CN110043623B - Stepless speed change device - Google Patents

Stepless speed change device Download PDF

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Publication number
CN110043623B
CN110043623B CN201910249533.6A CN201910249533A CN110043623B CN 110043623 B CN110043623 B CN 110043623B CN 201910249533 A CN201910249533 A CN 201910249533A CN 110043623 B CN110043623 B CN 110043623B
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CN
China
Prior art keywords
conical
rotor
transmission
floating
driving
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CN201910249533.6A
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Chinese (zh)
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CN110043623A (en
Inventor
何奥元
郭晓亮
王海峰
邓向斌
丁文兵
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Hangzhou Lebben Technology Co ltd
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Hangzhou Lebben Technology Co ltd
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Priority to CN201910249533.6A priority Critical patent/CN110043623B/en
Publication of CN110043623A publication Critical patent/CN110043623A/en
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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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/44—Gearings providing a continuous range of gear ratios in which two members of non-uniform effective diameter directly co-operate with one another
    • 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
    • F16H61/664—Friction gearings
    • 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

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

Abstract

The present invention provides a continuously variable transmission device including: the output shaft comprises a conical cylinder with a hollow inside, the outer side surface of the conical cylinder is used for outputting driving force, and the inner side surface of the conical cylinder is a first acting surface; the input shaft comprises a conical entity arranged in the conical cylinder, the conical surface of the conical entity is a second action surface, the conical direction of the second action surface is opposite to the conical direction of the first action surface, and a first generatrix of the first action surface is parallel to a second generatrix of the second action surface; a transmission member; and the variable speed driving mechanism is used for driving the transmission member to move along a working path to change the transmission ratio between the input shaft and the output shaft, and the working path extends along the directions of the first bus and the second bus. The technical scheme disclosed by the invention is compact in volume, so that the layout and the installation of the interior of the engine room are convenient; meanwhile, the speed change effect is smooth, and the speed change effect is good.

Description

Stepless speed change device
Technical Field
The invention relates to the field of speed variators, in particular to a stepless speed change device.
Background
The stepless speed changer is a key subject in the later development period of the automobile, and is popular in the era of pursuing automobile comfort due to the characteristics of stable acceleration and fuel saving in an acceleration state. At present, the stepless speed changer is realized by hydraulic transmission, electric transmission and mechanical transmission, and belongs to the mechanical transmission with more reliability. In the designed mechanical transmission, if meshing of a tooth structure occurs, the mechanical transmission belongs to an infinitely approaching continuously variable transmission, and is not truly infinitely variable torque. The mechanical transmission with infinite torque conversion is disc type, cone type and spherical type. The cone type contact is divided into direct contact and indirect contact by an intermediate machine member.
The related art discloses a ring collision stop protection structure for a conical ring type continuously variable transmission, which comprises a first transmission cone and a transmission ring, wherein the surface of the first transmission cone is contacted with one surface of the transmission ring, the small end of the first transmission cone is provided with a shaft shoulder opposite to the cone surface, and the shaft shoulder is in the shape of a revolution body; the surfaces of the driving ring, the shaft shoulder and the cone have the following geometric matching relations: when the transmission ring contacts the shaft shoulder, a first contact point is arranged between the transmission ring and the shaft shoulder, a second contact point is arranged between the transmission ring and the conical surface, the distance from the first contact point to the conical axis is a first contact radius, the distance from the second contact point to the conical axis is a second contact radius, and the first contact radius is smaller than the second contact radius. The transmission input shaft and the transmission output shaft disclosed in the technical document are arranged in a staggered mode in space, and are driven by a cone ring with a large size, so that the whole transmission is large in size and is not beneficial to the layout in a cabin.
Disclosure of Invention
The invention provides a stepless speed change device with small volume, good speed change effect and smooth speed change process.
