CN110878818A - Stepless speed variator - Google Patents

Stepless speed variator Download PDF

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Publication number
CN110878818A
CN110878818A CN201911359099.3A CN201911359099A CN110878818A CN 110878818 A CN110878818 A CN 110878818A CN 201911359099 A CN201911359099 A CN 201911359099A CN 110878818 A CN110878818 A CN 110878818A
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CN
China
Prior art keywords
driven
driving
speed
shaft
disc
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CN201911359099.3A
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Chinese (zh)
Inventor
包木仁
王勇
梁文涛
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Chongqing Zongshen Cvt Co ltd
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Chongqing Zongshen Cvt Co ltd
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Priority to CN201911359099.3A priority Critical patent/CN110878818A/en
Publication of CN110878818A publication Critical patent/CN110878818A/en
Priority to CN202011220400.5A priority patent/CN112128327A/en
Withdrawn legal-status Critical Current

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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
    • 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
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors actuators or related electrical control means therefor
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2884—Screw-nut devices
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2892—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted other gears, e.g. worm gears, for transmitting rotary motion to the output mechanism
    • 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
    • F16H2061/66277—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 by optimising the clamping force exerted on the endless flexible member
    • 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
    • F16H2061/66295—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 geometrical interrelationship of pulleys and the endless flexible member, e.g. belt alignment or position of the resulting axial pulley force in the plane perpendicular to the pulley axis

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

The invention discloses a continuously variable transmission, which comprises a driving part, a driven part and a flexible element arranged between the driving part and the driven part, wherein the driving part comprises a driving shaft and a pair of driving conical disks which are arranged on the driving shaft in a transmission manner and used for clamping the flexible element; be provided with the elastic component between the back of initiative movable cone dish and the axially fixed locating part the back of driven fixed cone dish is provided with but axial promotion the elastic speed control mechanism of driven movable cone dish, the stubborn coefficient of elastic component is K1, the stubborn coefficient of elastic speed control mechanism is K2, and K1 is more than or equal to K2. The invention simplifies the speed regulation mode of the stepless speed changer, improves the speed regulation speed and reduces the cost.

