Continuously variable transmission device with speed regulating centrifugal force not acting on cone disk

Abstract

The present invention belongs to the technical field of transmission, and relates to a continuously variable transmission transmission device in which the speed regulating centrifugal force does not act on a cone disc, comprising a one-shaft cone disc unit, a two-shaft cone disc unit and an annular transmission member, and also comprising a thrust unit and a centrifugal speed regulating unit; the centrifugal speed regulating unit comprises a dynamic centrifugal disc, a fixed centrifugal disc, a centrifugal body and a first elastic component of a shaft, the dynamic centrifugal disc is butted against the one-shaft dynamic cone disc, the first elastic component of the one shaft presses against the end face of the dynamic centrifugal disc, and provides a thrust to the dynamic centrifugal disc in the direction of the one-shaft dynamic cone disc; the two end faces of the fixed centrifugal disc and the dynamic centrifugal disc are coaxially arranged opposite to each other, and at least one end face is provided with a centrifugal ramp groove; the centrifugal body is clamped in the centrifugal ramp groove, and under the action of the rotating centrifugal force, the centrifugal body climbs along the centrifugal ramp groove and compresses the one-shaft first elastic component and pushes the dynamic centrifugal disc to make an axial movement away from the fixed centrifugal disc, and at the same time provides an axial movement space for the one-shaft dynamic cone disc to move synchronously and in the same direction as the dynamic centrifugal disc.

Description

Technical Field

[0001] The invention belongs to the technical field of transmission, and relates to a continuously variable transmission device in which the speed regulating centrifugal force does not act on a cone disk. Background Art

[0002] The cone-disc type continuously variable transmission transmits power by establishing rolling friction through the conical surfaces of two pairs of cone disks clamping annular transmission parts (metal belts, rubber belts, etc.), and achieves speed regulation by changing the rolling radius of the annular transmission parts on the cone disks. Its two most core structures are the speed regulation system for adjusting the transmission ratio (referred to as "speed regulation") and the thrust system for providing the clamping force for transmitting torque (referred to as "clamping force").

[0003] The speed control systems of the common cone-disc continuously variable transmissions today are divided into three categories: the first category achieves speed control by establishing thrust through hydraulics; the second category achieves speed control by establishing thrust through centrifugal force; and the third category achieves speed control by controlling a mechanical transmission device through an electric motor.

[0004] The hydraulic speed control solution is currently mainly used in the field of fuel passenger cars with small and medium torque. The torque capacity is generally in the range of 100Nm to 200Nm. Its disadvantages are:

[0005] 1. The hydraulic system has high manufacturing process requirements and the electronic control system is complex, resulting in high cost and low reliability of the hydraulic speed control solution;

[0006] 2. When transmitting large torque speed regulation, high speed regulation power is required (such as overtaking, accelerating and downshifting conditions). The configuration of a high-power hydraulic pump reduces the mechanical transmission efficiency, that is, the hydraulic speed regulation solution is not suitable for vehicle machinery fields with a large torque transmission range (such as heavy-duty trucks, medium and large agricultural tractors, some wind turbines, etc.).

[0007] The centrifugal speed control solution is mainly used in small power vehicle fields such as scooters and beach cars. The torque capacity of the power source is generally within 50Nm. Its main disadvantages are:

[0008] 1. The centrifugal speed regulating thrust acts on the cone disc and the annular transmission parts, resulting in excessive clamping force and a short service life, which is especially unsuitable for use in the field of medium and large vehicle machinery;

[0009] 2. Centrifugal speed regulating force will cause excess clamping force required to transmit torque, resulting in low mechanical efficiency.

[0010] The invention patent with publication number CN103867678A proposes a structure for speed regulation by controlling the mechanical structure through a motor. The mechanical system in this speed regulation scheme needs to set two bearings on the active cone disc and the passive cone disc to isolate the speed. The speed reduction motor drives the speed regulation mechanical system to achieve synchronous and unidirectional movement of the active and passive cone discs to complete the speed regulation. The disadvantages of this scheme are as follows:

[0011] 1. Actively controlled reduction motors require electronic control software and hardware to achieve speed regulation, which increases the complexity of the system, resulting in high costs and reduced reliability;

[0012] 2. The four bearings of the speed regulating mechanical system that bear high speed and high thrust reduce the mechanical transmission efficiency;

[0013] 3. For cone-disc continuously variable transmissions used in medium and large vehicles (such as those with a power source torque of 400Nm), the maximum speed regulation thrust will exceed 10 tons, and at the same time, it will withstand a speed of more than 8000rpm. The physical limits of the thrust bearing cannot effectively adapt to the working conditions, and limit the application field or service life of the speed regulation solution.

[0014] There are significant differences in the torque characteristics and energy consumption characteristics of internal combustion engines and electric motors:

[0015] 1. The motor can output a constant maximum torque from 0rpm to the rated speed, while the internal combustion engine can usually operate stably at 800rpm (gasoline engine), and its output torque characteristics show a parabolic trend;

[0016] 2. The motor can output power at a constant power within the range of rated speed to 2 times the rated speed. When the maximum speed of the motor exceeds 2 times the rated speed, the energy efficiency will be reduced, and the cost of the mechanical system and the electronic control system will increase. The speed and power output characteristics of the internal combustion engine are monotonically increasing, and the peak power speed of the internal combustion engine is usually equal to the maximum speed of the engine.

[0017] 3. The speed in the high-efficiency energy consumption zone of the motor is usually between the rated speed and 2 times the rated speed, and the corresponding high-efficiency torque range is usually between 10% load rate and 90% load rate. The high-efficiency energy consumption speed zone of the internal combustion engine is usually between 30% maximum speed and 40% maximum speed, and the corresponding torque energy consumption high-efficiency zone is between 50% maximum torque and 70% maximum torque.

[0018] Due to the significant differences in the power and energy consumption characteristics of vehicle-mounted motors and internal combustion engines, the requirements for the adapted transmission and its speed regulation strategy are also significantly different as follows:

[0019] 1. The requirement of the motor drive for the transmission is to make the heavy load and maximum speed of the vehicle as much as possible within the range of rated speed to 2 times the rated speed, that is, the motor speed of the vehicle equipped with the motor drive is less than the rated speed to 2 times the rated speed, and the maximum speed ratio is maintained to meet the maximum wheel torque output under the vehicle load. When the rated speed is exceeded or 2 times the rated speed, the speed ratio is reduced to maintain the motor speed within the range of rated speed to 2 times the rated speed, ensuring that the available backup power of the motor meets the vehicle use requirements;

[0020] 2. The requirements of the transmission for internal combustion engine drive are that the speed ratio of the vehicle under heavy load conditions should be kept at the maximum; the speed ratio of the vehicle under uniform speed conditions should be adjusted to maintain the energy-efficient zone to ensure vehicle driving; the speed ratio should be adjusted to a high speed to maintain stable engine operation; the speed ratio should be adjusted to a high speed to increase the speed of the internal combustion engine to provide the power required for acceleration; the speed ratio should be adjusted to the speed at which the engine can output maximum power under the vehicle's highest speed conditions;

[0021] The electrification or hybrid configuration of vehicle power units is a development trend. Compared with internal combustion engines, electric motors have excellent low-speed torque performance, high energy conversion efficiency, and fast power output response; electric drive configuration transmission can solve the contradiction between heavy load, higher speed and cost of vehicles; in summary, the market urgently needs a low-cost transmission that can be adapted to both internal combustion engine drive and electric drive to meet the development needs of the vehicle industry. Summary of the invention

[0022] In view of this, the purpose of the present invention is to provide a continuously variable transmission device in which the centrifugal force for speed regulation does not act on the cone disc, so as to solve the problems of short life, low mechanical transmission efficiency and unsuitability for medium and large vehicle machinery due to excessive clamping force in the existing centrifugal speed regulation scheme, and high cost and poor adaptability to the extreme performance of the thrust bearing in the electromechanical speed regulation scheme; and without the need to set up an active speed regulation system, by setting the elastic coefficient of the elastic component to adapt to the application requirements of electric drive and internal combustion engine driven vehicle machinery, it brings the advantages of long life, low cost, high transmission efficiency, simple and reliable structure, thereby significantly improving the application prospects of the cone disc type continuously variable transmission in the era of vehicle electrification.

