, self-locking phenomenon occurs, and it is impossible to move; in addition, in actual use, the rolling elements in the cam structure are generally not at the lowest position in the shape of the cross-section of the raceway, in the process of converting the forward torque into the reverse torque. The moving cone will follow the cam for axial movement, causing the flexible transmission element to slip and invalidate the transmission; further, the structure of the space cam does not consider the forward and reverse pressure problems, and does not have the forward and reverse pressure function.
  • German Patent No. DE 30 28 490 discloses a structure in which a fixed-cone disk is pressurized by a hydraulic system using an end cam.
  • the pressurized system of this structure is still a hydraulic system, wherein the main pressurized cylinder is located on the back of the active and driven shaft cones, and a hydraulic cylinder, an end cam and the hydraulic cylinder are disposed on the back of the driving shaft fixed cone The other end is connected to the drive shaft.
  • the main pressurizing cylinder is used. Only when the sudden load is encountered, the end cam on the back of the active shaft taper disk can quickly compress the hydraulic cylinder to increase the hydraulic pressure and prevent the flexible transmission component from slipping. Therefore, the structure still does not get rid of the above defects existing in the same moving cone on the pressure and speed regulation.
  • the CN201875074U patent document discloses a cone-plate type continuously variable transmission adopting a screw pressurization method.
  • the cone-and-disk type continuously variable transmission includes a pair of driving cones mounted on a driving shaft and a pair of driven cone disks mounted on the driven shaft; the driving cone and the driven cone disc sandwich the flexible transmission element.
  • the pressing mechanism of the cone-and-disk type continuously variable transmission is composed of a pressing screw and a pressing nut which are mounted on the back surface of the driving shaft cone, and the pressing screw and the pressing nut are screw-fitted.
  • the speed regulating mechanism comprises a hollow screw and a nut arranged on the back of the driving shaft cone.
  • the hollow screw and the nut are a ball screw structure or a sliding spiral structure, and one of the hollow screw and the nut is fixedly connected with the driving shaft cone, and the outer wall has a speed regulating gear.
  • the speed regulating motor is regulated by a speed reducer on the reducer and the hollow screw or nut.
  • the speed governing mechanism and the pressing mechanism are mounted on the same moving cone, and the pressing portion needs to simultaneously satisfy the axial moving stroke of the moving cone, thereby causing the transmission.
  • the axial dimension is large and the structure is not compact enough.
  • the pressurizing mechanism can only pressurize in one direction, and can not transmit torque in the reverse direction. It can only be applied in one-way transmission motion and torque.
  • the object of the present invention is to provide a compact structure, two-way pressurization, real-time adjustment of transmission pressure with transmission torque, high transmission efficiency, long service life and high reliability for the defects and deficiencies of the prior art described above.
  • a cone-and-disk type continuously variable transmission includes a pair of driving cones mounted on a driving shaft and a pair of driven cones mounted on a driven shaft; a pair of driving cones The pair of cones in the cone and the driven cone are respectively connected by splines, or ball keys, or other means that allow the two cones to move axially relative to each other and cannot rotate with each other; the active cone and the driven cone clamp Holding a flexible transmission element;
  • the pair of cones in the driving cone includes a driving shaft cone and a driving shaft pressure cone;
  • the pair of cones in the driven cone includes a driven shaft cone and a driven shaft pressure cone a back surface (pressing end face) of at least one of the driving shaft pressing cone and the driven shaft pressing cone is provided with an end cam pressing mechanism;
  • the end cam pressing mechanism includes axially oppositely disposed Active cam and driven cam, the active cam and the corresponding drive shaft (drive shaft or driven shaft) can be fixedly connected (including integral), or can be used by splines, or ball keys, or flat keys, or other allowable axes Connected to the sliding but not mutually rotatable, the driven cam can be fixedly connected to the corresponding drive shaft (drive shaft or driven shaft), or can be axially slid by splines, or ball keys, or flat keys, or other And can not be connected to each other; the pressure cone on the back side of the end cam pressing mechanism (the drive shaft pressure cone and / or the driven shaft pressure cone) and the
  • the cone-and-disc type continuously variable transmission is provided with a speed governing mechanism for driving a synchronous axial moving cone and a driven axial rotating cone shaft for synchronous, same speed and axial movement in the same direction.
  • the speed regulating mechanism comprises a speed regulating shaft and a hollow screw and a nut respectively disposed on the back of the driving shaft cone and the driven shaft cone; the driving shaft and the driven shaft are respectively disposed in the hollow screw; the hollow screw and the nut are Ball screw or sliding screw connection; one of the hollow screw and the nut passes through the bearing that can withstand the axial load and radial load and its corresponding moving cone (active shaft cone or driven shaft pressure cone) One is connected, the other is connected to its corresponding drive shaft (driver or driven shaft) by a bearing that can withstand axial and radial loads; one of the hollow screw or nut is axially movable with the casing, but They are not connected to each other in a mutually rotatable manner, and the other is connected by a fixed ratio transmission mechanism and a speed control shaft, and the conversion relationship i1 of the rotation of the speed control shaft to the axial movement of the driving shaft cone and the driven shaft cone shaft
  • the active cam and the driven cam of the end cam pressing mechanism are in one of two forms:
  • each raceway including a forward pressing section and a reverse pressing force connected to each other a segment, the raceway of the active cam and the driven cam correspond to each other, and a rolling body is arranged between the corresponding raceways, and the active cam and the driven cam are matched by the rolling bodies;
  • V-shaped pressing faces distributed along the circumferential direction are respectively disposed on the axial opposite end faces of the driving cam and the driven cam, and each pressing face includes a positive pressing face and a reverse connection To the pressing surface.