A continuously variable transmission comprising:
the output shaft comprises a conical cylinder with a hollow inside, the outer side surface of the conical cylinder is used for outputting driving force, and the inner side surface of the conical cylinder is a first acting surface;
the input shaft comprises a conical entity arranged in the conical cylinder, the conical surface of the conical entity is a second action surface, the conical direction of the second action surface is opposite to the conical direction of the first action surface, and a first generatrix of the first action surface is parallel to a second generatrix of the second action surface;
the transmission piece is positioned in the radial direction of the axis of the input shaft and is in transmission connection between the first acting surface and the second acting surface;
and the variable speed driving mechanism is used for driving the transmission member to move along a working path to change the transmission ratio between the input shaft and the output shaft, and the working path extends along the directions of the first bus and the second bus.
The following provides several alternatives, but not as additional limitations to the above-described overall scheme, and only further additions or preferences, each of which may be individually combined for the above-described overall scheme, or may be combined among multiple alternatives, without technical or logical contradictions.
Optionally, the transmission member is a rotor in friction transmission with the first acting surface and the second acting surface.
Optionally, the rotors are provided with two rotors which are in friction transmission with each other, and the two rotors are in friction transmission with the first acting surface and the second acting surface respectively.
Optionally, the variable speed drive mechanism includes:
a rotor box for defining and guiding the position of the rotor on the working path;
a drive belt secured to the rotor case and for driving the rotor case to change position on the working path;
a guide bar for guiding the rotor box to move along the working path;
and a driving source for providing a driving force to the driving belt.
Optionally, the variable speed drive mechanism comprises a rigid guide bar and a floating platform comprising:
the rotor box is used for limiting and guiding the position of the rotor on the working path, and a first sliding block and a second sliding block which can swing freely are hinged at two ends of the rotor box, and the first sliding block is in sliding fit with the guide rod;
a floating frame including a floating rod slidingly engaged with the second slider and a driving belt mounted on the floating rod for driving the second slider to move along the floating rod;
and a driving source for providing a driving force to the driving belt.
Optionally, the rotor install in through the pivot rotor case, the pivot wear to locate bar hole on the rotor case, two the rotor can be along bar hole draws close or keep away from each other.
Optionally, the continuously variable transmission device further comprises a box body, the input shaft is rotatably installed on the box body, and the conical entity is accommodated in the box body; the variable speed driving mechanism is arranged around the conical entity, the guide rod is fixed with the box body, and the floating frame is movably arranged on the box body; the conical cylinder is rotatably arranged in the box body, the conical entity and the variable speed driving mechanism are accommodated in the hollow area inside the box body, and the rotor is positioned between the conical entity and the conical cylinder and props against the conical entity and the conical cylinder.
Optionally, the connection mode of the floating platform and the box body is:
the box body is provided with a directional elastic piece for installing the floating platform, and the directional elastic piece can be stressed and deformed in the floating direction of the floating platform and keep rigidity in other directions;
or (b)
The box body is provided with an electric control mechanism for controlling the floating platform.
Optionally, the transmission member has a constant speed ratio state, in which a movement direction of the transmission member is perpendicular to a plane in which the first bus and the second bus are located, and the driving belt is configured to drive the transmission member to exit the constant speed ratio state.
Optionally, the floating platform further comprises a limiting block for limiting the movement stroke of the driving belt, the limiting block is mounted on the driving belt and moves along with the driving belt, and the limiting block abuts against the floating frame when the driving belt moves to the designed maximum stroke.
The technical scheme disclosed by the invention can bring the following optimized technical effects:
the size is compact, the size of the speed changing device can be effectively reduced due to the arrangement of the input shaft and the output shaft, and therefore the layout and the installation of the cabin are convenient;
the speed change effect is smooth, the transmission ratio between the two conical surfaces is changed through the transmission piece, the transmission ratio change process is uniform and fine, and different speed change requirements under different working conditions are realized;
the speed change effect is good, and the position of the transmission part and the speed of the change position can be controlled finely through the speed change driving mechanism, so that the speed ratio change can be controlled accurately.
Drawings
Fig. 1 is a schematic view of a continuously variable transmission in the present embodiment;
FIG. 2 is a schematic view of the internal structure of the continuously variable transmission of FIG. 1 with the output shaft omitted;
fig. 3 is an enlarged view at a in fig. 2.