[0023] In order to achieve the above object, the present invention provides the following technical solutions:

[0024] The transmission device of a continuously variable transmission in which the centrifugal force for speed regulation does not act on a cone disc comprises a one-shaft cone disc unit, a two-shaft cone disc unit and an annular transmission member for transmitting power between the one-shaft cone disc unit and the two-shaft cone disc unit, the one-shaft cone disc unit comprises a one-shaft fixed cone disc and a one-shaft movable cone disc arranged relatively to one shaft and a cone surface, the one-shaft fixed cone disc is sleeved and fixedly connected to the one shaft, and the one-shaft movable cone disc is sleeved and connected to the one shaft in an axially movable but circumferentially fixed manner; the two-shaft cone disc unit comprises two-shaft fixed cone discs and two-shaft movable cone discs arranged relatively to one shaft and a cone surface; the one shaft or the two shafts are connected to the output shaft of a power source, the power source comprises an internal combustion engine and an electric motor, and is used to provide driving force to a vehicle mechanical device; it is characterized in that it also comprises a thrust unit arranged at a non-conical surface end of the two-shaft movable cone disc, which transmits power to the annular transmission member and provides a clamping force, and a centrifugal speed regulation unit arranged on one shaft;

[0025] The centrifugal speed regulating unit comprises a dynamic centrifugal disc, a fixed centrifugal disc, a centrifugal body and a first elastic component of a shaft, wherein the dynamic centrifugal disc is abutted against a dynamic conical disc of a shaft, and the first elastic component of a shaft abuts against an end surface of the dynamic centrifugal disc and provides a thrust to the dynamic centrifugal disc in a direction toward the dynamic conical disc of the shaft;

[0026] The fixed centrifugal disc and the dynamic centrifugal disc are coaxially arranged opposite to each other, and at least one of the two oppositely arranged end faces is provided with a centrifugal slope groove, wherein the one provided on the end face of the fixed centrifugal disc is a fixed centrifugal slope groove, and the one provided on the dynamic centrifugal end face is a dynamic centrifugal slope groove;

[0027] The centrifugal body is clamped in the centrifugal ramp groove. Under the action of the rotating centrifugal force, the centrifugal body climbs along the centrifugal ramp groove and compresses the first elastic component of the one-axis and pushes the dynamic centrifugal disk to move axially away from the fixed centrifugal disk, while providing an axial movement space for the one-axis dynamic cone disk to move synchronously and in the same direction as the dynamic centrifugal disk.

[0028] Furthermore, the axially opposite end surfaces of the fixed centrifugal disc and the dynamic centrifugal disc are respectively provided with a fixed centrifugal slope groove and a dynamic centrifugal slope groove;

[0029] The fixed centrifugal ramp groove and the dynamic centrifugal ramp groove are radially inclined rolling tracks from low to high, and at least two groups of dynamic centrifugal ramp grooves and fixed centrifugal ramp grooves clamping the centrifugal body are evenly distributed along the circumferential direction of the fixed centrifugal disc.

[0030] Furthermore, when the two shafts are connected to a power source and serve as driving shafts, the fixed centrifugal disc is fixedly sleeved on one shaft and arranged on the non-conical side of the dynamic conical disc of the one shaft, and the dynamic centrifugal disc is sleeved on one shaft in an axially movable and circumferentially fixed manner and arranged on the side of the fixed centrifugal disc that is circularly away from the dynamic conical disc of the one shaft;

[0031] The fixed centrifugal disc is provided with a through hole, so that the non-conical end of the one-shaft dynamic conical disc and the end surface of the dynamic centrifugal disc are abutted and connected through a speed regulating push rod passing through the through hole on the fixed centrifugal disc;

[0032] In the installed state, the annular transmission member is at the maximum working radius of the shaft cone disk unit, and in the process of transmitting torque, the axial thrust generated by the thrust unit acting on the shaft dynamic cone disk through the annular transmission member is smaller than the elastic force of the first elastic component of the shaft.

[0033] Furthermore, when the one shaft is connected to a power source and serves as a driving shaft, the centrifugal speed regulating unit further comprises a second elastic component of the one shaft;

[0034] One end of the second elastic component of the first shaft is fixedly connected to the first shaft sleeve, and the other end is pressed against the non-conical end of the movable cone disk of the first shaft.

[0035] and provide a thrust to the movable cone disk of one shaft toward the fixed cone disk of one shaft; the second elastic component of one shaft is provided with at least two groups of elastic members with different elastic coefficients, and each elastic coefficient of the second elastic component of one shaft is smaller than the elastic coefficient of the first elastic component of one shaft; the movable centrifugal disk is sleeve-connected with one shaft in an axially movable and circumferentially fixed manner, and is arranged on one side of the non-conical surface side of the fixed cone disk of one shaft, the fixed centrifugal disk is fixedly connected with the non-conical surface end of the fixed cone disk of one shaft or manufactured in one piece, and is arranged on one side of the movable centrifugal disk close to the fixed cone disk of the second shaft;

[0036] The fixed conical disc and the fixed centrifugal disc of the one shaft are provided with through holes, and the dynamic centrifugal disc abuts against the dynamic conical disc of the one shaft via a speed regulating push rod passing through the through holes;

[0037] In the installed state, the first elastic component of the first shaft compresses the second elastic component of the first shaft through the speed regulating push rod, and satisfies that the annular transmission member is at the minimum working radius in the cone disk unit of the first shaft.

[0038] Furthermore, the two-shaft fixed cone disks are sleeved on the two shafts in a manner of circumferential rotation and axial fixation, and the two-shaft movable cone disks are sleeved on the two-shaft fixed cone disks in an axially slidable and circumferentially fixed manner;

[0039] The thrust unit comprises a main thrust disc, a thrust rolling body and a first elastic component of the two shafts. The main thrust disc is sleeve-connected with the two shafts in an axially movable and circumferentially fixed manner and is arranged on one side of the non-conical surface end of the movable cone disc of the two shafts.

[0040] The first elastic component of the second shaft is sleeved on the second shaft and arranged on a side of the main thrust plate away from the movable cone plate of the second shaft, so as to provide the main thrust plate with an axial thrust in the direction of the movable cone plate of the second shaft, and an end surface of the main thrust plate on a side away from the movable cone plate of the second shaft abuts against a fourth support seat fixedly connected to the second shaft;

[0041] The main thrust ramp groove and the secondary thrust ramp groove are respectively provided on the opposite end surfaces of the non-conical surface side of the main thrust disc and the second-axis dynamic cone disc in the circumferential direction, and the thrust rolling body is clamped between the main thrust ramp groove and the secondary thrust ramp groove. Both the secondary thrust ramp groove and the main thrust ramp groove are V-shaped slope grooves that rise symmetrically from the low point to both ends, and the secondary thrust ramp groove and the main thrust ramp groove are arranged symmetrically with the clamped thrust rolling body as the center;

[0042] The torque transmitted by the main thrust disc and the two-axis movable cone disc can generate an axial thrust on the two-axis movable cone disc and form the clamping force required for the annular transmission member to transmit the torque, and the axial stroke generated by the mutual rotation between the main thrust disc and the two-axis movable cone disc matches the axial stroke required for the speed regulation of the two-axis movable cone disc.

[0043] Furthermore, it also includes a torsion unit arranged on the two shafts, the torsion unit includes a main torsion plate, a torsion rolling body and a second elastic component of the two shafts;

[0044] The main torque disc is sleeved on the two shafts in a manner that it can move relatively axially but is fixed circumferentially and is arranged on one side of the non-conical surface end of the movable cone disc of the two shafts, and the main torque ramp groove and the auxiliary torque ramp groove are respectively provided on the opposite end surfaces of the non-conical surface side of the main torque disc and the movable cone disc of the two shafts in the circumferential direction, and the torsion rolling body is clamped between the main torque ramp groove and the auxiliary torque ramp groove, and the main torque ramp groove and the auxiliary torque ramp groove are both unidirectional ramp grooves that rise from one end to the other end, and are arranged symmetrically with the center to clamp the torsion rolling body, and the second elastic component of the two shafts is pressed against the end surface of the main torque disc away from the main ramp groove and provides a thrust in the direction of the movable cone disc of the two shafts, so as to realize that the torque unit generates a torque that drives the power source to rotate in the forward direction.

[0045] Furthermore, the torsion unit is provided with at least two groups of auxiliary torsion ramp grooves and main torsion ramp grooves for clamping the torsion rolling body, and the thrust unit is provided with at least two groups of auxiliary thrust ramp grooves and main thrust ramp grooves for clamping the thrust rolling body.

[0046] Furthermore, when the one shaft is connected to a power source and serves as a driving shaft, in the installed state, the thrust rolling body is arranged at the highest point in the main thrust ramp groove, the torsion rolling body is arranged at the middle position of the main torsion ramp groove, and the annular transmission member is located at the minimum working radius in the one shaft cone disk unit.