  • the pressure cone (the drive shaft pressure cone and/or the driven shaft pressure cone) provided with the end cam pressing mechanism on the back surface and the corresponding drive shaft (the drive shaft or the driven shaft) are mounted between A needle bearing disposed between the inner bore of the pressure cone and the drive shaft.
  • An elastic axial pressing element is disposed between the end cam pressing mechanism and the corresponding pressing cone, or between the end cam pressing mechanism and the corresponding transmission shaft.
  • the end cam pressing mechanism and the speed regulating mechanism are separated in space, and the pressing mechanism is not installed on the speed regulating cone, and the axial movement of the speed regulating cone is not required, thereby reducing the axial direction of the pressing mechanism.
  • the size makes the entire continuously variable transmission compact.
  • the forward and reverse bidirectional pressure can be realized by the end cam pressing.
  • the end cam is used to convert the input torque into the axial thrust.
  • the axial thrust can be changed according to the transmission torque, which can ensure the friction transmission and avoid unnecessary overload of the system, which is beneficial to improve the service life of the system;
  • the axial thrust is provided by the input torque, and no additional energy is needed, which can improve the efficiency of the system;
  • the axial thrust can be increased in real time for the sudden change of the load, and the flexible transmission component can be prevented from slipping on the cone and the system safety can be improved.
  • the two hollow screws and nuts in the speed governing mechanism are driven by a speed control shaft, and the speed regulating torques can cancel each other, thereby reducing the torque required for speed regulation, reducing system load and performance of the speed regulating motor. Claim.
  • Figure 1 is a schematic structural view of the embodiment
  • Figure 2 is a longitudinal cross-sectional view of an end cam pressing mechanism using a rolling element drive
  • Figure 3 is a perspective view of the end cam pressing mechanism of Figure 2;
  • Figure 4 is a split view of the end cam pressing mechanism of Figure 2;
  • Figure 5 is a development view of the raceway on the opposite axial end faces of the active cam and the driven cam in the end cam pressing mechanism of Figure 2;
  • Figure 6 is a perspective view of the end face cam pressurizing mechanism using a bevel drive
  • Figure 7 is a split view of the end face cam pressurizing mechanism of Figure 6;
  • Figure 8 is a schematic view showing a connection mode of the end face cam pressing mechanism of the rolling element transmission
  • Figure 9 is a schematic view showing a second connection mode of the end face cam pressurizing mechanism of the rolling element drive
  • Figure 10 is a schematic view showing a third connection mode of the end face cam pressurizing mechanism of the rolling body drive
  • Figure 11 is a fourth connection diagram of the end face cam pressurizing mechanism of the rolling body drive.
  • a driving cone composed of a driving shaft cone 2 and a driving shaft pressing cone 1 is mounted on the driving shaft 18, and a driven shaft parallel to the driving shaft 18 is mounted.
  • a driven cone disk composed of a driven axial rotating cone 20 and a driven shaft pressing cone 21 is mounted on the body 19, and the driving cone and the driven cone disc hold the flexible transmission element 12, and the flexible transmission component can be used.
  • the driving shaft pressing cone and the driven shaft pressing cone are respectively maintained by the needle bearing 11 and the driving shaft 18 and the driven shaft 19, and the connecting shaft can be moved within a distance of 1 mm on the transmission shaft, but cannot rotate with each other;
  • the axial rotating cone and the driven axial rotating disc are respectively fed by a spline or a ball key, or other means that allow the two cones to move axially relative to each other and cannot mutually rotate with the driving shaft and the driven shaft plus the driven shaft Pressure cone connection.
  • An end cam pressing mechanism 3 is provided on the back surface of the driving shaft pressing cone and the driven shaft pressing cone, that is, the pressing end surface.
  • the end cam pressing mechanism is composed of two axially opposite active cams 3-1 and driven cams 3-2.
  • the active cam 3-1 and the driven cam 3-2 can be driven by a rolling body or a beveled transmission.
  • the end face cam pressing mechanism of the rolling body transmission has six V-shaped raceways in the circumferential direction on the axially opposite end faces of the driving cam 3-1 and the driven cam 3-2, respectively.
  • each of the raceways includes a forward pressing section 3-3 and a reverse pressing section 3-4 which are connected to each other, and the raceways of the driving cam and the driven cam correspond to each other, and the corresponding raceways are corresponding.
  • the pressing principle of the end cam pressing mechanism is that the torque on the transmission shaft is transmitted to the end cam pressing mechanism, so that the opposite ends of the opposite active cam and the driven cam and the rolling bodies are relatively moved.