Reference numerals in the drawings are described as follows:
51. an output shaft; 511. a conical cylinder; 512. an auxiliary shaft; 513. a first active surface; 514. a first bus; 52. an input shaft; 521. a conical entity; 522. a second active surface; 523. a second bus bar; 53. a transmission member; 531. a rotor; 5311. a rotating shaft; 54. a variable speed drive mechanism; 541. a rotor case; 5411. a first slider; 5412. a second slider; 542. a drive belt; 543. a guide rod; 544. a turntable; 545. a floating platform; 5451. a limiting block; 546. a floating frame; 5461. a floating rod.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It will be understood that when an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. When an element is referred to as being "disposed on" another element, it can be directly on the other element or intervening elements may also be present.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and/or" as used herein includes any and all combinations of one or more of the associated listed items.
A continuously variable transmission comprising:
an output shaft 51 including a conical tube 511 having a hollow interior and an auxiliary shaft 512 for friction transmission with the conical tube 511, the outer side surface of the conical tube 511 outputting a driving force through the auxiliary shaft 512, the inner side surface of the conical tube 511 being a first acting surface 513;
the input shaft 52 includes a conical solid 521 disposed inside the conical cylinder 511, the conical surface of the conical solid 521 being a second active surface 522, the conical orientation of the second active surface 522 being opposite to the conical orientation of the first active surface 513, the first generatrix 514 of the first active surface 513 being parallel to the second generatrix 523 of the second active surface 522;
a transmission member 53 located in a radial direction of the axis of the input shaft 52 and drivingly connected between the first acting surface 513 and the second acting surface 522;
a variable speed drive 54 for driving the transmission member 53 along a working path (not numbered) extending in the direction of the first busbar 514 and the second busbar 523 to change the transmission ratio between the input shaft 52 and the output shaft 51.
The input shaft 52 inputs power through the conical entity 521 rotating along with the input shaft 52, the conical entity 521 can freely rotate, the conical cylinder 511 sleeved around the conical entity 521 can also freely rotate, the outer side surface of the conical cylinder 511, which is back to the conical entity 521, is used for outputting power to the outside of the continuously variable transmission through the auxiliary shaft 512, and the conical cylinder 511 faces the inner side surface of the conical entity 521, namely the first acting surface 513, and is used for receiving the power input by the conical entity 521. The conical orientation of conical entity 521 and conical barrel 511 are opposite, meaning that the end of conical barrel 511 with the smaller diameter is at the end of conical entity 521 with the larger diameter. The transmission member 53 is thus capable of achieving a continuously stepless transmission ratio change when transmitting the cone 511 and the cone entity 521.
Both cone drum 511 and cone body 521 are conical surfaces and thus have numerous generatrix lines, so that first generatrix 514 and second generatrix 523 do not refer to a particular generatrix, but one of the generatrix representing first active surface 513 is designated first generatrix 514, while second active surface 522 has one generatrix parallel to first generatrix 514, designated second generatrix 523. When the first busbar 514 and the second busbar 523 are parallel, a working path is formed between the first working surface 513 and the second working surface 522, the distance of which is constant, along which the transmission element 53 moves and remains in transmission connection with the first working surface 513 and the second working surface 522 at all times.
Therefore, the variable speed driving mechanism 54 can determine the transmission ratio only by limiting the position of the transmission member 53, the transmission member 53 is driven to change the position, the transmission ratio can be changed, and the speed of the change of the transmission member 53 can be accurately controlled. Meets the requirements of different designs of different products under different working conditions.
In one embodiment, the transmission member 53 is a rotor 531 frictionally transmitting with the first and second active surfaces 513, 522.
The design of the rotor 531 can ensure that the abrasion of the rotor 531, the first acting surface 513 and the second acting surface 522 is reduced in the transmission process, so that the service life of the whole continuously variable transmission is effectively prolonged.
In one embodiment, the rotor 531 is provided with two and frictionally engaged with each other, and the two rotors 531 frictionally engage the first and second active surfaces 513, 522, respectively.