Description

Stepless speed variator
Technical Field
The invention relates to a speed change mechanism, in particular to a continuously variable transmission.
Background
The Chinese patent CN201110193407.7 discloses a continuously variable transmission, and specifically discloses two parallel transmission shafts, wherein each of the two transmission shafts is provided with at least one pair of conical discs with conical surfaces oppositely arranged, at least one flexible transmission element is clamped between the conical discs, one conical disc in each pair of conical discs can axially move on the transmission shaft, and the other conical disc cannot axially move on the transmission shaft and can rotate along with the transmission shaft; the back of a conical disc which can axially move between a transmission shaft and the shaft is connected with a screw mechanism (a motor-driven speed regulating mechanism), the screw mechanism consists of a hollow screw and a nut matched with the hollow screw, and the transmission shaft is arranged in the hollow screw; one of the hollow screw rod and the nut of the screw mechanism is connected with the transmission shaft which belongs to the screw mechanism through a bearing which can bear axial load and radial load at the same time, and is directly connected with the conical disc which belongs to the screw mechanism and can move axially; the other one of the hollow screw and the nut is connected with the cone disc which is axially movable and belongs to the hollow screw and the nut through a bearing which can bear axial load and radial load simultaneously, and is directly connected with the transmission shaft which belongs to the hollow screw and the nut; one of the hollow screw and the nut is connected … … with a motor through a speed reducing mechanism, two cone discs which can move axially and are respectively positioned on the two transmission shafts are respectively connected with the cone discs through at least one end directly or indirectly, and the other end is directly or indirectly connected with a spring or a spring group on the transmission shaft of the cone disc and is pressed on the flexible transmission element and the fixed cone disc; wherein, the coefficient of stiffness or the total coefficient of stiffness of the conical disc connected with the speed-adjusting spiral mechanism and the spring or the spring group on the transmission shaft is larger than the coefficient of stiffness or the total coefficient of stiffness of the spring or the spring group on the other transmission shaft.
The above patent further provides one embodiment, in which a driven shaft pressing spring is arranged on the back of the driven shaft moving conical disc, and a motor driving speed regulating mechanism, namely a spiral speed regulating mechanism, is arranged on the back of the driving shaft moving conical disc. The coefficient of stiffness of the compression spring of the spiral speed regulating mechanism on the driving shaft is larger than that of the compression spring on the driven shaft.
With the continuously variable transmission in the above patent, there are the following problems: 1. the compression spring needs to be large in size and large in elasticity, and further the cone disc is too large in size. 2. When the speed is regulated, the speed is regulated by driving the spiral speed regulating mechanism with the motor no matter the transmission ratio is from large to small or from small to large, so that the motor with positive and negative rotation must be adopted, and the speed regulation is too slow by overcoming the elasticity of the spring. 3. The speed regulation system needs to coordinate the stiffness coefficients of the two groups of disc springs at the same time, so that the speed regulation is complex; and the speed regulation cone disc is subjected to bidirectional stress, so that the speed regulation is too slow for the speed regulation with small transmission ratio, and the bearing structure is complex, the cost is high and the space is large. 4. The change of the clamping force of the flexible transmission element during transmission is opposite to the change of the elastic force of the compression spring on the driven shaft, so that the speed regulation is slow and the speed regulation force is large.
Disclosure of Invention
The invention aims to provide a continuously variable transmission which is low in cost and simple and quick in speed regulation.
In order to achieve the above object, the present invention is realized by: a continuously variable transmission comprises a driving part, a driven part and a flexible element arranged between the driving part and the driven part, wherein the driving part comprises a driving shaft and a pair of driving conical disks which are arranged on the driving shaft in a transmission mode and used for clamping the flexible element, and the driven part comprises a driven shaft and a pair of driven conical disks which are arranged on the driven shaft in a transmission mode and used for clamping the flexible element; wherein a initiative awl dish is for fixing the initiative fixed cone dish on the driving shaft, and another initiative awl dish moves the awl dish for can following the initiative of driving shaft endwise slip, and one of them driven awl dish is for fixing driven fixed cone dish on the driven shaft and relative with initiative fixed cone dish, and another driven awl dish is for can following driven shaft endwise slip driven movable cone dish and relative with initiative fixed cone dish, its characterized in that: be