  • the position of the pressure cone is limited by the speed governing cone and the flexible transmission element, and the active cam and the driven cam convert the torque applied to the working radius of the rolling body through its end face and rolling elements into the required friction drive.
  • Axial thrust The active cam and the driven cam perform forward and reverse pressurization by the opposite movement of the rolling body in the forward pressurizing section and the reverse pressurizing section of the race according to different directions of the torque.
  • the end cam pressing mechanism can adopt at least the following four connection methods:
  • the first connection method is shown in Fig. 8.
  • the active cam 3-1 and the corresponding drive shaft are slidable spline connections, and the driven cam 3-2 and the corresponding pressure cone are slidable spline connection, disc spring 5 acts on the driven cam; this connection method makes the cam processing more convenient, but the number of parts is large and the axial dimension is relatively large.
  • the second connection mode is as shown in FIG. 9.
  • the active cam 3-1 and the corresponding drive shaft, and the driven cam 3-2 and the corresponding pressure cone are slidable spline connections, and the disc spring 5 acts on the active cam.
  • the connection is basically the same as the first one, but the disc spring acts on the active cam, the size of the disc spring can be reduced, and the centrifugal force is small when rotating.
  • the third connection mode is as shown in FIG. 10, the active cam 3-1 and the corresponding transmission shaft are fixedly coupled, the driven cam 3-2 and the corresponding pressure cone are slidable spline connection, and the disc spring 5 acts on the slave On the moving cam; this connection method directly processes the cam-pressed raceway on the drive shaft, and the structure is relatively compact and reliable, but the processing is difficult.
  • the fourth connection mode is shown in Fig. 11.
  • the active cam 3-1 and the corresponding transmission shaft are slidable spline connection, the driven cam 3-2 and the corresponding pressure cone are fixedly coupled, and the disc spring 5 acts on the active On the cam; as in the third type, the cam surface is directly machined on the pressure cone, the structure is relatively compact and reliable, but the cam processing is difficult.
  • the disc spring of the above four connection modes is used as an elastic axial pressing element for the end cam pressing mechanism to provide a pre-tightening pressure to the pressing cone; meanwhile, at the moment of switching between the forward and reverse pressing, it is pressed Two cams prevent the rolling elements from being misaligned between the cams that are not pressed.
  • the advantage of the end cam pressing mechanism using the rolling element transmission is that the friction is small and the sensitivity is high.
  • the end cam pressing mechanism using the bevel transmission has two or more circumferentially distributed directions on the axially opposite end faces of the driving cam 3-1 and the driven cam 3-2.
  • the V-shaped pressing surface, each pressing surface includes a positive pressing surface 3-3' and a reverse pressing surface 3-4' which are connected to each other.
  • the pressing principle is similar to the end cam pressing mechanism of the rolling element transmission.
  • the active cam and the driven cam perform forward and reverse pressing through the positive pressing surface and the reverse pressing surface according to different directions of the torque.
  • the advantage of the end cam pressing mechanism using the bevel transmission is that the structure is relatively simple, and the disadvantage is that the friction is large and the sensitivity is slightly low.
  • the speed control system of the cone-type continuously variable transmission is controlled by a separate active drive
  • the axial movement of the cone is changed to a speed control mode for controlling the synchronous movement of the movable shaft cone and the driven shaft cone.
  • the speed regulating motor 10 is connected to the speed regulating shaft 9 through a speed reducing mechanism, and the speed regulating shaft is arranged in parallel with the driving shaft 18 and the driven shaft 19, and is provided with two gears (not shown) respectively, and the two nuts respectively.
  • the upper speed regulating gear 8 is meshed, and the two sets of gears meshing with each other constitute a fixed ratio transmission mechanism, so that the rotation of the speed regulating shaft 9 to the axial movement of the driving shaft cone 2 is converted i1 and the driven shaft cone
  • the hollow screw and the nut can be connected by a rolling screw with an intermediate rolling body (such as a ball) (not shown), which can reduce the speed regulation torque, improve the spiral life and reduce the speed of the motor compared with the ordinary sliding screw connection.
  • an intermediate rolling body such as a ball
  • Claim. In order to reduce the volume and weight of the speed governing mechanism and the space required for the movement, the rolling elements between the hollow screw and the nut move only in the raceway between the hollow screw and the nut; in order to ensure the speed regulation distance of the speed governing mechanism and The effective working length of the rolling space between the hollow screw and the nut should be greater than the total length of all rolling bodies.
  • the hollow screw is connected to the housing of the continuously variable transmission by a stop pin (not shown) or other structure, mechanism, or part that prevents it from rotating, but does not cause axial load and axial positioning.
  • the axial force of the speed regulation is enclosed in the transmission shaft, so that the load is not transmitted to the continuously variable transmission case with low relative strength, and does not rotate together with the speed regulation mechanism, thereby achieving the speed regulation function and the speed adjustment function. Eliminate the influence of the speed regulation force on the continuously variable transmission housing and improve the reliability.
  • the rotational speed sensor 13 and the rotational speed signal generating means 14 may be respectively disposed on the housing of the continuously variable transmission at appropriate positions corresponding to the drive shaft and the driven shaft.