The two rotors 531 cooperate with each other to increase the contact area of the transmission in a limited space, thereby increasing the life of the transmission 53. At the same time, the rotor 531 needs to change position between the first and second active surfaces 513, 522 to effect a change in the gear ratio, so that the rotor 531 is simultaneously subjected to forces between the first and second active surfaces 513, 522. The two rotors 531 provide better relief of forces between the first and second active surfaces 513, 522 than a single rotor 531, facilitating movement of the transmission 53 between the first and second active surfaces 513, 522. Providing a smoother shifting effect.
In one embodiment, the variable speed drive mechanism 54 includes:
a rotor case 541 for defining and guiding a position of the rotor 531 on the working path;
a driving belt 542 fixed to the rotor case 541 and for driving the rotor case 541 to change a position on the work path;
a guide lever 543 for guiding the rotor case 541 to move along the working path;
a drive source (not shown) may in practice be selected to drive a motor coupled to the turntable 544 for providing drive to the drive belt 542.
Because the rotor 531 needs to roll between the first active surface 513 and the second active surface 522 and to move on the working path, the spatial movement is complex and only accurate and stable spatial constraints can achieve good speed change effects. The rotor case 541 serves to restrict and guide the rotor 531 to roll between the first and second acting surfaces 513 and 522 while being able to drive the rotor 531 to move on the working path without affecting the rolling of the rotor 531. The guide lever 543 can ensure that the rotor 531 does not shift in the working path. The drive belt 542 can be designed in a manner similar to a timing belt in an engine in practical use, ensuring the accuracy of driving.
In one embodiment, the variable speed drive mechanism 54 includes a rigid guide rod 543 and a floating platform 545, the floating platform 545 including:
a rotor case 541 for defining and guiding a position of the rotor 531 on the working path and having a first slider 5411 and a second slider 5412 hinged at both ends thereof to be capable of freely swinging, the first slider 5411 being slidably engaged with the guide lever 543;
a floating frame 546 including a floating rod 5461 slidably engaged with the second slider 5412 and a driving belt 542 mounted on the floating rod 5461, the driving belt 542 for driving the second slider 5412 to move along the floating rod 5461;
a driving source for providing driving force to the driving belt 542.
The floating platform 545 is designed to overcome the problem that the first and second active surfaces 513, 522 apply a resistive force to the transmission member 53 when it is desired to change the position of the transmission member 53 during the transmission of the input shaft 52 and the output shaft 51 to each other. The two ends of the rotor box 541 are provided with swingable sliders, the first slider 5411 is sleeved on the guide rod 543, so that the rotor box 541 can slide and swing relative to the guide rod 543, the second slider is sleeved on the floating rod 5461, the floating rod 5461 and the guide rod 543 are horizontally arranged, and therefore, under the condition of a fixed transmission ratio, the rolling direction of the rotor 531 is kept vertical to the working path, and the rotor box 541 is parallel to the rolling direction of the rotor 531. When it is necessary to change the transmission ratio, the driving belt 542 pulls the second slider 5412 to move along the floating rod 5461, misalignment occurs between the first slider 5411 and the second slider 5412 due to the hinge, and the rotor case 541 is changed from a straight line into a zigzag-like shape, i.e., the rolling direction of the rotor 531 is no longer perpendicular to the working path, and at this time, since the total length of the rotor case 541 is not changed, the distance between the rigid guide rod 543 and the floating rod 5461 tends to be reduced, and the movement tendency is released by the movement of the floating rod 5461.
After the rolling direction of the rotor 531 is no longer perpendicular to the working path, the rolling of the rotor 531 generates a motion component on the working path, and the motion component not on the working path is released by the rolling of the rotor 531 itself due to the rigid guide lever 543. Thus, the rotor 531 is moved on the working path by the drive belt 542, changing the rotation speed ratio.
In addition to being able to smoothly change the position of the rotor 531 in the working path, the floating platform 545 has the important advantage of being able to precisely control the rate of displacement of the rotor 531 in the working path, i.e. the rate of change of the rotation ratio. The magnitude of the displacement or the force applied to the second slider 5412 by the driving belt 542 can be controlled to control the magnitude of the misalignment between the first slider 5411 and the second slider 5412, thereby controlling the included angle between the rolling direction of the rotor 531 and the working path, and further controlling the magnitude of the motion component generated by the rolling of the rotor 531 on the working path, and precisely controlling the displacement rate of the rotor 531 on the working path in cooperation with the motion of the driving belt 542.