[0047] Furthermore, when the two shafts are connected to a power source and serve as driving shafts, in the installed state, the thrust rolling body is arranged at the lowest point in the main thrust ramp groove, the torsion rolling body is arranged at the middle position of the main torsion ramp groove, and the annular transmission member is located at the maximum working radius in a single-axis cone disk unit.

[0048] Furthermore, the angle of the secondary thrust ramp groove, the angle of the primary thrust ramp groove, the raceway length of the secondary thrust ramp groove, the raceway length of the primary thrust ramp groove, the diameter of the thrust rolling element, and the diameters of the torsion rolling element and the centrifugal element satisfy the following relationship:

[0049]

[0050] L≥2*(R max -R min )*tan a1 / 0.9 / sin a2

[0051] d≥(R max -R min )*tan a1*2 / 0.9

[0052] In the above formula, i is the transmission speed ratio; R1 is the rolling working radius of the annular transmission part on the first axis; R2 is the rolling working radius of the annular transmission part on the second axis; a1 is the cone angle of the cone disk; μ is the friction coefficient between the annular transmission part and the cone disk; σ is the thrust ratio required for the first axis and the second axis to transmit torque. The σ value is monotonically negatively correlated with the transmission speed ratio i. Through experiments, it is found that: σ=0.266*i^ 2 -1.02*i+2.02;R t is the rotation radius of the thrust rolling body around the two axes; a2 is the continuously changing angle of the secondary thrust ramp groove and the main thrust ramp groove; η is the efficiency of the thrust provided by the thrust unit being transmitted to one axis through the annular transmission member; L is the raceway length of the main thrust ramp groove and the secondary thrust ramp groove; R max is the maximum rolling radius of the annular transmission part, R min is the minimum rolling radius of the annular transmission part; d is the diameter of the thrust rolling body, torsion rolling body and centrifugal body.

[0053] The beneficial effects of the present invention are:

[0054] 1. The core idea of ​​the present invention is to provide the axial space required for the speed regulation of the first axis movable cone disc by compressing the axial movement displacement brought by the first elastic component of the first axis through the thrust generated by the centrifugal force, and to provide the clamping force required for the transmission torque through the thrust unit arranged on the side of the second axis movable cone disc, so as to realize the separation of the action paths of the speed regulation force and the clamping force, and significantly improve the adaptability of the scheme;

[0055] 2. By setting multiple groups of different elastic coefficients for the first elastic component of one shaft and the second elastic component of one shaft to adapt to the specific speed regulation strategy requirements, the cone-disc continuously variable transmission meets the application requirements of the vehicle machinery field equipped with internal combustion engine drive or motor drive through a simple mechanical structure. For example, when matched with the internal combustion engine power source, the thrust unit will compress the elastic part with the smallest elastic coefficient of the second elastic component of one shaft to increase the transmission speed ratio to increase the power required for rapid acceleration;

[0056] 3. The centrifugal force of speed regulation does not act between the cone surface of the cone disk and the annular transmission part, which solves the problem of low service life caused by excessive clamping force; it creates conditions for the application of centrifugal speed regulation schemes in medium and large power vehicles;

[0057] 4. The present invention does not need to set up an electronically controlled speed regulating system or a thrust bearing with poor adaptability (high speed, large thrust), which significantly reduces costs, improves reliability and improves mechanical transmission efficiency;

[0058] 5. The speed regulating centrifugal force does not act between the conical surface of the cone disk and the annular transmission member, thereby avoiding excessive clamping force leading to a decrease in mechanical efficiency. At the same time, the present invention solves the problem of impact of the thrust unit and the inability to reversely transmit power by setting a torque unit, further improving the mechanical transmission efficiency and practicability of the present invention;

[0059] 6. The function of the torque unit is to drive the power source to rotate in the forward direction until the mechanical clearance caused by wear, inelastic elongation and assembly of the annular transmission parts is eliminated, thereby avoiding oscillation shock when transmitting power.

[0060] Other advantages, objectives and features of the present invention will be described in the following description to some extent, and to some extent, will be obvious to those skilled in the art based on the following examination and study, or can be taught from the practice of the present invention. The objectives and other advantages of the present invention can be realized and obtained through the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0061] In order to make the purpose, technical solutions and advantages of the present invention more clear, the present invention will be described in detail below in conjunction with the accompanying drawings, wherein:

[0062] Figure 1 It is a structural schematic diagram of a continuously variable transmission device in Example 1 in which the speed regulating centrifugal force does not act on the cone disk;

[0063] Figure 2 for Figure 1 The right view of the moving cone disc, auxiliary thrust ramp groove and auxiliary torque ramp groove of the middle second shaft;

[0064] Figure 3 for Figure 1 Schematic diagram of the structure of the middle main thrust plate and the main thrust ramp groove;

[0065] Figure 4 for Figure 1 A schematic diagram of the structure of the middle main torque disc and its main torque ramp groove;

[0066] Figure 5 for Figure 1 Schematic diagram of the structure of the central fixed centrifugal disc and the fixed centrifugal ramp groove;

[0067] Figure 6 for Figure 1 Schematic diagram of the structure of the dynamic centrifugal disc and the dynamic centrifugal ramp groove;

[0068] Figure 7 It is a structural schematic diagram of a continuously variable transmission device in Example 2 in which the speed regulating centrifugal force does not act on the cone disk;

[0069] Figure 8A structural diagram showing that the fixed centrifugal disc is not provided with a centrifugal slope groove, while the moving centrifugal disc is provided with a centrifugal slope groove;

[0070] Fig. 9 A structural diagram showing that the fixed centrifugal disc is provided with a centrifugal slope groove, while the dynamic centrifugal disc is not provided with a centrifugal slope groove;

[0071] Fig.10 It is a schematic diagram of a state in which a mechanical gap exists between the main thrust ramp groove and the auxiliary thrust ramp groove due to wear, inelastic deformation or assembly reasons of the annular transmission part;

[0072] Fig.11 It is a schematic diagram of the state in which the torque unit drives the power source to rotate forward until the mechanical clearance is eliminated;

[0073] Fig.12 This is a schematic diagram of the positions of the thrust rolling body, the torsion rolling body and the centrifugal block in the installation state of Example 2, where the torsion unit eliminates the mechanical clearance by driving the power source to rotate;

[0074] Fig.13 A schematic diagram of the positions of the thrust rolling element, the torsion rolling element and the centrifugal block in the corresponding ramp groove when the transmission speed ratio is the minimum in Example 2;

[0075] Fig.14 Schematic diagram of the positions of the thrust rolling body, the torsion rolling body and the centrifugal block in the corresponding ramp grooves under the instantaneous working condition of the vehicle's braking energy recovery and reverse power transmission in Example 2;

[0076] Fig.15 A schematic structural diagram of a continuously variable transmission device in Example 3 in which the speed regulating centrifugal force does not act on the cone disk.

[0077] Figure numerals: a shaft 1, a first support seat 2, a first elastic component of a shaft 3, a dynamic centrifugal disc 4, a dynamic centrifugal ramp groove 4-1, a radial limiter 5, a centrifugal block 6, a fixed centrifugal disc 7, a fixed centrifugal ramp groove 7-1, a fixed cone disc of a shaft 8, an annular transmission member 9, a speed regulating push rod 10, a dynamic cone disc of a shaft 11, a power positive rotation direction 12, a second elastic component of a shaft 13, a second support seat 14, a second shaft 15, a third support seat 16, a thrust bearing 17, a second Axis fixed cone disk 18, second axis movable cone disk 19, secondary thrust ramp groove 22-2, secondary torsion ramp groove 24-2, torsion rolling body 20, thrust rolling body 21, main thrust disk 22, main thrust ramp groove 22-1, fourth support seat 23, main torsion disk 24, main torsion ramp groove 24-1, second axis first elastic component 25, second axis second elastic component 26, fifth support seat 27, thrust elastic component 28, sixth support seat 29, mechanical clearance 30. DETAILED DESCRIPTION

[0078] The following describes the embodiments of the present invention by specific examples, and those skilled in the art can easily understand other advantages and effects of the present invention from the contents disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed in various ways based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the illustrations provided in the following embodiments only illustrate the basic concept of the present invention in a schematic manner, and the following embodiments and features in the embodiments can be combined with each other without conflict.

[0079] Among them, the drawings are only used for illustrative explanations, and they only represent schematic diagrams rather than actual pictures, and should not be understood as limitations on the present invention. In order to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of actual products. For those skilled in the art, it is understandable that some well-known structures and their descriptions in the drawings may be omitted.