  • an angular displacement sensor 15 for measuring the moving position of the cone can be installed on the casing of the continuously variable transmission, and the probe (not shown) of the angular displacement sensor is opened on the nut.
  • the circumferential grooves (not shown) are connected.
  • a flange-shaped limiting mechanism a16 may be disposed on the speed regulating gear 8 of the nut 6, and a limiting mechanism matched with the limiting mechanism a16 is disposed at a corresponding position of the housing.
  • B17 when the axial movement of the speed-regulating cone is beyond the limit position of both ends, the limit nut a16 and the limit mechanism b17 are used to prevent the speed-regulating nut from continuing to rotate, thereby ensuring the safety of the speed-regulating mechanism.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

一种锥盘式无级变速器，其主动锥盘和从动锥盘分别由一对动锥盘和加压锥盘组成；其加压机构由设置在主动轴加压锥盘和从动轴加压锥盘中至少一个加压锥盘背面的端面凸轮加压机构所侯成；其调速机构由调速轴和分别设置在主动轴动锥盘及从动轴动锥盘背面的空心螺杆和螺母组成，空心螺杆和螺母为滚珠丝杠结构或滑动螺旋结构，通过调速轴和定比传动机构使调速轴的转动到主动轴动锥盘和到从动轴动锥盘的轴向移动的转换关系i1＝i2，保证主动轴动锥盘和从动轴动锥盘轴作同步、同速、同向移动。该变速器的端面凸轮加压机构和调速机构在空间分开，可减小加压机构的轴向尺寸；利用端面凸轮加压机构可实现正反向双向加压；加压压力能随传递扭矩实时调整，传递效率高，系统使用寿命长，可靠性高。

Description

一种锥盘式无级变速器 技术领域
本发明涉及变速器，特别是一种锥盘式无级变速器。
背景技术
锥盘式无级变速器由夹持于锥盘间的挠性传动组件，如橡胶带、钢带、链等以摩擦方式传递动力和运动，被广泛应用于交通工具、工程机械及其它动力机械上。锥盘式无级变速器的加压系统和调速系统是无级变速器的关键部分，通过加压系统实现锥盘和挠性传动组件之间的摩擦传动，通过调速系统实现变速功能。
自无级变速器面世以来，其技术发展一直是以追求传递效率、速比范围和可靠性、以及结构紧凑为目标。
最先工程化，也是目前最常用的锥盘式无级变速器，其加压和调速是由一套设置在动锥盘上的液压系统来控制，液压系统按预先设定的控制模式对锥盘施加压力和进行调速。这种无级变速器的加压压力是固定的，不能随着变速器所受载荷的变化而实时调整。为保证系统的功能和可靠性，设计的加压压力一般要比实际需要的压力大很多，由此带来的结果是，无级变速器的传递效率低；各部件的负载增加，系统寿命和可靠性下降；系统对突变载荷无法有效做出反应；同时，液压系统的能耗和制造成本较高。
为克服上述液压加压和和调速系统的缺陷，德国Luk公司在DE000004036683和DE102006018806专利文献及CN200780010525.1专利文献中公开了一种利用端面凸轮与液压系统相配合对无级变速器动锥盘进行实时加压的方法(该方法已大规模应用在奥迪公司的Multitronic无级变速器上)。该方法是在液压系统中，将构成端面凸轮的一个斜坡面与动锥盘的传动轴刚性相连，另一个斜坡面与一个液压活塞相连，两个斜坡面之间有滚子，两个斜坡面通过其之间的滚子产生一个与扭矩相关的推力，该推力通过液压活塞附加到液压压力上。这种加压方式，加压压力可随传递扭矩的变化而适时调整，对突变载荷做出反应，从而可适当减小液压系统的设计压力，降低能耗，减小对液压泵的性能要求。但因端面凸轮的行程无法满足动锥盘调速需要的的轴向行程(约15至20mm)，所以只能作为与液压系统配合使用的辅助部件，不能单独作为加压机构使用。
