Transmission device of continuously variable transmission

Abstract

The utility model belongs to the technical field of transmissions, and relates to a transmission device of a continuously variable transmission, which comprises a first-shaft conical disc unit, a second-shaft conical disc unit, an annular transmission part for transmission connection, an axial limiting part and a torsion unit, the axial limiting part is fixedly connected with the first shaft, in the assembling state, the axial limiting part limits the axial position of the first shaft moving cone disc to prevent the axial force of the first elastic assembly from acting on the annular transmission piece, and the annular transmission piece is located at the maximum working radius of the first shaft cone disc unit; the torsion unit comprises a main torsion disc which is arranged on the second shaft in a sleeving mode in an axial sliding and circumferential fixing mode, and in the installation state, the main torsion disc is used for providing forward rotation torque for a power source and providing pre-tightening force for the annular transmission piece.

Description

Technical Field

[0001] This utility model belongs to the field of transmission technology, specifically relating to a continuously variable transmission (CVT) device. Background Technology

[0002] The cone-disc type continuously variable transmission device establishes rolling friction to transmit power by clamping an annular transmission component (metal belt, rubber belt, etc.) between the conical surfaces of two pairs of cone discs, and achieves speed regulation by changing the rolling radius of the annular transmission component on the cone discs.

[0003] Electrification of vehicle power units is a current trend, especially in road transportation, where the market penetration rate has exceeded 50%. Compared to internal combustion engines, electric motors offer low-speed constant torque output, greater overload capacity, and excellent smoothness. Electric motors can typically output twice their rated power for up to one minute, operating at high efficiency between their rated speed and twice their rated speed. However, beyond twice their rated speed, their efficiency decreases, manufacturing processes become more complex, and material strength requirements increase, leading to higher costs and reduced reliability. Compared to internal combustion engines, using electric motors as the power source for vehicle machinery simplifies the speed control requirements of the transmission system. When higher wheel-end torque is needed, the transmission ratio is at its maximum; when higher wheel-end speed is needed, the transmission ratio is at its minimum, eliminating the need for frequent, precise active speed adjustment to improve power system efficiency. Furthermore, for commercial cargo vehicles and sports cars, single-stage reducers still cannot adequately meet the demands of heavy loads and higher speeds. Given the above background, continuously variable transmissions (CVTs) that can provide timely power response, without power interruption, without shock or jerking, without the need for clutch settings, and without the need for active speed control are the transmission technologies urgently needed in the electric vehicle market.

[0004] Based on the above requirements, CN117090910A proposes a cone-disc continuously variable transmission (CVT) scheme that can adaptively provide clamping force and speed regulation force. This scheme provides clamping force and speed regulation force through a sloped pressure mechanism on the driven shaft, effectively simplifying the structure and reducing costs. However, this scheme has the following problems: 1. If the preload value of the active pressure spring group is sufficient to transmit large torque at the minimum speed ratio, there will be excessive clamping force when transmitting small to medium torque, resulting in low transmission efficiency and reduced service life; 2. If the preload of the active pressure spring is designed to adapt to the transmission of small to medium torque, it will lead to frequent speed adjustments during the transmission of medium to high torque, reducing the system's service life and transmission efficiency. Furthermore, rapid acceleration under high-speed conditions may cause the power system speed to exceed the range due to the increased speed ratio, resulting in damage (such as the motor speed exceeding the limit, causing rotor damage, and excessive back EMF causing damage to the motor controller); 3. This scheme discloses setting more than two yield strength coefficients for the active pressure spring group. If a spring group with a sufficiently small yield coefficient is used to meet the system preload, Furthermore, the design utilizes a distance setting device to avoid issues such as low mechanical efficiency and reduced service life due to excessive clamping force during short-range torque transmission. Additionally, mechanical clearances exist in the annular transmission components due to wear, inelastic elongation, and assembly issues, leading to oscillations and impacts during power transmission, causing malfunctions. 4. To prevent destructive impacts on the annular transmission components caused by uncontrolled torque fluctuations at high speeds, the design includes complex active and passive buffering devices. This increases system cost and complexity, and only mitigates the impact damage to the annular transmission components, failing to eliminate the destructive effects. 5. Finally, it is worth emphasizing that the design does not consider matching the raceway angle of the sloped pressurization structure to the transmission speed ratio. A fixed raceway angle will result in excessive clamping force, leading to low mechanical efficiency and reduced service life.

[0005] In CN119802175A, this invention proposes a method that uses a torque unit to enable a slope pressurization structure to smoothly and without impact transmit power in both forward and reverse directions, and eliminates system impact problems caused by mechanical backlash by providing positive rotational torque to the power source. However, this technology achieves speed regulation by setting a centrifugal speed regulation unit, and its centrifugal speed regulation system has a relatively complex structure, making it unsuitable for use in the field of small-scale machinery where size requirements are high. Utility Model Content

[0006] In view of this, the main purpose of this utility model is to provide a continuously variable transmission device to solve the problems that the active pressure spring assembly of the existing solution cannot meet the needs of the vehicle under different working conditions; such as low mechanical efficiency, frequent speed adjustment reducing service life, complex buffer mechanism and failure to eliminate the risk of impact damage to the ring transmission component, and excessive clamping force caused by the slope pressure raceway angle not being designed according to the transmission speed ratio, resulting in low transmission efficiency and reduced service life.