[0080] The same or similar numbers in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if the terms "upper", "lower", "left", "right", "front", "rear", etc. indicate the orientation or position relationship, they are based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation. Therefore, the terms describing the position relationship in the drawings are only used for illustrative purposes and cannot be understood as limiting the present invention. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0081] Example 1

[0082] like Figure 1 As shown, a continuously variable speed change device in which the centrifugal force for speed regulation does not act on the cone disk is disclosed, comprising a first-shaft cone disk unit, a second-shaft cone disk unit, a thrust unit, a torque unit, and an annular transmission member 9 for transmitting power between the first-shaft cone disk unit and the second-shaft cone disk unit and a centrifugal speed regulation unit; in this embodiment, the first shaft 1 is used as a driving shaft for inputting a power source, and the second shaft 15 is used as a driven shaft;

[0083] The one-shaft cone-disk unit comprises an axis 1 and an axis fixed cone disk 8 and an axis movable cone disk 11 arranged with coaxial cone surfaces opposite to each other; the one-shaft fixed cone disk 8 is sleeve-fixedly connected to the one-shaft 1, and the one-shaft movable cone disk 11 is sleeve-fixedly connected to the one-shaft 1 so as to be axially relatively movable and circumferentially fixed;

[0084] Further, the centrifugal speed regulating unit includes a dynamic centrifugal disc 4, a centrifugal block 6, a first elastic component 3 of a shaft, a second elastic component 13 of a shaft, and a fixed centrifugal disc 7 provided at a non-conical end of a fixed cone disc of a shaft, and the fixed centrifugal disc 7 and the fixed cone disc 8 of a shaft are integrally formed and manufactured; the dynamic centrifugal disc 4 is sleeved on a shaft 1 in a manner that it can move axially relative to each other but is fixed circumferentially; the dynamic centrifugal disc 4 and the fixed centrifugal disc 7 have opposite end surfaces provided with a dynamic centrifugal slope groove 4-1 and a fixed centrifugal slope groove 7-1, respectively; as an alternative, the end surface of the dynamic centrifugal disc 4 is provided with a fixed centrifugal slope groove 4-1, and the fixed centrifugal disc 7 is not provided with a fixed centrifugal slope groove 7-1 (such as Figure 8 As shown), or the end surface of the moving centrifugal disc 4 is not provided with a fixed centrifugal slope groove 4-1, and a fixed centrifugal slope groove 7-1 is provided on the fixed centrifugal disc 7 (as shown Fig. 9 As shown); the dynamic centrifugal ramp groove 4-1 and the fixed centrifugal ramp groove 7-1 are radially inclined ramp raceways from low to high; in the installed state, the centrifugal block 6 is clamped at the lowest point of the raceways of the dynamic centrifugal ramp groove 4-1 and the fixed centrifugal ramp groove 7-1; the first elastic component 3 of the one shaft is sleeved on the one shaft 1, and one end is pressed and connected with the dynamic centrifugal disc 4, and the other end is pressed on the first support seat 2 fixedly connected to the one shaft 1; the second elastic component 13 of the one shaft is sleeved on the one shaft 1, and two groups of elastic parts with different elastic coefficients are provided, one end of the second elastic component 13 of the one shaft is pressed against the non-conical end of the dynamic cone disc 11 of the one shaft, and provides thrust to the dynamic cone disc 11 of the one shaft, and the other end is axially fixed by the second support seat 14 sleeved and fixedly connected to the one shaft 1;

[0085] Furthermore, three through holes are provided near the sleeve portion of the fixed cone disc 8 of one shaft, and the speed regulating push rod 10 passes through the through holes to abut and connect the dynamic centrifugal disc 4 with the dynamic cone disc 11 of one shaft, and groove-shaped radial limiting portions 5 are provided at the abutting positions to limit the radial position of the speed regulating push rod 10;

[0086] Furthermore, the centrifugal speed regulating unit is provided with 6 groups of dynamic centrifugal ramp grooves 4-1 and fixed centrifugal ramp grooves 7-1 clamping the centrifugal block 6; in the installed state, the first elastic component 3 of one shaft limits the axial position of the dynamic cone disk 11 of one shaft through the speed regulating push rod 10, so that the annular transmission member 9 is at the minimum working radius of the cone disk unit of one shaft;

[0087] Further, the other end of the annular transmission member 9 is clamped between the conical surfaces of the two-shaft cone disk unit. The two-shaft cone disk unit includes two shafts 15, two-shaft fixed cone disks 18 and two-shaft movable cone disks 19. The two-shaft fixed cone disk 18 includes a sleeve manufactured integrally with the cone disk, and is sleeved on the two shafts 15 in an axially movable and circumferentially rotatable manner. The outer ring of the sleeve of the two-shaft fixed cone disk 18 is provided with a sliding spline, and the inner ring of the two-shaft movable cone disk 19 is provided with a sliding spline and sleeved on the sleeve of the two-shaft fixed cone disk 18, so that the two-shaft movable cone disk 19 and the two-shaft fixed cone disk 18 can move axially with each other but cannot rotate circumferentially with each other; the two-shaft fixed cone disk 18 includes a sleeve manufactured integrally with the cone disk, and is sleeved on the two shafts 15 in an axially movable and circumferentially rotatable manner. The outer ring of the sleeve of the two-shaft fixed cone disk 18 is provided with a sliding spline, and the inner ring of the two-shaft movable cone disk 19 is provided with a sliding spline and sleeved on the sleeve of the two-shaft fixed cone disk 18, so that the two-shaft movable cone disk 19 and the two-shaft fixed cone disk 18 can move axially with each other but cannot rotate circumferentially with each other; The non-conical end of the cone disk 18 is connected to the outer ring of the thrust bearing 17, and the inner ring of the thrust bearing 17 is sleeved on the second shaft 15 and rests on the third support seat 16 fixedly connected to the second shaft 15, so that the second shaft cone disk unit and the second shaft 15 can achieve mutual rolling rotation, reducing the rotational friction and limiting the axial movement of the second shaft fixed cone disk 18; it is worth emphasizing that the rotation angle of the inner and outer rings of the thrust bearing 17 is the same and synchronized with the rotation angle of the main thrust disk 22 and the second shaft movable cone disk 19, that is, the maximum rotation angle of the thrust bearing 17 will not exceed one circle, and low mechanical efficiency and poor adaptability will not be caused by high-speed rotation.

[0088] Further, the thrust unit includes a main thrust disc 22, a thrust rolling body 21 and a first elastic component 25 of the second shaft; the main thrust disc 22 is sleeved and connected with the second shaft 15 in an axially movable and circumferentially fixed manner, and the end face of the main thrust disc 22 is against a fourth support seat 23 fixedly connected with the second shaft 15; the main thrust disc 22 and the opposite end faces of the non-conical end of the second shaft movable cone disc 19 are respectively provided with a main thrust ramp groove 22-1 and a secondary thrust ramp groove 22-2, and the secondary thrust ramp groove 22-2 and the main thrust ramp groove 22-1 are both V-shaped ramp grooves that rise symmetrically from the low point to both ends in the circumferential direction, and the secondary thrust ramp groove 22-2 and the main thrust ramp groove 22-1 are clamped in a manner of The thrust rolling body 21 held by the second shaft is arranged symmetrically in the center; the first elastic component 25 of the second shaft is sleeved on the second shaft 15, one end of which is pressed against the end surface of the main thrust disc 22 to provide thrust to the main thrust disc 22 toward the side of the second shaft dynamic cone disc 19, and the other end is sleeved and fixedly connected with the second shaft 15. When switching from transmitting the positive driving torque to the reverse drag torque (such as electric vehicle braking energy recovery), the first elastic component 25 of the second shaft pushes the main thrust disc 22 to move axially and press the thrust rolling body 21 to prevent the thrust rolling body 21 from escaping from the thrust ramp groove in this working condition, that is, the main effect of the first elastic component 25 of the second shaft is to ensure that the thrust rolling body 21 can roll normally when switching to the reverse drag working condition;

[0089] Furthermore, the thrust unit is provided with three groups of secondary thrust ramp grooves 22-2 and main thrust ramp grooves 22-1 clamping the thrust rolling body 21; in the installed state, the thrust rolling body 21 is arranged in the main thrust ramp groove 22-1 in the positive driving torque direction of the power source, and the axial displacement from the highest point of the main thrust ramp groove 22-1 is 3mm;

[0090] Further, the torsion unit includes a main torsion plate 24, a torsion rolling body 20 and a second elastic component 26 of the two shafts; the main torsion plate 24 is axially movable with the two shafts 15 but is circumferentially fixedly connected; the main torsion plate 24 and the opposite end surfaces of the non-conical end of the two-shaft movable cone plate 19 are respectively provided with a main torsion ramp groove 24-1 and a secondary torsion ramp groove 24-2; the main torsion ramp groove 24-1 and the secondary torsion ramp groove 24-2 are both unidirectional ramp grooves uniformly distributed in the circumferential direction and rising from one end to the other end, and are arranged symmetrically with the torsion rolling body 20 as the center;