provided with the elastic component between the back of initiative movable cone dish and axially fixed locating part the back of driven movable cone dish is provided with but axial promotion the elasticity speed adjusting mechanism of driven movable cone dish, the stubborn coefficient of elastic component is K1The coefficient of stiffness of the elastic speed regulating mechanism is K2And K is1≥K2. The stepless speed changer arranged in the mode has the advantages that the elastic speed regulating mechanism is arranged on the driven shaft, the elastic piece is arranged on the driving shaft, and the stiffness coefficient of the elastic speed regulating mechanism is set to be less than or equal to the stiffness coefficient of the elastic piece. When the speed is regulated from a large transmission ratio to a small transmission ratio, the driven movable conical disc is only pushed by the elastic speed regulation mechanismThe axial movement is enough, and the force applied by the flexible element is consistent with the change direction of the clamping force of the flexible element, so that the speed regulation speed is improved. When the speed is regulated from a small transmission ratio to a large transmission ratio, the elastic speed regulating mechanism does not need to apply force and only needs to push the driven movable conical disc to realize speed regulation through the axial return force of the elastic piece on the driving shaft. The speed regulating mechanism is simple, the speed regulating force requirement is low, and the speed regulating efficiency is high. In the continuously variable transmission arranged in the mode, the elastic speed regulating mechanism does not need to overcome the elastic force of the elastic speed regulating mechanism when returning, so that the elastic speed regulating mechanism and the elastic part can be designed to be smaller in volume and elastic force, the conical disc can be designed to be smaller, more parts can be saved, the cost of the continuously variable transmission is reduced, and the volume of the continuously variable transmission is reduced.
Preferably, the elastic speed regulating mechanism comprises a hollow speed regulating screw and a speed regulating nut; the hollow speed regulation screw rod is connected with the driven shaft through a first bearing, one end of a speed regulation nut is connected with the driven cone disc through a second bearing, the other end of the speed regulation nut is provided with an internal thread and is in threaded connection with the external thread of the hollow speed regulation screw rod, the hollow speed regulation screw rod is limited in circumferential rotation through a fixed limiting block, the speed regulation nut is driven to rotate through a driving mechanism, and a disc spring assembly is sleeved on the driven shaft between the first bearing and the second bearing.
Preferably, the elastic part is a disc spring assembly, the limiting part is a shaft sleeve fixed on the driving shaft, and the disc spring assembly is sleeved on the driving shaft.
In order to further realize the speed regulation range of the transmission ratio, the elastic element is composed of n disc springs, and the relation n is more than or equal to 4. This way a range of 0.5-2 four times the transmission ratio requirement can be achieved.
In order to further realize the speed regulation range of the transmission ratio, the inner diameter of the disc spring is D, the outer diameter of the disc spring is D, the thickness is t, and the outer diameter of the conical disc is D0And has the following relation, D < D0+1，D/d<1.6，t>(D0+ 1)/d. By such an arrangement, a curve of axial force requirements can be achieved, achieving maximum to minimum gear ratios.
To further ensure the speed regulation range and the stability of the disc spring, the openingA retainer ring is arranged between the disc springs with opposite openings, and the diameter of the retainer ring is d0And the following conditions are satisfied: t/10 < d0< t. The thickness of the retainer ring is too large to affect the transmission ratio range, resulting in a reduction of the transmission ratio range, and too small to affect the force stability of the disc spring, so that selection of a particular thickness is required.
In order to further prolong the service life of the transmission, the speed regulating nut and the hollow speed regulating screw are of rolling spiral or sliding spiral structures, wherein the diameter is DLAnd satisfies the following relationship: dL＞D0/2。
In order to further realize the speed regulation range, the thread length L of the hollow speed regulation screw or the speed regulation nut meets the following relationship: l > 2 (D)0/2- D0/3）tan(11π/180)。
In order to further reduce the space of the transmission, the driving mechanism comprises a driving shaft, one end of the driving shaft is provided with a driving gear, driven teeth meshed with the driving gear are arranged on the outer wall of the speed regulating nut, and the other end of the driving shaft is driven by a motor and a worm and gear mechanism. The motor drives the worm, the worm drives the worm wheel to rotate, the worm wheel further drives the driving gear on the driving shaft to rotate, and the speed regulating nut is driven due to meshing with the driving gear.