[0007] To achieve the above objectives, this utility model provides the following technical solution:

[0008] A continuously variable transmission (CVT) includes a primary shaft conical disc unit, a secondary shaft conical disc unit, an annular transmission component, and a first elastic component sleeved and connected to a primary shaft. The primary shaft conical disc unit includes a primary shaft and a primary shaft fixed conical disc and a primary shaft movable conical disc arranged coaxially with their conical surfaces opposite each other. The primary shaft fixed conical disc is fixedly sleeved and connected to the primary shaft, and the primary shaft movable conical disc is sleeved on the primary shaft in a circumferentially fixed and axially sliding manner. The first elastic component presses against the non-conical end of the primary shaft movable conical disc and provides thrust to it. The secondary shaft conical disc unit includes two shafts and secondary shaft fixed conical discs and secondary shaft movable conical discs arranged with their conical surfaces opposite each other. The secondary shaft fixed conical discs are sleeved on the secondary shafts in a manner that allows them to rotate relative to each other and are fixed in at least one axial direction. The secondary shaft movable conical discs are sleeved on the secondary shaft fixed conical discs in a circumferentially fixed and axially sliding manner. A power source is connected to the primary shaft. The primary shaft is characterized by:

[0009] It also includes an axial limiting part disposed between a fixed cone disk and a movable cone disk, the axial limiting part being fixedly connected to a shaft; in the assembled state, the axial limiting part prevents the axial force of the first elastic component from acting on the annular transmission component by limiting the axial position of the movable cone disk, and realizes that the annular transmission component is at the maximum working radius of the cone disk unit.

[0010] It also includes a torque unit mounted on the two shafts, the torque unit including a main torque disc that is axially sliding and circumferentially fixed on the two shafts; in the installed state, the main torque disc is used to provide a positive rotational torque to the power source and to provide a preload force to the annular transmission component.

[0011] Furthermore, the non-conical end face of the dual-axis moving cone disk is provided with a secondary torque disk and a main thrust disk, and the secondary torque disk and the main thrust disk are coaxially and fixedly connected to the dual-axis moving cone disk;

[0012] Furthermore, the torque unit also includes a torque rolling element and a third elastic component; the main torque disk is arranged on one side of the non-conical end of the dual-axis moving cone disk, and the main torque ramp groove and the auxiliary torque ramp groove are respectively provided in the circumferential direction of the main torque disk and the auxiliary torque disk to clamp the torque rolling element in a centrally symmetrical manner. The main torque ramp groove and the auxiliary torque ramp groove are both unidirectional ramp grooves that rise from one end to the other.

[0013] One end of the third elastic component abuts against the end face of the main torque disc on the side opposite to the main torque ramp groove and provides axial pressure toward the auxiliary torque disc to the main torque disc.

[0014] Furthermore, at least two sets of secondary torque ramp grooves and primary torque ramp grooves are evenly distributed along the circumference; in the assembled state, the torque rolling element is positioned in the middle of the secondary torque ramp groove.

[0015] Furthermore, it also includes a thrust unit disposed on the second shaft, the thrust unit comprising an auxiliary thrust disk and a thrust rolling element; the auxiliary thrust disk is disposed on the non-conical side of the second shaft moving cone disk and is connected to the second shaft in a circumferentially fixed and axially movable manner; the auxiliary thrust disk and the main thrust disk are respectively provided with an auxiliary thrust ramp groove and a main thrust ramp groove that are centrally symmetrical to clamp the thrust rolling element, so that when the auxiliary thrust disk transmits torque to the second shaft moving cone disk, it can generate an axial thrust on the second shaft moving cone disk and form the clamping force required for the annular transmission component to transmit torque, and the axial travel generated by the mutual rotation between the auxiliary thrust disk and the second shaft moving cone disk matches the axial travel required for the speed adjustment of the second shaft moving cone disk.

[0016] Furthermore, the thrust unit also includes a second elastic component, which is sleeved on the second shaft and arranged on the side of the auxiliary thrust disk away from the second shaft moving cone disk, so as to provide an axial thrust to the auxiliary thrust disk in the direction of the second shaft moving cone disk, and the end face of the auxiliary thrust disk away from the second shaft moving cone disk abuts against a third support fixedly connected to the second shaft.

[0017] Furthermore, at least two sets of secondary thrust ramps and main thrust ramps are evenly distributed along the circumference of the secondary thrust disk, and both the secondary thrust ramps and main thrust ramps are V-shaped slope groove structures that rise symmetrically from the low point to both ends.

[0018] Furthermore, in the installed state, the thrust rolling element is positioned at the lowest point in the main thrust ramp groove, and the annular transmission component is located at the minimum working radius of the two-axis cone disk unit.