[0091] The second elastic component 26 of the second shaft is sleeved on the second shaft 15, one end of which is pressed against the end surface of the main torque plate 24, and the other end is pressed against the fifth support seat 27 which is sleeved and fixedly connected with the second shaft 15. The second elastic component 26 of the second shaft pushes the main torque plate 24 to squeeze the torsion rolling body 20 to roll, so as to realize the positive rotation of the driving power source until the mechanical clearance 30 (such as Fig.10 and Fig.11 As shown), the annular transmission member 9 forms a preload between the first-axis cone disk unit and the second-axis cone disk unit;

[0092] Furthermore, the torsion unit is provided with three groups of auxiliary torsion ramp grooves 24-2 and main torsion ramp grooves 24-1 that clamp the torsion rolling body 20; in the installed state, the torsion rolling body 20 is arranged in the middle position of the auxiliary torsion ramp groove 24-2, and the second elastic component 26 of the second axis limits the annular transmission member 9 to the maximum working radius state of the second axis cone disk unit; the elastic coefficient of the second elastic component 26 of the second axis is less than the minimum elastic coefficient of the second elastic component 13 of the first axis.

[0093] The elastic coefficient of the first elastic component 3 of the first shaft is greater than the elastic coefficient of the second elastic component 13 of the first shaft; in the installed state, the thrust of the second elastic component 13 of the first shaft does not act on the annular transmission member 9, and the preload force of the system is provided by the torque unit.

[0094] i is the transmission speed ratio; R1 is the rolling working radius of the annular transmission part on the first axis; R2 is the rolling working radius of the annular transmission part on the second axis; a1 is the cone angle of the cone disk; μ is the friction coefficient between the annular transmission part and the cone disk; σ is the thrust ratio required for the torque transmission between the first axis and the second axis. The σ value is monotonically negatively correlated with the transmission speed ratio i. Through experiments, it is found that: σ=0.266*i^ 2 -1.02*i+2.02;R t is the rotation radius of the thrust rolling body around the two axes; a2 is the continuously changing angle of the secondary thrust ramp groove and the main thrust ramp groove; η is the efficiency of the thrust provided by the thrust unit being transmitted to one axis through the annular transmission member; L is the raceway length of the main thrust ramp groove and the secondary thrust ramp groove; R max is the maximum rolling radius of the annular transmission part, Rmin is the minimum rolling radius of the annular transmission member; d is the diameter of the thrust rolling body, the torsion rolling body and the centrifugal body. In this embodiment, a2, L, and d satisfy the following mathematical relationship:

[0095]

[0096] L≥2*(R max -R min )*tan a1 / 0.9 / sin a2

[0097] d≥(R max -R min )*tan a1*2 / 0.9

[0098] Example 2

[0099] like Figure 7 As shown, a continuously variable speed change device in which the centrifugal force for speed regulation does not act on the cone disk includes a first-axis cone disk unit, a second-axis cone disk unit, a thrust unit, a torque unit, and an annular transmission member 9 for transmitting power between the first-axis cone disk unit and the second-axis cone disk unit, and also includes a centrifugal speed regulation unit; wherein the second shaft 15 is used as a driving shaft for power source input, and the first shaft 1 is used as a driven shaft for power source input;

[0100] The shaft-cone-disc unit comprises a shaft 1, a shaft-fixed cone disk 8 fixedly connected to the shaft 1, and a shaft-moving cone disk 11 coaxially sleeved on the shaft 1 through an axial sliding spline, so that the shaft-moving cone disk 11 and the shaft 1 can move axially relative to each other but are fixed circumferentially;

[0101] like Fig.13 As shown, the centrifugal speed regulating unit includes a fixed centrifugal disc 7 provided with a fixed centrifugal ramp groove 7-1, a dynamic centrifugal disc 4 provided with a dynamic centrifugal ramp groove 4-1, a centrifugal block 6 and a first elastic component 3 of a shaft;

[0102] The fixed centrifugal disc 7 is fixedly connected to a shaft 1, and the non-slope groove end of the fixed centrifugal disc 7 is coaxially arranged with the non-conical surface end of the moving cone disc 11 of the shaft, and the spacing distance is greater than the axial movement distance of the moving cone disc 11 of the shaft; the moving centrifugal disc 4 is connected to the shaft 1 through an axial sliding spline so that it can move axially with each other but cannot rotate circumferentially with each other; the moving centrifugal slope groove 4-1 and the fixed centrifugal slope groove 7-1 are both unidirectionally rising slope grooves arranged radially along the shaft 1; in the installed state, the centrifugal block 6 is clamped at the lowest position (such as Fig.12 This embodiment provides 6 sets of centrifugal blocks 6 holding the dynamic centrifugal ramp groove 4-1 and the fixed centrifugal ramp groove 7-1.

[0103] The first elastic component 3 of the one shaft is sleeved on the one shaft 1, with one end abutting against the first support seat 2 fixedly connected to the one shaft 1, and the other end abutting against the non-slope groove end of the dynamic centrifugal disc 4 and providing pressure; it should be noted that the connection method between the first support seat 2 and the one shaft 1 can be integrally manufactured, fixed with a locking nut or other non-rotatable and non-axially movable connection methods;

[0104] The fixed centrifugal disc 7 is evenly provided with three through holes for sleeve-mounting the speed regulating push rods 10 near the inner ring. The three speed regulating push rods 10 pass through the through holes on the fixed centrifugal disc 7, with one end abutting against the slope groove end of the dynamic centrifugal disc 4, and the other end abutting against the non-conical surface end of the one-axis dynamic cone disc 11. The outer sides of the dynamic centrifugal disc 4 and the one-axis dynamic cone disc 11 in contact with the speed regulating push rods 10 are provided with radial limiting parts 5. The function of the radial limiting parts 5 is to prevent the speed regulating push rods 10 from moving radially under the action of centrifugal force and interfering with the through holes on the fixed centrifugal disc 7.

[0105] In the installed state, the length of the speed regulating push rod 10 is set to meet the requirement that the elastic force of the first elastic component 3 of the first shaft does not act on the movable cone disk 11 of the first shaft, and the axial position of the movable cone disk 11 of the first shaft is limited to ensure that the annular transmission member 9 is at the maximum working radius of the cone disk unit of the first shaft; in the process of transmitting torque, the axial thrust generated by the thrust unit acts on the movable cone disk 11 of the first shaft through the annular transmission member 9, and the thrust is less than the elastic force of the first elastic component 3 of the first shaft; when the first shaft 1 rotates at a high speed, the centrifugal force generated by the centrifugal block 6 compresses the first elastic component 3 of the first shaft and pushes the movable centrifugal disk 4 to generate axial displacement, and at the same time, the thrust jointly generated by the thrust unit and the torsion unit will act on the movable cone disk 11 of the first shaft through the annular transmission member 9, and push the movable cone disk 11 of the first shaft and the movable centrifugal disk 4 to move axially in the same direction synchronously.

[0106] The two-shaft cone-disk unit comprises two shafts 15, two-shaft fixed cone disks 18 and two-shaft movable cone disks 19. One end of the annular transmission member 9 is clamped between the conical surfaces of the two-shaft fixed cone disk 18 and the two-shaft movable cone disk 19. The two-shaft fixed cone disk 18 comprises a sleeve manufactured integrally with the cone disk, and is sleeved on the two shafts 15 in an axially movable and circumferentially rotatable manner. The outer ring of the sleeve of the two-shaft fixed cone disk 18 is provided with a sliding spline, and the inner ring of the two-shaft movable cone disk 19 is provided with a sliding spline and sleeved on the sleeve of the two-shaft fixed cone disk 18, so that the two-shaft movable cone disk 19 and the two-shaft fixed cone disk 18 can move axially with each other but cannot rotate circumferentially with each other. The non-conical surface end of the two-shaft fixed cone disk 18 is connected to the outer ring of the thrust bearing 17. The thrust bearing 17 The inner ring is sleeved on the second shaft 15 and rests on the third support seat 16 fixedly connected to the second shaft 15, so that the second shaft cone disk unit and the second shaft 15 can realize mutual rolling rotation, reduce the rotational friction, and limit the axial movement of the second shaft fixed cone disk 18; it is worth emphasizing that the rotation angle of the inner and outer rings of the thrust bearing 17 is the same and synchronous with the rotation angle of the main thrust disk 22 and the second shaft movable cone disk 19, that is, the maximum rotation angle of the thrust bearing 17 will not exceed one circle, and the mechanical efficiency and poor adaptability will not be low due to high-speed rotation; it should be noted that the connection method of the third support seat 16 and the second shaft 15 can be integrally manufactured, fixed with a locking nut or other non-rotatable and non-axially movable connection methods.