LuK公司在DE000010139119专利文献中公开了一种直接对动锥盘加压的空间凸轮结构。此种结构因空间凸轮仍设置在动锥盘一侧，同样存在无法提供动锥盘调速所需轴向移动空间 的问题。解决这一问题的唯一办法是增加凸轮结构的轴向尺寸。而在很多应用中，尤其是车辆应用中，尺寸增加是一个极大的缺陷；同时，此种空间凸轮在径向上的斜面角度小于摩擦自锁角，在动锥盘远离加压锥盘的动作中，会发生自锁现象，无法运动；另外，在实际使用中，该凸轮结构中的滚动体一般不会在滚道截面形状中的最低位置，在正向扭矩转换为反向扭矩的过程中，动锥盘会跟随凸轮作轴向移动，导致挠性传动元件打滑，使传动失效；再有，该空间凸轮的结构未考虑正反向加压问题，不具有正反向加压功能。
德国PIV公司在DE3028490中公开了一种利用端面凸轮通过液压系统对定锥盘加压的结构。此种结构的加压系统仍为液压系统，其中主加压油缸位于主动和从动轴动锥盘的背面，同时在主动轴定锥盘的背面布置有液压缸，端面凸轮与该液压缸的另一端和传动轴相接。正常工作时靠主加压油缸，只有在遇到突变载荷时，主动轴定锥盘背面的端面凸轮才起到迅速压缩液压缸，以提升液压压力，防止挠性传动元件打滑的作用。故此结构仍未摆脱加压和调速置于同一动锥盘上存在的上述缺陷。
针对上述加压系统存在的问题，近年来出现了采用机电控制加压的锥盘式无级变速器，其中比较简单的采用碟簧加压、螺杆调速。这种无级变速器虽然结构简单，但存在加压压力无法随变速器所受载荷变化实时调整的缺陷；同时，因碟簧加压机构和螺杆调速机构均安装在动锥盘的一侧，变速器结构不够紧凑。
为克服上述碟簧加压、螺杆调速的缺陷，CN201875074U专利文献公开了一种采用螺旋加压方式的锥盘式无级变速器。该锥盘式无级变速器包括安装在主动轴上的一对主动锥盘和安装在从动轴上的一对从动锥盘；主动锥盘和从动锥盘夹持挠性传动元件。该锥盘式无级变速器的加压机构由安装在主动轴动锥盘背面的加压螺杆和加压螺母构成，加压螺杆和加压螺母为螺旋配合。调速机构包括设在主动轴动锥盘背面的空心螺杆和螺母构成。空心螺杆和螺母为滚珠丝杠结构或滑动螺旋结构，空心螺杆和螺母中的一个与主动轴动锥盘固定连接，其外壁上有调速齿轮。调速电机通过减速器和空心螺杆或螺母上的调速齿轮进行调速。这种锥盘式无级变速器的优点是加压机构对锥盘施加的压力能够随变速器承受扭矩的变化实时调整，当传递扭矩降低时，加压压力也随之降低，从而可提高无级变速器的传递效率，减低各部件的负载，有利于提高系统的使用寿命；且变速器结构简单，能耗和制造成本较低。但这种无级变速器也存在缺陷和不足，一是调速机构和加压机构安装在同一个动锥盘上，加压部分需同时满足动锥盘调速的轴向移动行程，导致变速器的轴向尺寸较大，结构不够紧凑；二是加压机构只能单向加压，不能反向传递扭矩，只能应用在单向传递运动和扭矩的情况。
发明内容
本发明的目的是针对上述现有技术存在的缺陷和不足提供一种结构紧凑、可实现双向加压、加压压力能随传递扭矩实时调整、传递效率高、系统使用寿命长和可靠性高的锥盘式无级变速器。
为实现上述目的，本发明提供的锥盘式无级变速器，包括安装在主动轴上的一对主动锥盘和安装在从动轴上的一对从动锥盘；主动锥盘中的一对锥盘和从动锥盘中的一对锥盘分别通过花键、或球键、或其他允许两个锥盘相互轴向移动而不能相互转动的方式连接；主动锥盘和从动锥盘夹持挠性传动元件；
所述主动锥盘中的一对锥盘包括主动轴动锥盘和主动轴加压锥盘；从动锥盘中的一对锥盘包括从动轴动锥盘和从动轴加压锥盘；主动轴加压锥盘和从动轴加压锥盘中的至少一个加压锥盘的背面(加压端面)设有端面凸轮加压机构；该端面凸轮加压机构包括轴向相对布置的主动凸轮和从动凸轮，主动凸轮与对应的传动轴(主动轴或从动轴)可固定连接(包括做成一体)，也可通过花键、或球键、或平键、或其他允许轴向滑动而不能相互转动的方式连接，从动凸轮与对应的传动轴(主动轴或从动轴)可固定连接，也可通过花键、或球键、或平键、或其它允许轴向滑动而不能相互转动的方式连接；背面设有端面凸轮加压机构的加压锥盘(主动轴加压锥盘和/或从动轴加压锥盘)与对应的传动轴(主动轴或从动轴)保持既可作1mm以内的轴向相互移动、又可相互转动的连接关系；背面未设端面凸轮加压机构的加压锥盘(主动轴加压锥盘或从动轴加压锥盘)与对应的传动轴(主动轴或从动轴)固定连接；