In order to further reduce the space of the transmission, the driving mechanism comprises a driving shaft, a turbine is arranged on the driving shaft, the outer wall of the turbine and the outer wall of the speed regulating nut are provided with transmission teeth which are meshed with each other, and the turbine is driven by a motor and a worm. The motor drives the worm, the worm drives the worm wheel to rotate, and the worm wheel further drives the speed regulating nut to rotate, so that the axial movement of the speed regulating nut is realized.
Has the advantages that:
according to the invention, through structure adjustment, the elastic speed regulating mechanism is arranged on the back of the driven movable conical disc of the driven shaft, and the disc spring assembly is arranged on the back of the driving movable conical disc of the driving shaft for matching, so that the speed adjustment of the whole transmission is realized. And the coefficient of stiffness of the disc spring assembly of the elastic speed regulating mechanism is set to be less than or equal to the coefficient of stiffness of the disc spring assembly on the driving shaft. Therefore, the speed regulation mode of the stepless speed changer is simplified, the speed regulation speed is improved, the speed regulation force required by the elastic speed regulation mechanism is reduced, and the power required by the speed regulation motor is further reduced. The space arrangement of the transmission is optimized, the size and parts of the transmission are reduced, and the cost is reduced.
Specifically, the method comprises the following steps: 1. in the stepless speed changer, in the speed regulation process of which the transmission ratio is reduced from high to low, only the elastic speed regulation mechanism is needed to pressurize the driven dynamic conical disc, and the force applied by the elastic speed regulation mechanism is consistent with the change direction of the clamping force required by the flexible element, so that the speed regulation speed is improved, and the force required by a speed regulation motor is reduced. In the speed regulation process of the transmission ratio from small to large, the elastic speed regulation mechanism does not need to apply force, and only needs to transmit the axial return force of the disc spring assembly on the driving movable conical disc to the driven movable conical disc through the flexible element, so that the driven movable conical disc is axially pushed to realize the increase of the transmission ratio. In the process, additional stress is not required to be applied to the elastic speed regulating mechanism through the speed regulating motor, and the elastic force of a disc spring on the elastic speed regulating mechanism is not required to be overcome, so that the speed regulating speed is high. Therefore, the speed regulation force is reduced by reasonably configuring the disc spring, and the speed regulation is faster for small transmission ratio and direction.
2. Through the design of the speed regulating mechanism and the disc spring assembly, the force required to be overcome by the driven dynamic cone disc is small in the speed regulating process, the stress condition of the driven dynamic cone disc is consistent with the change direction of the clamping force of the flexible element, and overlarge elastic force does not need to be designed for the disc spring, so that the design volume of the cone disc is further reduced, and the overall volume of the continuously variable transmission is reduced.
3. The stepless speed changer has simple speed regulation structure, the conical disc driven by the speed regulation mechanism is changed into unidirectional stress from bidirectional stress, the bearing type is simplified, the positioning mode is simplified, and the cost is reduced.
Drawings
FIG. 1 is a block diagram of a continuously variable transmission of the present invention;
fig. 2 is a partially enlarged view of fig. 1.
Detailed Description
The following detailed description of the embodiments of the present invention will be made with reference to the accompanying drawings, but the present invention is not limited to these embodiments, and any modifications or substitutions in the basic spirit of the embodiments will still fall within the scope of the present invention as claimed in the claims.
Example 1: as shown in fig. 1, the present embodiment provides a continuously variable transmission including a driving portion and a driven portion, and a flexible element 1 disposed between the driving portion and the driven portion, the driving portion including a driving shaft 2 and a pair of driving conical disks drivingly disposed on the driving shaft for clamping the flexible element, and the driven portion including a driven shaft 3 and a pair of driven conical disks drivingly disposed on the driven shaft for clamping the flexible element. One of the driving conical discs is a driving fixed conical disc 21 fixed on the driving shaft 2, and the other driving conical disc is a driving movable conical disc 22 arranged on the driving shaft in an axially sliding manner. One of the driven conical disks is a driven fixed conical disk 31 fixed on the driven shaft 3 and opposite to the driving fixed conical disk 21, and the other driven conical disk is a driven movable conical disk 32 axially slidably arranged on the driven shaft 3 and opposite to the driving movable conical disk. In addition, be provided with the elastic component between the back of initiative movable cone disc and the axially fixed locating part the back of driven movable cone disc is provided with but axial promotion the elasticity speed adjusting mechanism 4 of driven movable cone disc, the coefficient of stiffness of elastic component is K1, the coefficient of stiffness of elasticity speed adjusting mechanism is K2, and K1 is more than or equal to K2.