In one embodiment, the rotor 531 is mounted on the rotor case 541 by a rotating shaft 5311, and the rotating shaft 5311 is disposed through a bar-shaped hole (not shown) in the rotor case 541, so that the two rotors 531 can be close to or far away from each other along the bar-shaped hole.
The two rotors 531 can appear wearing and tearing in the use, but the key parts of rotor 531 transmission in fact, the circumstances of transmission effect and even transmission inefficacy can appear probably to the rotor 531 after wearing and tearing, in order to prolong whole continuously variable transmission's life-span, is equipped with the bar hole that is used for the compensation on the rotor case 541, can adjust the interval between the rotor 531 to increase of service life.
In one embodiment, the continuously variable transmission further comprises a housing (not shown) on which the input shaft 52 is rotatably mounted, the conical body 521 being housed in the housing; the variable speed driving mechanism 54 is arranged around the conical entity 521, wherein the guide rod 543 is fixed with the box body, and the floating frame 546 is movably arranged on the box body; the cone 511 is rotatably mounted in the case and houses the cone 521 and the variable speed drive 54 through a hollow region inside, and the rotor 531 is located between and abuts the cone 521 and the cone 511.
In practical use, the cone 511 is assembled on the box through a large bearing, the cone 521 is rotatably mounted on the box through two ends, the cone 521 is spatially located in a central control area inside the cone 511, the floating frame 546 passes between the cone 511 and the cone 521, the core components such as the rotor box 541 need to be located between the cone 511 and the cone 521, and the mating components such as the guide rod 543 may extend outside the cone 511 and the cone 521 for fixing and arranging.
In one embodiment, the floating platform 545 is connected to the tank in the following manner:
the box body is provided with a directional elastic piece for installing the floating platform 545, and the directional elastic piece can be stressed and deformed in the floating direction of the floating platform 545 and keep rigidity in other directions;
or (b)
An electrical control mechanism for controlling the floating platform 545 is provided on the housing.
The direction of movement of the transmission member 53 refers to the rolling direction of the rotor 531. The floating platform 545 needs to precisely position the rotor 531 in the working path, so the floating platform 545 needs to remain rigid in the working path direction, while the floating platform 545 needs to release the deformation of the rotor case 541 and thus to be able to move a certain distance in the movement direction of the transmission member 53, so the directional elastic member can eliminate unnecessary or harmful movement of the floating platform 545 while satisfying the movement requirement of the floating platform 545. In a specific implementation, a sliding groove in the motion direction of the floating platform 545 can be selectively formed in the box, the fixed rotating shaft of the turntable 544 is slidably mounted in the sliding groove, and elastic pieces are arranged at two ends of the sliding groove in the sliding direction to fix the fixed rotating shaft, so that floating fixation is realized. The beneficial structure of this scheme is simple and stable.
Alternatively, the floating platform 545 may be fixed by means of electric control, such as fixing a rotating shaft of the turntable 544 on an electromagnetic push rod, and the position of the floating platform 545 may be automatically adjusted according to the requirement, which has the advantage of realizing accurate position adjustment.
In one embodiment, the transmission member 53 has a constant speed ratio state in which the direction of movement of the transmission member 53 is perpendicular to the plane in which the first busbar 514 and the second busbar 523 lie, and the driving belt 542 is used to drive the transmission member 53 out of the constant speed ratio state.
The constant ratio state is a state in which a gear ratio is determined when the moving direction of the rotor 531 is perpendicular to the plane in which the first bus bar 514 and the second bus bar 523 are located. When the driving belt 542 pulls the driving member 53 to move along the working path, the rolling direction of the rotor 531 forms an included angle with the working path, i.e. the state of exiting the constant speed ratio is exited, and the rolling of the rotor 531 generates a motion component on the working path, so as to perform a speed change action.