该锥盘式无级变速器设有驱动主动轴动锥盘和从动轴动锥盘轴作同步、同速、同方向轴向移动的调速机构。
所述调速机构包括调速轴和分别设置在主动轴动锥盘及从动轴动锥盘背面的空心螺杆和螺母；主动轴和从动轴分别置于空心螺杆内；空心螺杆和螺母以滚珠丝杠方式或滑动螺旋方式连接；空心螺杆和螺母中的一个通过可承受轴向载荷和径向载荷的轴承与其对应的动锥盘(主动轴动锥盘或从动轴加压锥盘)相连接，另一个通过可承受轴向载荷和径向载荷的轴承与其对应的传动轴(主动轴或从动轴)相连接；空心螺杆或螺母中的一个与机壳以可轴向移动、但不可相互转动的方式连接，另一个通过定比传动机构和调速轴相连接，并使调速轴的转动到主动轴动锥盘轴向移动的转换关系i1和到从动轴动锥盘轴向移动的转换关系i2相等(i＝调速轴的转数/动锥盘轴向移动距离)。
所述端面凸轮加压机构的主动凸轮和从动凸轮为以下两种形式中的一种：
1)主动凸轮和从动凸轮的轴向相对端面上分别设有两个或两个以上沿圆周方向的V形滚道，每个滚道包括相互连接的正向加压段和反向加压段，主动凸轮和从动凸轮的滚道相互对应，相互对应的滚道之间有滚动体，主动凸轮和从动凸轮通过滚动体配合；
2)主动凸轮和从动凸轮的轴向相对端面上分别设有两个或两个以上沿圆周方向分布的V形加压面，每个加压面包括相互连接的正向加压面和反向加压面。
所述背面设有端面凸轮加压机构的加压锥盘(主动轴加压锥盘和/或从动轴加压锥盘)与对应的传动轴(主动轴或从动轴)之间安装有布置在加压锥盘内孔和传动轴之间的滚针轴承。
在端面凸轮加压机构和相应的加压锥盘之间，或端面凸轮加压机构和相应的传动轴之间，设有弹性轴向加压元件。
与现有技术相比较，本发明的有益效果是：
1、将端面凸轮加压机构和调速机构在空间分开，加压机构不安装在调速锥盘上，不需配合调速锥盘的轴向移动，从而可减小加压机构的轴向尺寸，使整个无级变速器结构紧凑。
2、利用端面凸轮加压可实现正反向双向加压。
3、利用端面凸轮加压将输入转矩转化为轴向推力，轴向推力能跟随传递扭矩而变化，既可保证摩擦传动，又可避免系统不必要的过载，有利于提高系统的使用寿命；同时，通过输入扭矩提供轴向推力，不需要额外的能量，可提高系统的效率；可针对载荷突变实时增加轴向推力，防止挠性传动元件在锥盘上打滑，提高系统安全性。
4、调速机构中的两个空心螺杆和螺母通过一根调速轴传动，其调速力矩可以互相抵消，从而可减小调速所需的力矩，降低系统载荷和对调速电机的性能要求。
附图说明
附图为本发明一个实施例的示意图，其中：
图1为该实施例的结构示意图；
图2为采用滚动体传动的端面凸轮加压机构的纵向截面图；
图3为图2端面凸轮加压机构的立体图；
图4为图2端面凸轮加压机构的拆分图；
图5为图2端面凸轮加压机构中主动凸轮和从动凸轮轴向相对端面上的滚道的展开图；
图6为采用斜面传动的端面凸轮加压机构的立体图；
图7为图6端面凸轮加压机构的拆分图；
图8为滚动体传动的端面凸轮加压机构的一种连接方式示意图；
图9为滚动体传动的端面凸轮加压机构的第二种连接方式示意图；
图10为滚动体传动的端面凸轮加压机构的第三种连接方式示意图；
图11为滚动体传动的端面凸轮加压机构的第四种连接方式示意图。
图中：1、主动轴加压锥盘；2、主动轴动锥盘；3、端面凸轮；3-1、主动凸轮；3-2、从动凸轮；3-3、正向加压段；3-4、反向加压段；3-3′、正向加压面；3-4′、反向加压面；3-5、保持架；4、滚动体；5、碟簧；6、(位于主动轴动锥盘上的)螺母；7、(位于主动轴动锥盘上的)空心螺杆；8、调速齿轮；9、调速轴；10、调速电机；11、滚针轴承；12、挠性传动元件；13、转速传感器；14、转速信号发生装置；15、角位移传感器；16、(位于壳体上的)限位机构a；17、(位于齿轮上的)限位机构b；18、主动轴；19、从动轴；20、从动轴动锥盘；21、从动轴加压锥盘；22、(位于从动轴动锥盘上的)螺母；23；(位于从动轴动锥盘上的)空心螺杆。
具体实施方式：
以下结合附图和实施例对本发明作进一步描述。
结合图1，本发明锥盘式无级变速器，在主动轴18上安装由主动轴动锥盘2和主动轴加压锥盘1构成的主动锥盘，在与主动轴18平行的从动轴19上安装由从动轴动锥盘20和从动轴加压锥盘21构成的从动锥盘，主动锥盘和从动锥盘夹持挠性传动元件12，该挠性传动元件可采用无级变速器用推力钢带，或金属带，或链，或V型带。主动轴加压锥盘和从动轴加压锥盘分别通过滚针轴承11与主动轴18和从动轴19保持可在传动轴上作1mm以内微量移动、但不能相互转动的连接关系；主动轴动锥盘和从动轴动锥盘分别通过花键，或球键，或其他允许两个锥盘相互轴向移动、而不能相互转动的方式与主动轴加压锥盘和从动轴加压锥盘连接。在主动轴加压锥盘和从动轴加压锥盘的背面(即加压端面)分别设置端面凸轮加压机构3。该端面凸轮加压机构由两个轴向相对布置的主动凸轮3-1和从动凸轮3-2构成。主动凸轮3-1和从动凸轮3-2可采用滚动体传动，也可采用斜面传动。