The back surface of the active movable conical disc refers to the surface of the active movable conical disc, which is back to the active fixed conical disc, and the surface facing the active fixed conical disc is the front surface. The back of the driven movable conical disc refers to the side of the driven movable conical disc, which is back to the driven fixed conical disc, and the side facing the driven fixed conical disc is the front side.
In this embodiment, the elastic member is a disc spring assembly B23 sleeved on the driving shaft, and the limiting member is a bushing C24 fixed on the driving shaft.
In this embodiment, the elastic speed adjusting mechanism 4 includes a driving mechanism 6 and an elastic push disc assembly 5 acting on the driven dynamic cone disc. As one embodiment in this embodiment, the push disc assembly includes a hollow speed regulation screw 52 and a speed regulation nut 51, an integral or separate shaft sleeve a33 is provided on the outer end surface of the driven movable conical disc, and one end of the speed regulation nut is fixed to be connected with the shaft sleeve a through a bearing a 53. The other end of the speed regulating nut is far away from the driven movable conical disc and is in threaded connection with the hollow speed regulating screw. A shaft sleeve B55 is fixed on the driven shaft at one end far away from the driven movable conical disc, and the hollow speed regulating screw is fixed on the shaft sleeve B55 through a bearing B56. And an external thread and an internal thread which are matched with each other are arranged between the outer wall of the hollow speed regulating screw rod and the inner wall of the speed regulating nut, and a ball 54 is arranged between the external thread and the internal thread. And an axial disc spring component A57 is arranged in a cavity limited by the hollow speed regulating screw and the speed regulating nut, and specifically, the disc spring component A is sleeved on the driven shaft and is abutted against the bearing A and the bearing B.
In addition, an element for axially and circumferentially limiting the hollow speed regulating nut is also arranged. The shell 100 of the continuously variable transmission is provided with a stop block 58, the stop block can limit circumferential rotation of the hollow speed regulating nut, the inner wall of the hollow speed regulating nut is provided with a circular truncated cone, the circular truncated cone is clamped on the end face, facing one side of the conical disc, of the bearing B56, limiting when the disc spring assembly A57 returns is further achieved, and accurate transmission ratio values are guaranteed.
In another embodiment of the present invention, the driving mechanism 6 includes a driving shaft 61, a driving gear 62 is fixed on the driving shaft, and the outer wall of the speed nut is provided with a driven gear 59 meshed with the driving gear for transmission. A turbine assembly 63 is fixedly arranged on the driving shaft, and the driving shaft is driven by a motor driving a screw rod 64 matched with the turbine assembly. As another embodiment, a driving tooth engaged with the driven tooth 59 of the outer wall of the speed nut may be provided directly outside the turbine assembly.
When the continuously variable transmission of the embodiment is adopted, the disc spring assembly B is sleeved on the driving shaft in advance, and all the conical discs, the flexible elements and the elastic driving mechanism are assembled. When the transmission ratio is maximum, the disc spring component A and the disc spring component B are guaranteed not to be compressed. When the continuously variable transmission in the present embodiment is used, the gear ratio of the continuously variable transmission needs to be gradually changed from maximum to minimum. At the moment, the driving motor drives the driving gear to drive the speed regulating nut on the driven shaft to rotate, so that the axial movement (towards the driven fixed cone disc) of the speed regulating nut is realized, the driven movable cone disc is pushed to extrude the flexible element, and the transmission ratio of the continuously variable transmission is reduced. At the moment, the axial thrust of the driven movable conical disc is further transmitted to the driving movable conical disc through the flexible element, so that the driving movable conical disc axially compresses the disc spring component B, and the disc spring component B stores the force. In the speed regulation process, the force required by the flexible element for speed regulation is gradually increased and is provided by the driven conical disc, and the force borne by the driven conical disc is also gradually increased, namely, the force required by the flexible element for speed regulation and the force borne by the driven conical disc are both gradually increased, the force variation trend is consistent, and the speed regulation is faster.