[0107] like Figure 7 and Fig.12 As shown, the thrust unit includes a main thrust plate 22 provided with a main thrust ramp groove 22-1, a thrust rolling body 21 and a first elastic component 25 of the second shaft; a secondary thrust ramp groove 22-2 matching the main thrust ramp groove 22-1 is provided on the non-conical end surface of the second shaft movable cone plate 19; the main thrust plate 22 is axially movable with the second shaft 15 and is circumferentially fixedly connected; one end of the first elastic component 25 of the second shaft abuts against the end surface of the main thrust plate 22 and provides pressure toward the second shaft movable cone plate 19 to the main thrust plate 22, and the other end abuts against the end surface of the main torsion plate 24; the end surface of the main thrust plate 22 abuts against the fourth support seat 23 fixedly connected to the second shaft 15.

[0108] like Fig.12As shown, the secondary thrust ramp groove 22-2 and the main thrust ramp groove 22-1 are both V-shaped slope groove structures that rise symmetrically from the middle to both ends; the secondary thrust ramp groove 22-2 and the main thrust ramp groove 22-1 are arranged symmetrically with the clamped thrust rolling body 21 as the center, so that when the main thrust disc 22 and the two-axis dynamic cone disc 19 transmit torque, an axial thrust will be generated on the two-axis dynamic cone disc 19, and the main thrust disc 22 and the two-axis dynamic cone disc 19 can provide a speed regulating stroke for the axial movement of the two-axis dynamic cone disc 19 when the main thrust disc 22 and the two-axis dynamic cone disc 19 rotate relative to each other; in the installed state, the thrust rolling body 21 sets the lowest point position of the secondary thrust ramp groove 22-2, and the annular transmission member 9 is at the minimum working radius of the two-axis cone disc unit; in this embodiment, a total of 3 groups of secondary thrust ramp grooves 22-2 and main thrust ramp grooves 22-1 are provided, and are evenly arranged along the circumference of the two-axis dynamic cone disc 19.

[0109] like Figure 7 and Fig.12 As shown, the torsion unit includes a main torsion plate 24 provided with a main torsion ramp groove 24-1, a torsion rolling body 20 and a second elastic component 26 of the second axis;

[0110] The main torsion plate 24 is connected to the two shafts 15 in a relatively axially movable and circumferentially fixed manner; a secondary torsion ramp groove 24-2 matching the main torsion ramp groove 24-1 is provided on the non-conical end surface of the movable cone plate 19 of the two shafts; in the installed state, the torsion rolling body 20 is clamped in the middle position between the main torsion ramp groove 24-1 and the secondary torsion ramp groove 24-2; one end of the second elastic component 26 of the two shafts is against the end surface of the non-main torsion ramp groove 24-1 of the main torsion plate 24, and the other end is against the fifth support seat 27 fixedly connected to the two shafts 15. It should be noted that the connection method of the fifth support seat 27 and the two shafts 15 can be integrally manufactured, fixed with a locking nut or other non-rotatable and non-axially movable connection methods.

[0111] like Fig.12 As shown, the auxiliary torsion ramp groove 24-2 and the main torsion ramp groove 24-1 are both unidirectional ramp grooves rising from one end to the other end, and the auxiliary torsion ramp groove 24-2 and the main torsion ramp groove 24-1 are arranged symmetrically with the clamped torsion rolling body 20 as the center; the second elastic component 26 of the two axes pushes the main torsion disc 24 to squeeze the torsion rolling body 20 to roll, and the torsion unit can realize the positive rotation of the driving power source until the mechanical gap 30 is eliminated.

[0112] In this embodiment, three groups of auxiliary torsion ramp grooves 24-2 and main torsion ramp grooves 24-1 for clamping the torsion rolling body 20 are provided and are evenly arranged along the circumference of the two-axis movable cone disk 19; it should be noted that the positions of the thrust unit and the torsion unit on the two shafts 15 are not unique, and in other embodiments other than this embodiment, the thrust unit can be arranged on the outside, and the torsion unit can be arranged on the inside, which also belongs to the scope of protection of the present invention;

[0113] In this embodiment, the first elastic component 25 of the two axes is a butterfly spring with three stacked pieces, the second elastic component 26 of the two axes is a butterfly spring with five stacked pieces, and the first elastic component 3 of the one axis is a butterfly spring with seven stacked pieces;

[0114] In another embodiment, the speed regulating push rod 10 may also pass through the outer ring of the fixed centrifugal disc 7 (outside of the centrifugal block 6) to achieve the same function.

[0115] The method of use of Example 2 is as follows:

[0116] Taking the application of pure electric vehicles as an example, the second shaft 15 is used as the power input shaft and the first shaft 1 is used as the output shaft, and the typical working conditions are analyzed:

[0117] When the vehicle speed is zero and before the power is transmitted, the mechanical clearance 28 between the main thrust disc 22 and the second-axis dynamic cone disc 19 has been eliminated by the torque unit driving power source to rotate forward, and the thrust rolling body 21 is located at the position of the secondary thrust ramp groove 22-2 and the main thrust ramp groove 22-1. 0+ / N 0+ The torsion rolling element 20 is located at the X position between the secondary torsion ramp groove 24-2 and the primary torsion ramp groove 24-1. 0+ / Y 0+ , the centrifugal body 6 is located at the lowest point H0 / J0 of the dynamic centrifugal ramp groove 4-1 and the fixed centrifugal ramp groove 7-1, at which time the transmission speed ratio is the maximum (such as Fig.12 shown);

[0118] When the vehicle transmits torque and reaches the maximum speed from zero speed, the centrifugal body 6 compresses the first elastic component 3 of the first axis under the action of centrifugal force and pushes the dynamic centrifugal disc 4 to move axially. At the same time, the thrust generated by the dynamic cone disc 19 of the second axis under the action of the torque unit and the thrust unit acts on the dynamic cone disc 11 of the first axis through the annular transmission member 9 to enable it to achieve synchronous axial movement and speed regulation with the dynamic centrifugal disc 4; at this time, the thrust rolling body 21 is located at the M1 / N2 position of the secondary thrust ramp groove 22-2 and the main thrust ramp groove 22-1, the torsion rolling body 20 is located at the X1 / Y2 position of the secondary torsion ramp groove 24-2 and the main torsion ramp groove 24-1, the second elastic component 26 of the second axis is extended, and the centrifugal body 6 is located at the highest point H1 / J1 of the dynamic centrifugal ramp groove 4-1 and the fixed centrifugal ramp groove 7-1. At this time, the transmission speed ratio is at the minimum (such as Fig.13 shown).

[0119] When the vehicle switches to the braking energy recovery working condition, the process of the torsional rolling body 20 climbing from position X1 / Y2 to X2 / Y1 will compress the second elastic component 26 of the second axis and provide the clamping force required for transmitting the reverse torque. At the same time, the first elastic component 25 of the second axis pushes the main thrust disc 22 to move axially and presses the thrust rolling body 21 to prevent the thrust rolling body 21 from leaving the thrust ramp groove in this working condition, while satisfying the rolling motion of the thrust rolling body 21 (the thrust provided by the first elastic component 25 of the second axis only needs to meet the thrust of the main thrust disc 22 axially in this working condition). until the thrust rolling body 21 falls back from M1 / N2 to M0 / N0 and climbs to M2 / N1, the thrust unit starts to provide the clamping force required to transmit the reverse torque; because the mass of the power source is relatively small, the energy consumed in the process of compressing the second elastic component 26 of the second axis can prevent the thrust rolling body 21 from rushing directly from M1 / N2 to M2 / N1 quickly, causing the annular transmission member 9 to slip and vibrate and impact. At this time, it is a transient working condition, the vehicle speed has not been reduced in time, the centrifugal block 6 is still in the H1 / J1 position, and the transmission speed ratio is still at the minimum (such as Fig.14 This working process explains the principle of reverse drag transmission of power.