结合图2至图5，采用滚动体传动的端面凸轮加压机构，其主动凸轮3-1和从动凸轮3-2的轴向相对端面上分别有六个沿圆周方向的V形滚道(如图5所示)，每个滚道包括相互连接的正向加压段3-3和反向加压段3-4，主动凸轮和从动凸轮的滚道相互对应，相互对应的滚道间有一滚动体4，主动凸轮和从动凸轮通过滚动体配合，六个滚动体采用保持架3-5进行定位(提高系统的可靠性和装配性)。该端面凸轮加压机构的加压原理是：传动轴上的扭矩传递到端面凸轮加压机构，使相对的主动凸轮和从动凸轮的两个端面和滚动体产生相对运动，因 加压锥盘的位置被调速动锥盘和挠性传动元件所限制，主动凸轮和从动凸轮通过其端面和滚动体将施加在滚动体工作半径上的扭矩转化为与摩擦传动所需的轴向推力。主动凸轮和从动凸轮根据扭矩的不同方向，通过滚动体在滚道的正向加压段和反向加压段的相反运动实现正向和反向加压。
根据不同生产和应用条件，端面凸轮加压机构至少可采用以下四种连接方式：
第一种连接方式如图8所示，主动凸轮3-1和对应的传动轴为可滑动花键连接，从动凸轮3-2和对应的加压锥盘是可滑动花键连接，碟簧5作用于从动凸轮上；这种连接方式，凸轮的加工比较方便，但零件数量较多，轴向尺寸相对较大。
第二种连接方式如图9所示，主动凸轮3-1和对应的传动轴，以及从动凸轮3-2和对应的加压锥盘是可滑动花键连接，碟簧5作用在主动凸轮上；这种连接方式与第一种基本相同，但碟簧作用在主动凸轮处，碟簧的尺寸可以减小，转动时离心力较小。
第三种连接方式如图10所示，主动凸轮3-1和对应的传动轴固定联接，从动凸轮3-2和对应的加压锥盘是可滑动花键连接，碟簧5作用在从动凸轮上；这种连接方式直接在传动轴上加工出凸轮加压滚道，结构比较紧凑，可靠，但加工难度较大。
第四种连接方式如图11所示，主动凸轮3-1和对应的传动轴是可滑动花键连接，从动凸轮3-2和对应的加压锥盘固定联接，碟簧5作用在主动凸轮上；与第三种相同，直接在加压锥盘上加工凸轮曲面，结构比较紧凑，可靠，但凸轮加工难度较大。
上述四种连接方式中的碟簧作为弹性轴向加压元件，用于端面凸轮加压机构对加压锥盘提供预紧压力；同时，在正反向加压的切换瞬间，用其压紧两个凸轮，避免滚动体在没有压紧的凸轮间错位。
采用滚动体传动的端面凸轮加压机构的优点是摩擦力较小，灵敏度较高。
采用斜面传动的端面凸轮加压机构如图6和图7所示，其主动凸轮3-1和从动凸轮3-2的轴向相对端面上分别设有两个或两个以上沿圆周方向分布的V形加压面，每个加压面包括相互连接的正向加压面3-3′和反向加压面3-4′。其加压原理与滚动体传动的端面凸轮加压机构类似，主动凸轮和从动凸轮根据扭矩的不同方向，通过正向加压面和反向加压面进行正向和反向加压。
采用斜面传动的端面凸轮加压机构的优点是结构比较简单，缺点是摩擦力较大，灵敏度稍低。
和上述端面凸轮加压机构相配合，本锥盘式无级变速器的调速系统由单独控制主动轴动 锥盘轴向移动改变为控制主动轴动锥盘和从动轴动锥盘同步移动的调速方式。
如图1所示，在主动轴动锥盘2的背面有相互配合的空心螺杆7和螺母6，在从动轴动锥盘20的背面有相互配合空心螺杆23和螺母22，主动轴和从动轴分别置于空心螺杆内，此处所示空心螺杆和螺母为滚珠丝杠结构；空心螺杆7和23与其对应的主动轴动锥盘和从动轴动锥盘分别通过可同时承受轴向载荷和径向载荷的轴承相连接，与其对应的主动轴和从动轴直接相接，螺母通过可同时承受轴向载荷和径向载荷的轴承与其对应的主动轴和从动轴连接，螺母的外壁上分别设有调速齿轮8。调速电机10通过减速机构与调速轴9相接，调速轴与主动轴18和从动轴19平行布置，其上设有两个齿轮(未图示)，分别与所述两个螺母上的调速齿轮8相啮合，相互啮合的两组齿轮组成定比传动机构，使调速轴9的转动到主动轴动锥盘2轴向移动的转换关系i1和到从动轴动锥盘轴20轴向移动的转换关系i2，保持i1＝i2(i＝调速轴的转数/动锥盘轴向移动距离)。