In one embodiment, floating platform 545 further includes a stop 5451 for limiting the travel of drive belt 542, stop 5451 being mounted on drive belt 542 and moving with drive belt 542, limiting block 5451 against floating frame 546 when drive belt 542 moves to a design maximum travel.
The transmission member 53 cannot exceed two ranges when moving on the first acting surface 513 and the second acting surface 522, so that a limiting member is required, and the first acting surface 513 and the second acting surface 522 are in a state of rotating at a high speed, and a limiting structure is arranged on the first acting surface 513 and the second acting surface 522, so that a series of severe conditions such as dynamic balance and the like are required to be met, and the production and manufacturing costs of products are not reduced. The stopper 5451 is thus provided on the drive belt 542 for abutting against the floating frame 546. In a practical option, the driving belt 542 may be selected to be a rotary design on the floating frame 546, one side of the rotary is used for driving the rotor box 541, and the other side is used for mounting the limiting blocks 5451, and when the rotor box 541 moves to both ends, the limiting blocks 5451 correspondingly move to the other both ends, thereby realizing the limiting function.
During the use process:
when the fixed speed ratio is operated, the rolling direction of the rotor 531 is maintained perpendicular to the working path, and the rotor case 541 is parallel to the rolling direction of the rotor 531. At this time, the input shaft 52 drives the rotor 531 to drive the cone 511 to output power through the cone 521.
When it is necessary to change the transmission ratio, the driving belt 542 pulls the second slider 5412 of the rotor case 541 to move along the floating lever 5461, and the first slider 5411 positioned on the guide lever 543 and the second slider 5412 are dislocated due to the hinge, and at this time, the rotor case 541 becomes a zigzag-like shape from a straight line, i.e., the rolling direction of the rotor 531 is no longer maintained perpendicular to the working path, and at this time, because the total length of the rotor case 541 is not changed, the distance between the rigid guide lever 543 and the floating lever 5461 tends to be reduced, and the movement tendency is released by the movement of the floating lever 5461, i.e., the overall movement of the floating frame 546.
After the rolling direction of the rotor 531 is no longer perpendicular to the working path, the rolling of the rotor 531 generates a motion component on the working path, and the motion component not on the working path is released by the rolling of the rotor 531 itself due to the rigid guide lever 543. Thus, the rotor 531 is moved on the working path by the drive belt 542, changing the rotation speed ratio.
The technical features of the above embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.
The above examples illustrate only a few embodiments of the invention, which are described in detail and are not to be construed as limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.

Claims (9)

1. A continuously variable transmission, characterized by comprising:
the output shaft comprises a conical cylinder with a hollow inside, the outer side surface of the conical cylinder is used for outputting driving force, and the inner side surface of the conical cylinder is a first acting surface;
the input shaft comprises a conical entity arranged in the conical cylinder, the conical surface of the conical entity is a second action surface, the conical direction of the second action surface is opposite to the conical direction of the first action surface, and a first generatrix of the first action surface is parallel to a second generatrix of the second action surface;
the transmission piece is a rotor, is positioned in the radial direction of the axis of the input shaft and is in transmission connection between the first acting surface and the second acting surface;
a variable speed drive mechanism for driving the transmission member to move along a working path to vary a transmission ratio between the input shaft and the output shaft, the working path extending in the directions of the first and second bus bars; the variable speed drive mechanism includes a rigid guide bar and a floating platform comprising:
the rotor box is used for limiting and guiding the position of the rotor on the working path, and a first sliding block and a second sliding block which can swing freely are hinged at two ends of the rotor box, and the first sliding block is in sliding fit with the guide rod;
the floating frame comprises a floating rod in sliding fit with the second sliding block and a driving belt arranged on the floating rod, the driving belt is used for driving the second sliding block to move along the floating rod, and the driving belt can realize dislocation between the first sliding block and the second sliding block so as to control the rotor to move on a working path.
2. The continuously variable transmission of claim 1, wherein the transmission member is a rotor frictionally transmitting with the first and second apply surfaces.
3. The continuously variable transmission according to claim 2, wherein said rotors are provided with two and mutually frictionally driven, and wherein said two rotors are frictionally driven with said first and second active surfaces, respectively.