[0120] When the vehicle is moving from the maximum speed (such as Fig.14 As shown in the figure, the centrifugal force of the centrifugal body 6 decreases with the decrease of the vehicle speed, and the centrifugal body 6 falls from the highest position H1 / J1 to the lowest position H0 / J0 under the thrust of the first elastic component 3 of the first shaft. At the same time, the thrust of the first elastic component 3 of the first shaft acts on the first shaft movable cone disc 11 through the speed regulating push rod 10, and is transmitted to the second shaft cone disc unit through the annular transmission member 9. The second shaft movable cone disc 19 squeezes the thrust rolling body 21 from M2 / N1 to M 0+ / N 0+ At the same time, the main thrust disc 22 is pushed to move axially and compress the second-axis first elastic component 25 until the main thrust disc 22 abuts against the fourth support seat 23, and the torsion rolling body 20 falls back from X2 / Y1 to the middle position X 0+ / Y 0+ , at this time the transmission speed ratio is at its maximum (such as Fig.12 shown).

[0121] Example 3

[0122] like Fig.15 As shown, a continuously variable transmission device in which the centrifugal force for speed regulation does not act on the cone disk includes a first-axis cone disk unit, a second-axis cone disk unit, and an annular transmission member 9 for transmitting power between the first-axis cone disk unit and the second-axis cone disk unit, and also includes a centrifugal speed regulation unit; wherein the second shaft 15 is used as a driving shaft for power source input, and the first shaft 1 is used as a driven shaft for power source input;

[0123] The two-shaft cone disk unit includes two shafts 15, two-shaft fixed cone disks 18 and two-shaft movable cone disks 19, the two-shaft fixed cone disks 18 are fixedly connected to the two shafts 15; the two-shaft movable cone disks 19 and the two shafts 15 can move axially with each other but cannot rotate circumferentially with each other; the thrust unit of this embodiment is replaced by a thrust elastic component 28 sleeved on the two shafts 15, one end of the thrust elastic component 28 presses against the non-conical end surface of the two-shaft movable cone disk 19, and provides thrust to the two-shaft movable cone disk 19 to generate the clamping force required for the annular transmission member 9 to transmit torque, and the other end of the thrust elastic component 28 presses against the sixth support seat 29 fixedly connected to the two shafts 15; the annular transmission member 9 is at the minimum working radius of the two-shaft cone disk unit;

[0124] The shaft-cone-disc unit comprises a shaft 1, a shaft-fixed cone disk 8 fixedly connected to the shaft 1, and a shaft-moving cone disk 11 coaxially sleeved on the shaft 1 through an axial sliding spline, so that the shaft-moving cone disk 11 and the shaft 1 can move axially relative to each other but are fixed circumferentially;

[0125] The centrifugal speed regulating unit comprises a fixed centrifugal disc 7 provided with a fixed centrifugal ramp groove 7-1, a dynamic centrifugal disc 4 provided with a dynamic centrifugal ramp groove 4-1, a centrifugal block 6 and a first elastic component 3 of a shaft;

[0126] The fixed centrifugal disc 7 is fixedly connected to a shaft 1, and the non-slope groove end of the fixed centrifugal disc 7 is coaxially arranged with a non-conical surface end of a moving cone disc 11 of a shaft, and the spacing distance is greater than the axial movement distance of the moving cone disc 11 of a shaft; the moving centrifugal disc 4 is connected to the shaft 1 through an axial sliding spline so that it can move axially with each other but cannot rotate circumferentially with each other; the moving centrifugal slope groove 4-1 and the fixed centrifugal slope groove 7-1 are both unidirectionally rising slope grooves arranged radially along the shaft 1; in the installed state, the centrifugal block 6 is clamped in the lowest position of the moving centrifugal slope groove 4-1 and the fixed centrifugal slope groove 7-1; this embodiment is provided with 6 groups of moving centrifugal slope grooves 4-1 and fixed centrifugal slope grooves 7-1 clamping the centrifugal block 6.

[0127] The first elastic component 3 of the one shaft is sleeved on the one shaft 1, with one end abutting against the first support seat 2 fixedly connected to the one shaft 1, and the other end abutting against the non-slope groove end of the dynamic centrifugal disc 4 and providing pressure; it should be noted that the connection method between the first support seat 2 and the one shaft 1 can be integrally manufactured, fixed with a locking nut or other non-rotatable and non-axially movable connection methods;

[0128] The fixed centrifugal disc 7 is evenly provided with three through holes for sleeve-mounting the speed regulating push rods 10 near the inner ring. The three speed regulating push rods 10 pass through the through holes on the fixed centrifugal disc 7, with one end abutting against the slope groove end of the dynamic centrifugal disc 4, and the other end abutting against the non-conical surface end of the one-axis dynamic cone disc 11. The outer sides of the dynamic centrifugal disc 4 and the one-axis dynamic cone disc 11 in contact with the speed regulating push rods 10 are provided with radial limiting parts 5. The function of the radial limiting parts 5 is to prevent the speed regulating push rods 10 from moving radially under the action of centrifugal force and interfering with the through holes on the fixed centrifugal disc 7.

[0129] In the installed state, the length of the speed regulating push rod 10 is set to ensure that the elastic force of the first elastic component 3 of the first shaft does not act on the dynamic cone disk 11 of the first shaft, and the axial position of the dynamic cone disk 11 of the first shaft is limited to ensure that the annular transmission member 9 is at the maximum working radius of the cone disk unit of the first shaft; the axial thrust generated by the thrust elastic component 28 acts on the dynamic cone disk 11 of the first shaft through the annular transmission member 9, and the thrust is less than the elastic force of the first elastic component 3 of the first shaft; when the first shaft 1 rotates at a high speed, the centrifugal force generated by the centrifugal block 6 compresses the first elastic component 3 of the first shaft and the dynamic centrifugal disk 4 to generate axial displacement, and at the same time, the thrust of the thrust elastic component 28 will pass through the annular transmission member 9 acts on the one-axis dynamic cone disk 11, and pushes the one-axis dynamic cone disk 11 to move axially in the same direction as the dynamic centrifugal disk 4, thereby reducing the transmission speed ratio; when the vehicle speed decreases, the centrifugal body 6 descends along the centrifugal ramp groove under the thrust of the one-axis first elastic component 3, and at the same time pushes the one-axis dynamic cone disk 11 to move axially through the speed regulating push rod 10, and transmits the thrust to the second-axis dynamic cone disk 19 through the annular transmission member 9 to compress the thrust elastic member 28, thereby increasing the transmission speed ratio; in the installed state, the elastic coefficient of the one-axis first elastic component 3 is greater than the thrust elastic member 28, and the annular transmission member 9 limits the maximum working radius of the one-axis cone disk unit.

[0130] It is worth noting that the embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solution of the present invention can be modified or replaced by equivalents without departing from the purpose and scope of the technical solution, which should be included in the scope of the claims of the present invention.

Claims

1. A continuously variable transmission transmission device in which the centrifugal force for speed regulation does not act on the cone disk, comprising a first-shaft cone disk unit, a second-shaft cone disk unit and an annular transmission member for transmitting power between the first-shaft cone disk unit and the second-shaft cone disk unit, wherein the first-shaft cone disk unit comprises a first-shaft fixed cone disk and a first-shaft movable cone disk arranged with a shaft and a cone surface relatively, wherein the first-shaft fixed cone disk is sleeved and fixedly connected to the first shaft, and the first-shaft movable cone disk is sleeved and connected to the first shaft in an axially movable but circumferentially fixed manner; the second-shaft cone disk unit comprises a second-shaft fixed cone disk and a second-shaft movable cone disk arranged with a shaft and a cone surface relatively, and a power source is connected to the first shaft or the second shaft, characterized in that: It also includes a thrust unit arranged at the non-conical end of the two-shaft movable cone disc, transmitting power to the annular transmission member to provide a clamping force, and a centrifugal speed regulating unit arranged on one shaft; The centrifugal speed regulating unit comprises a dynamic centrifugal disc, a fixed centrifugal disc, a centrifugal body and a first elastic component of a shaft, wherein the dynamic centrifugal disc is abutted against a dynamic conical disc of a shaft, and the first elastic component of a shaft abuts against an end surface of the dynamic centrifugal disc and provides a thrust to the dynamic centrifugal disc in a direction toward the dynamic conical disc of the shaft; The fixed centrifugal disc and the dynamic centrifugal disc are coaxially arranged opposite to each other, and at least one of the two oppositely arranged end faces is provided with a centrifugal slope groove, wherein the one provided on the end face of the fixed centrifugal disc is a fixed centrifugal slope groove, and the one provided on the dynamic centrifugal end face is a dynamic centrifugal slope groove; The centrifugal body is clamped in the centrifugal ramp groove. Under the action of the rotating centrifugal force, the centrifugal body climbs along the centrifugal ramp groove and compresses the first elastic component of the one-axis and pushes the dynamic centrifugal disk to move axially away from the fixed centrifugal disk, while providing an axial movement space for the one-axis dynamic cone disk to move synchronously and in the same direction as the dynamic centrifugal disk.