空心螺杆和螺母可通过带有中间滚动体(如滚珠)的滚动螺旋方式连接(未图示)，相对于普通滑动螺旋连接，可减小调速力矩，提高螺旋寿命，降低对调速电机的要求。为了减小调速机构的体积和重量及运动所需的空间尺寸，空心螺杆和螺母之间的滚动体只在空心螺杆和螺母之间的滚道内运动；为了保证调速机构的调速距离和滚动体的运动空间，空心螺杆和螺母之间的滚道的有效工作长度应大于所有滚动体的总长度。空心螺杆通过止动挡销(未图示)或其它可以阻止其转动，但不会对其产生轴向载荷和进行轴向定位的结构、机构、或零件与无级变速器的壳体相连连，将调速的轴向力封闭在传动轴内，使载荷不会传递到相对强度较低的无级变速器壳体上，又不会随调速机构一起转动，既可实现调速功能，又可消除调速力对无级变速器壳体的影响，提高可靠性。
为给电器控制系统(未图示)提供控制信号，可在无级变速器的壳体上、对应主动轴和从动轴的适当位置分别设置转速传感器13和转速信号发生装置14。
为避免执行机构超出行程，危害系统安全，在无级变速器的壳体上还可安装用来测量锥盘移动位置的角位移传感器15，角位移传感器的探头(未图示)与螺母上所开设的圆周方向的滚槽(未图示)相连。
为保证无级变速器的安全运行，在螺母6的调速齿轮8上还可设置有凸起状的限位机构a16，在壳体的相应位置设置有与限位机构a16相配合的限位机构b17，当调速动锥盘轴向移动超出两端极限位置时，通过限位机构a16和限位机构b17，使调速螺母不能继续转动，保证调速机构运行安全。

Claims (5)

  1. 一种锥盘式无级变速器，包括安装在主动轴(18)上的一对主动锥盘和安装在从动轴(19)上的一对从动锥盘；主动锥盘中的一对锥盘和从动锥盘中的一对锥盘分别通过花键、或球键、或其他允许两个锥盘相互轴向移动而不能相互转动的方式连接；主动锥盘和从动锥盘夹持挠性传动元件(12)；其特征在于：
    所述主动锥盘中的一对锥盘包括主动轴动锥盘(2)和主动轴加压锥盘(1)；从动锥盘中的一对锥盘包括从动轴动锥盘(20)和从动轴加压锥盘(21)；主动轴加压锥盘和从动轴加压锥盘中的至少一个加压锥盘的背面设有端面凸轮加压机构(3)；该端面凸轮加压机构包括轴向相对布置的主动凸轮(3-1)和从动凸轮(3-2)，主动凸轮(3-1)与对应的传动轴可固定连接，也可通过花键、或球键、或平键、或其他允许轴向滑动而不能相互转动的方式连接，从动凸轮(3-2)与对应的传动轴可固定连接，也可通过花键、或球键、或平键、或其它允许轴向滑动而不能相互转动的方式连接；背面设有端面凸轮加压机构的加压锥盘与对应的传动轴保持既可作1mm以内的轴向相互移动、又可相互转动的连接关系；背面未设端面凸轮加压机构的加压锥盘与对应的传动轴固定连接；
    该锥盘式无级变速器设有驱动主动轴动锥盘和从动轴动锥盘轴作同步、同速、同方向轴向移动的调速机构。
  2. 根据权利要求1所述的锥盘式无级变速器，其特征在于：所述调速机构包括调速轴(9)和分别设置在主动轴动锥盘及从动轴动锥盘背面的空心螺杆(7、23)和螺母(6、22)；主动轴和从动轴分别置于空心螺杆内；空心螺杆(7、23)和螺母(6、22)以滚珠丝杠方式或滑动螺旋方式连接；空心螺杆(7、23)和螺母(6、22)中的一个通过可承受轴向载荷和径向载荷的轴承与其对应的动锥盘相连接，另一个通过可承受轴向载荷和径向载荷的轴承与其对应的传动轴相连接；空心螺杆或螺母中的一个与机壳以可轴向移动、但不可相互转动的方式连接，另一个通过定比传动机构和调速轴相连接，并使调速轴(9)的转动到主动轴动锥盘轴向移动的转换关系i1和到从动轴动锥盘轴向移动的转换关系i2相等。
  3. 根据权利要求1所述的锥盘式无级变速器，其特征在于：所述端面凸轮加压机构的主动凸轮和从动凸轮为以下两种形式中的一种：
    1)主动凸轮和从动凸轮的轴向相对端面上分别设有两个或两个以上沿圆周方向的V形滚道，每个滚道包括相互连接的正向加压段(3-3)和反向加压段(3-4)，主动凸轮和从动凸轮的滚道相互对应，相互对应的滚道之间有滚动体(4)，主动凸轮和从动凸轮通过滚动体配合；
    2)主动凸轮和从动凸轮的轴向相对端面上分别设有两个或两个以上沿圆周方向分布的V形加压面，每个加压面包括相互连接的正向加压面(3-3′)和反向加压面(3-4′)。
  4. 根据权利要求1所述的锥盘式无级变速器，其特征在于：所述背面设有端面凸轮加压机构的加压锥盘与对应的传动轴之间安装有布置在加压锥盘内孔和传动轴之间的滚针轴承(11)。
  5. 根据权利要求1所述的锥盘式无级变速器，其特征在于：在端面凸轮加压机构和相应的加压锥盘之间，或端面凸轮加压机构和相应的传动轴之间，设有弹性轴向加压元件。
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