If the speed change from the small transmission ratio to the large transmission ratio needs to be realized, the driving of the motor is only stopped, the axial force released by the disc spring assembly B on the driving shaft in the returning process is transmitted to the driven movable conical disc on the driven shaft through the flexible element, so that the driven movable conical disc is pushed to move towards the direction far away from the driven fixed conical disc, the extrusion on the flexible element is removed, and the speed regulation from the small transmission ratio to the large transmission ratio is realized. Moreover, because the coefficient of stiffness of the disc spring assembly B in this embodiment is greater than that of the disc spring assembly a, no external force is required to be provided by the motor during the speed regulation, and the situation of inaccurate speed regulation cannot occur due to the axial limitation of the hollow speed regulation nut. In the speed regulation process, the force required by the flexible element for speed regulation is gradually reduced and is provided by the driven conical disk, and the force borne by the driven conical disk is also gradually reduced, namely, the force required by the flexible element for speed regulation and the force borne by the driven conical disk are both gradually reduced, so that the speed regulation is faster. In addition, the driven dynamic cone disk does not need to overcome the elasticity of the disc spring component A in the speed regulation process, and the speed regulation speed is further improved.
Therefore, no matter the speed change from a large transmission ratio to a small transmission ratio or from the small transmission ratio to the large transmission ratio, the required speed regulating force is smaller, the disc spring assembly can be designed to be smaller, and further the volume of the cone disc assembly can be designed to be smaller. Not only the space size of the transmission is reduced, but also the type of the bearing is simplified, the positioning mode is simplified, and the cost is saved. Furthermore, because the speed regulation force is small, a motor with small power can be adopted, and the cost is further saved.
As another implementation manner in this embodiment, the driving fixed cone disc and the driving shaft may be integrally disposed or fixedly connected through a shoulder or a snap spring, and the driven fixed cone disc and the driven shaft may be integrally disposed or fixedly connected through a shoulder or a snap spring.
This embodiment sets up elasticity speed adjusting mechanism and the back of the initiative awl dish that moves of driving shaft sets up the dish spring subassembly and cooperates the speed adjustment that realizes whole derailleur through structural adjustment at the driven awl dish back of driven shaft. And the coefficient of stiffness of the disc spring assembly of the elastic speed regulating mechanism is set to be less than or equal to the coefficient of stiffness of the disc spring assembly on the driving shaft. Therefore, the speed regulation mode of the stepless speed changer is simplified, the speed regulation speed is improved, the speed regulation force required by the elastic speed regulation mechanism is reduced, and the power required by the speed regulation motor is further reduced. The space arrangement of the transmission is optimized, the size and parts of the transmission are reduced, and the cost is reduced.
Example 2: the present embodiment is an optimization selection made on the basis of embodiment 1.
In this embodiment, the disc spring assembly a is composed of n disc springs, and has the following relationship n ≧ 4, which can be selected from but not limited to 4, 6, 8, 10, 12, 14, 16, 18, and so on. In this embodiment, the disc spring assembly B is composed of 6 disc springs, and the disc spring assembly a is composed of 10 disc springs.
The inner diameter of the disc spring is D, the outer diameter of the disc spring is D, the thickness of the disc spring is t, the outer diameter of the conical disc is D0, and the relations that D is less than D0+1, and D/D is less than 1.6, t > (D0+1)/D exist.
In the embodiment, the change curve of the axial force of the conical disc and the change curve of the transmission ratio are further balanced by limiting the thickness, the inner diameter and the outer diameter of the disc spring, so that the change trends are basically consistent.
Example 3: the embodiment is further optimized on the basis of embodiment 1 or embodiment 2.
In this embodiment, a retainer ring 25 is disposed between the disc springs with opposite openings, the diameter of the retainer ring is d0, and the following conditions are satisfied: t/10 < d0 < t, wherein t is the thickness of the disc spring.
The thickness of the retainer ring of the embodiment is too large to influence the transmission ratio range, so that the transmission ratio range is reduced, and too small to influence the force stability of the disc spring, so that the selection of special thickness is needed to ensure the transmission ratio range and the stability of the disc spring.
Example 4: the embodiment is further optimized on the basis of embodiment 1, embodiment 2 or embodiment 3.
In this embodiment, the thread length L of the hollow speed-adjusting screw or the speed-adjusting nut satisfies the following relationship: l > 2 (D0/2-D0/3) tan (11 π/180).
As another implementation manner in this embodiment, the hollow speed regulation screw and the speed regulation screw are of a rolling screw structure or a sliding screw structure. Wherein the diameter is DL, and the following relation is satisfied: DL > D0/2. When the rolling screw is adopted, a ball is arranged between the nut and the screw rod, and the pitch diameter is 2 times of the distance from the center of the ball to the axis of the driven shaft.
In the embodiment, the realization of the speed regulation range is ensured and the service life of the transmission is prolonged by special setting of the hollow speed regulation screw rod and the speed regulation nut.