2. The continuously variable transmission device according to claim 1, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: The axially opposite end surfaces of the fixed centrifugal disc and the dynamic centrifugal disc are respectively provided with a fixed centrifugal slope groove and a dynamic centrifugal slope groove; The fixed centrifugal ramp groove and the dynamic centrifugal ramp groove are radially inclined rolling tracks from low to high, and at least two groups of dynamic centrifugal ramp grooves and fixed centrifugal ramp grooves clamping the centrifugal body are evenly distributed along the circumferential direction of the fixed centrifugal disc.

3. The continuously variable transmission device according to claim 2, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: When the two shafts are connected to a power source and serve as driving shafts, the fixed centrifugal disc is fixedly sleeved on one shaft and arranged on the non-conical side of the dynamic conical disc of the one shaft, and the dynamic centrifugal disc is sleeved on one shaft in an axially movable and circumferentially fixed manner and arranged on the side of the fixed centrifugal disc that is circularly away from the dynamic conical disc of the one shaft; The fixed centrifugal disc is provided with a through hole, so that the non-conical end of the one-shaft dynamic conical disc and the end surface of the dynamic centrifugal disc are abutted and connected through a speed regulating push rod passing through the through hole on the fixed centrifugal disc; In the installed state, the annular transmission member is at the maximum working radius of the shaft cone disk unit, and in the process of transmitting torque, the axial thrust generated by the thrust unit acting on the shaft dynamic cone disk through the annular transmission member is smaller than the elastic force of the first elastic component of the shaft.

4. The continuously variable transmission device according to claim 2, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: When the one shaft is connected to the power source and serves as the driving shaft, the centrifugal speed regulating unit further comprises a second elastic component of the one shaft; One end of the second elastic component of the one shaft is sleeve-fixedly connected to the one shaft, and the other end presses against the non-conical end of the movable cone disk of the one shaft, and provides a thrust to the movable cone disk of the one shaft toward the fixed cone disk of the one shaft; the second elastic component of the one shaft is provided with at least two groups of elastic members with different elastic coefficients, and each elastic coefficient of the second elastic component of the one shaft is smaller than the elastic coefficient of the first elastic component of the one shaft; the dynamic centrifugal disk is sleeve-connected to the one shaft in an axially movable and circumferentially fixed manner, and is arranged on one side of the non-conical side of the fixed cone disk of the one shaft, the fixed centrifugal disk is fixedly connected to the non-conical end of the fixed cone disk of the one shaft or manufactured in one piece, and is arranged on the side of the dynamic centrifugal disk close to the fixed cone disk of the two shafts; The fixed conical disc and the fixed centrifugal disc of the one shaft are provided with through holes, and the dynamic centrifugal disc abuts against the dynamic conical disc of the one shaft via a speed regulating push rod passing through the through holes; In the installed state, the first elastic component of the first shaft compresses the second elastic component of the first shaft through the speed regulating push rod, and satisfies that the annular transmission member is at the minimum working radius in the cone disk unit of the first shaft.

5. The continuously variable transmission device according to claim 3, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: The two-shaft fixed cone disks are sleeved on the two shafts in a manner of circumferential rotation and axial fixation, and the two-shaft movable cone disks are sleeved on the two-shaft fixed cone disks in an axially slidable and circumferentially fixed manner; The thrust unit comprises a main thrust disc, a thrust rolling body and a first elastic component of the two shafts. The main thrust disc is sleeve-connected with the two shafts in an axially movable and circumferentially fixed manner and is arranged on one side of the non-conical surface end of the movable cone disc of the two shafts. The first elastic component of the second shaft is sleeved on the second shaft and arranged on a side of the main thrust plate away from the movable cone plate of the second shaft, so as to provide the main thrust plate with an axial thrust in the direction of the movable cone plate of the second shaft, and an end surface of the main thrust plate on a side away from the movable cone plate of the second shaft abuts against a fourth support seat fixedly connected to the second shaft; The main thrust ramp groove and the secondary thrust ramp groove are respectively provided on the opposite end surfaces of the non-conical surface side of the main thrust disc and the second-axis dynamic cone disc in the circumferential direction, and the thrust rolling body is clamped between the main thrust ramp groove and the secondary thrust ramp groove. Both the secondary thrust ramp groove and the main thrust ramp groove are V-shaped slope grooves that rise symmetrically from the low point to both ends, and the secondary thrust ramp groove and the main thrust ramp groove are arranged symmetrically with the clamped thrust rolling body as the center; The torque transmitted by the main thrust disc and the two-axis movable cone disc can generate an axial thrust on the two-axis movable cone disc and form the clamping force required for the annular transmission member to transmit the torque, and the axial stroke generated by the mutual rotation between the main thrust disc and the two-axis movable cone disc matches the axial stroke required for the speed regulation of the two-axis movable cone disc.

6. The continuously variable transmission device according to claim 5, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: It also includes a torsion unit arranged on the two shafts, the torsion unit includes a main torsion plate, a torsion rolling body and a second elastic component of the two shafts; The main torque disc is sleeved on the two shafts in a manner that it can move relatively axially but is fixed circumferentially and is arranged on one side of the non-conical surface end of the movable cone disc of the two shafts, and the main torque ramp groove and the auxiliary torque ramp groove are respectively provided on the opposite end surfaces of the non-conical surface side of the main torque disc and the movable cone disc of the two shafts in the circumferential direction, and the torsion rolling body is clamped between the main torque ramp groove and the auxiliary torque ramp groove, and the main torque ramp groove and the auxiliary torque ramp groove are both unidirectional ramp grooves that rise from one end to the other end, and are arranged symmetrically with the center to clamp the torsion rolling body, and the second elastic component of the two shafts is pressed against the end surface of the main torque disc away from the main ramp groove and provides a thrust in the direction of the movable cone disc of the two shafts, so as to realize that the torque unit generates a torque that drives the power source to rotate in the forward direction.

7. The continuously variable transmission device according to claim 6, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: The torsion unit is provided with at least two groups of auxiliary torsion ramp grooves and main torsion ramp grooves for clamping the torsion rolling body, and the thrust unit is provided with at least two groups of auxiliary thrust ramp grooves and main thrust ramp grooves for clamping the thrust rolling body.

8. The continuously variable transmission device according to claim 7, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: When the one shaft is connected to a power source and serves as a driving shaft, in the installed state, the thrust rolling body is arranged at the highest point in the main thrust ramp groove, the torsion rolling body is arranged at the middle position of the main torsion ramp groove, and the annular transmission member is located at the minimum working radius in the one shaft cone disk unit.

9. The continuously variable transmission device according to claim 7, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: When the two shafts are connected to a power source and serve as driving shafts, in the installed state, the thrust rolling body is arranged at the lowest point in the main thrust ramp groove, the torsion rolling body is arranged at the middle position of the main torsion ramp groove, and the annular transmission member is located at the maximum working radius in a single-shaft cone disk unit.

10. The continuously variable transmission device according to claim 7, wherein the centrifugal force for speed regulation does not act on the cone disk, is characterized in that: The angle of the secondary thrust ramp groove, the angle of the main thrust ramp groove, the raceway length of the secondary thrust ramp groove, the raceway length of the main thrust ramp groove, the diameter of the thrust rolling element, and the diameters of the torsion rolling element and the centrifugal element satisfy the following relationship: <h2 style=";text-align:left;direction:ltr">L≥2*(R<h2 style=";text-align:left;direction:ltr"> max <h2 style=";text-align:left;direction:ltr"> -R<h2 style=";text-align:left;direction:ltr"> min <h2 style=";text-align:left;direction:ltr"> )*tan a1 / 0.9 / sin a2 d≥(R max -R min )*tan a1*2 / 0.9 In the above formula, i is the transmission speed ratio; R1 is the rolling working radius of the annular transmission part on the first axis; R2 is the rolling working radius of the annular transmission part on the second axis; a1 is the cone angle value of the cone disk; μ is the friction coefficient between the annular transmission part and the cone disk; σ is the thrust ratio required for the first axis and the second axis to transmit torque, and the σ value is monotonically negatively correlated with the transmission speed ratio i; R t is the rotation radius of the thrust rolling body around the two axes; a2 is the continuously changing angle of the secondary thrust ramp groove and the main thrust ramp groove; η is the efficiency of the thrust provided by the thrust unit being transmitted to one axis through the annular transmission member; L is the raceway length of the main thrust ramp groove and the secondary thrust ramp groove; R max is the maximum rolling radius of the annular transmission part, R min is the minimum rolling radius of the annular transmission part; d is the diameter of the thrust rolling body, torsion rolling body and centrifugal body.

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