4. The continuously variable transmission of claim 1, wherein the variable transmission drive mechanism further comprises a drive source for providing a drive force to the drive belt.
5. The stepless speed change device according to claim 1, wherein the rotor is mounted on the rotor box through a rotating shaft, the rotating shaft penetrates through a strip-shaped hole in the rotor box, and the two rotors can be close to or far away from each other along the strip-shaped hole.
6. The variable transmission device of claim 1, further comprising a housing, the input shaft rotatably mounted to the housing, the conical body received in the housing; the variable speed driving mechanism is arranged around the conical entity, the guide rod is fixed with the box body, and the floating frame is movably arranged on the box body; the conical cylinder is rotatably arranged in the box body, the conical entity and the variable speed driving mechanism are accommodated in the hollow area inside the box body, and the rotor is positioned between the conical entity and the conical cylinder and props against the conical entity and the conical cylinder.
7. The infinitely variable transmission of claim 6, wherein the floating platform is connected to the housing in the following manner:
the box body is provided with a directional elastic piece for installing the floating platform, and the directional elastic piece can be stressed and deformed in the floating direction of the floating platform and keep rigidity in other directions;
or (b)
The box body is provided with an electric control mechanism for controlling the floating platform.
8. The continuously variable transmission of claim 1, wherein the transmission member has a constant speed ratio state in which a direction of movement of the transmission member is perpendicular to a plane in which the first and second bus bars lie, and the drive belt is configured to drive the transmission member out of the constant speed ratio state.
9. The infinitely variable transmission of claim 1, wherein the floating platform further comprises a stop block for limiting the travel of the drive belt, the stop block being mounted on and moving with the drive belt, the stop block abutting the floating frame when the drive belt moves to a designed maximum travel.
CN201910249533.6A 2019-03-29 2019-03-29 Stepless speed change device Active CN110043623B (en)

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191207878A (en) * 1912-04-01 1913-03-06 Charles Bertram Liddell Improvements in Transmission Gear for Motor Cars and the like.
DE10227949A1 (en) * 2002-06-18 2004-04-15 Stefan Matuzic Infinite three-wheeled friction gearing has inner cone and funnel-shaped cone body and one piece gearing system held by hydraulic contact pressure with cone wheels transferring rotary movement
JP2006112511A (en) * 2004-10-14 2006-04-27 Nissan Motor Co Ltd Stepless speed change device
CN1862056A (en) * 2005-05-09 2006-11-15 范泽林 Automatic gear for automobile
DE102013020451B3 (en) * 2013-12-06 2015-04-16 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Infinitely variable transmission
CN105889439A (en) * 2016-06-23 2016-08-24 郭嘉辉 Conical disc type continuously variable transmission
CN205715507U (en) * 2016-06-23 2016-11-23 郭嘉辉 A kind of cone disk type buncher
CN209943451U (en) * 2019-03-29 2020-01-14 杭州莱本科技有限公司 Stepless speed change device

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191207878A (en) * 1912-04-01 1913-03-06 Charles Bertram Liddell Improvements in Transmission Gear for Motor Cars and the like.
DE10227949A1 (en) * 2002-06-18 2004-04-15 Stefan Matuzic Infinite three-wheeled friction gearing has inner cone and funnel-shaped cone body and one piece gearing system held by hydraulic contact pressure with cone wheels transferring rotary movement
JP2006112511A (en) * 2004-10-14 2006-04-27 Nissan Motor Co Ltd Stepless speed change device
CN1862056A (en) * 2005-05-09 2006-11-15 范泽林 Automatic gear for automobile
DE102013020451B3 (en) * 2013-12-06 2015-04-16 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Infinitely variable transmission
CN105889439A (en) * 2016-06-23 2016-08-24 郭嘉辉 Conical disc type continuously variable transmission
CN205715507U (en) * 2016-06-23 2016-11-23 郭嘉辉 A kind of cone disk type buncher
CN209943451U (en) * 2019-03-29 2020-01-14 杭州莱本科技有限公司 Stepless speed change device

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