Claims (10)

1. A continuously variable transmission comprises a driving part, a driven part and a flexible element arranged between the driving part and the driven part, wherein the driving part comprises a driving shaft and a pair of driving conical disks which are arranged on the driving shaft in a transmission mode and used for clamping the flexible element, and the driven part comprises a driven shaft and a pair of driven conical disks which are arranged on the driven shaft in a transmission mode and used for clamping the flexible element; one driving cone disk is a driving fixed cone disk fixed on the driving shaft, and the other driving cone disk can be axially fixed along the driving shaftGliding initiative moves the awl dish, and one of them driven awl dish is for fixing driven fixed cone dish on the driven shaft and relative with initiative fixed cone dish, and another driven awl dish is for can following driven shaft axial slip's driven cone dish and relative with initiative movable cone dish, its characterized in that: be provided with the elastic component between the back of initiative movable cone dish and axially fixed locating part the back of driven movable cone dish is provided with but axial promotion the elasticity speed adjusting mechanism of driven movable cone dish, the stubborn coefficient of elastic component is K1The coefficient of stiffness of the elastic speed regulating mechanism is K2And K is1≥K2。
2. The variable transmission of claim 1, wherein: the elastic speed regulating mechanism is wrapped by a hollow speed regulating screw and a speed regulating nut; the hollow speed regulation screw rod is connected with the driven shaft through a first bearing, one end of a speed regulation nut is connected with the driven cone disc through a second bearing, the other end of the speed regulation nut is provided with an internal thread and is in threaded connection with the external thread of the hollow speed regulation screw rod, the hollow speed regulation screw rod is limited in circumferential rotation through a fixed limiting block, the speed regulation nut is driven to rotate through a driving mechanism, and a disc spring assembly is sleeved on the driven shaft between the first bearing and the second bearing.
3. The continuously variable transmission according to claim 1 or 2, characterized in that: the elastic part is a disc spring assembly, the limiting part is a shaft sleeve fixed on the driving shaft, and the disc spring assembly is sleeved on the driving shaft.
4. The variable transmission of claim 3, wherein: the elastic member is composed of n disc springs, and has the following relationship that n is more than or equal to 4.
5. The continuously variable transmission of claim 3 or 4, wherein: the inner diameter of the disc spring is D, the outer diameter of the disc spring is D, the thickness of the disc spring is t, and the outer diameter of the conical disc is D0And has the following relation, D < D0+1，D/d<1.6，t>(D0+1)/d。
6. The continuously variable transmission of claim 3, 4 or 5, wherein: a retainer ring is arranged between the disc springs with opposite openings, and the diameter of the retainer ring is d0And the following conditions are satisfied: t/10 < d0＜t。
7. The continuously variable transmission of claim 3, 4, 5 or 6, wherein: the speed regulating nut and the hollow speed regulating screw are of rolling spiral or sliding spiral structure, and the pitch diameter of the spiral structure is DLAnd satisfies the following relationship: dL＞D0/2。
8. The continuously variable transmission of claim 2, 3, 4, 5, 6 or 7, wherein: the thread length L of the hollow speed regulating screw or the speed regulating nut meets the following relation: l > 2 (D)0/2- D0/3）tan(11π/180)。
9. The continuously variable transmission of claim 2, 3, 4, 5, 6, 7 or 8, wherein: the driving mechanism comprises a driving shaft, a driving gear is arranged at one end of the driving shaft, driven teeth meshed with the driving gear are arranged on the outer wall of the speed regulating nut, and the other end of the driving shaft is driven by a motor and a worm and gear mechanism.
10. The continuously variable transmission of claim 2, 3, 4, 5, 6, 7 or 8, wherein: the driving mechanism comprises a driving shaft, a turbine is arranged on the driving shaft, transmission teeth which are meshed with each other are arranged on the outer wall of the turbine and the outer wall of the speed regulating nut, and the turbine is driven by a motor and a worm.
CN201911359099.3A 2019-12-25 2019-12-25 Stepless speed variator Withdrawn CN110878818A (en)

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Application Number Priority Date Filing Date Title
CN201911359099.3A CN110878818A (en) 2019-12-25 2019-12-25 Stepless speed variator
CN202011220400.5A CN112128327A (en) 2019-12-25 2020-11-05 Stepless speed variator

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Application Number Priority Date Filing Date Title
CN201911359099.3A CN110878818A (en) 2019-12-25 2019-12-25 Stepless speed variator

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CN202011220400.5A Pending CN112128327A (en) 2019-12-25 2020-11-05 Stepless speed variator

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113653781A (en) * 2020-12-28 2021-11-16 重庆宗申无级变速传动有限公司 Stepless speed variator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113653781A (en) * 2020-12-28 2021-11-16 重庆宗申无级变速传动有限公司 Stepless speed variator

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