[0019] Furthermore, the elastic coefficient of the first elastic component is greater than that of the third elastic component, and the elastic coefficient of the third elastic component is greater than that of the second elastic component; in the assembled state, the system preload of the annular transmission component and the first-axis conical disk unit and the second-axis conical disk unit is provided by the torque unit.

[0020] Furthermore, the angles of the secondary thrust ramp and the primary thrust ramp satisfy the following relationship:

[0021]

[0022] In the above formula, i is the transmission speed ratio; R1 is the rolling working radius of the annular transmission component on the first shaft; R2 is the rolling working radius of the annular transmission component on the second shaft; a1 is the cone angle of the conical disk; μ is the friction coefficient between the annular transmission component and the conical disk; σ is the thrust ratio required to transmit torque between the first and second shafts, and the value of σ is monotonically negatively correlated with the transmission speed ratio i; Rt η is the radius of rotation of the thrust rolling element around the second shaft; a2 is the continuously changing angle of the auxiliary thrust ramp and the main thrust ramp; η is the efficiency of the thrust provided by the thrust unit being transmitted to the first shaft through the annular transmission component.

[0023] The beneficial effects of this utility model are as follows:

[0024] 1. By setting an axial limiting part on a single-axis moving cone disk, the impact damage to the annular transmission component caused by sudden torque changes is avoided with a simple structure;

[0025] 2. By setting an axial limiting part on the one-axis moving cone disk, the mechanical efficiency of transmitting small torque is improved and mechanical wear is reduced;

[0026] 3. By setting an axial limiting part on the one-axis moving cone disk, frequent speed adjustment is avoided when transmitting small and medium-sized torque, thus improving the system reliability and smoothness.

[0027] 4. By setting up a torque unit, while providing preload to the system, it can also smoothly transmit power in both forward and reverse directions, avoiding sliding impact when switching power transmission directions;

[0028] 5. By designing different angles for the ramp pressurization track corresponding to different transmission speed ratios, mechanical efficiency and service life are improved;

[0029] 6. In the installed state, the axial limiting part of the one-shaft moving cone disk isolates the preload force provided by the first elastic component to the system. When the annular transmission component has a mechanical gap with the cone disk unit due to non-elastic elongation, normal wear, assembly, etc., there will be oscillation and impact during the process of transmitting power to compress the preload elastic component, resulting in service life and smoothness not meeting the usage requirements. This problem is solved by the third elastic component in the torque unit pushing the main torque disk to squeeze the torque rolling element to roll in the main torque ramp groove and the secondary torque ramp groove. This can overcome the torque with the same direction of power torque (this torque is greater than the anti-drag torque at the peak speed of the power source) and drive the power source to rotate until the mechanical gap is eliminated, thus avoiding oscillation and impact during the power transmission process.

[0030] Other advantages, objectives, and features of this invention will be set forth in part in the description which follows, and in part will be apparent to those skilled in the art from the following examination and study, or may be learned from practice of this invention. The objectives and other advantages of this invention can be realized and obtained through the following description. Attached Figure Description

[0031] To make the objectives, technical solutions, and advantages of this utility model clearer, the preferred embodiments of this utility model will be described in detail below with reference to the accompanying drawings, wherein:

[0032] Figure 1 This is a schematic diagram of the continuously variable transmission (CVT) device in Example 1;

[0033] Figure 2 This is a schematic diagram of the torsion unit in Example 2;

[0034] Figure 3 for Figure 2 Schematic diagram of the arrangement of the circumferential elastic components;

[0035] Figure 4 Left view of the thrust rolling element, torsion rolling element, main thrust ramp, and secondary torsion ramp;

[0036] Figure 5 Right view of the main torque disc and main torque ramp;

[0037] Figure 6 Right view of the auxiliary thrust disk and auxiliary thrust ramp;

[0038] Figure 7 This is a schematic diagram showing the relative positions of the thrust rolling element, the torque rolling element, and the axial moving cone disk with respect to the axial limiting part after the torque unit eliminates mechanical backlash by driving the power source to rotate in the installation state in Example 1.

[0039] Figure 8 This is a schematic diagram showing the relative positions of the thrust rolling element, the torsion rolling element, the one-shaft moving cone disk, and the axial limiting part when the transmission speed ratio is at its maximum in Example 1.

[0040] Figure 9 This is a schematic diagram showing the relative positions of the thrust rolling element, the torque rolling element, and the first-axis moving cone disk with respect to the axial limiting part when the vehicle's braking energy recovery outputs the maximum reverse torque in Example 1.

[0041] Figure 10 This is a schematic diagram of the continuously variable transmission (CVT) device in Example 7;

[0042] Reference numerals: 1. First shaft; 2. First shaft fixed cone disk; 3. Annular transmission component; 4. Axial limiting part; 5. First shaft moving cone disk; 6. First elastic component; 7. First support seat; 8. Second shaft; 9. Second support seat; 10. Thrust bearing; 11. Second shaft fixed cone disk; 12. Second shaft moving cone disk; 13. Torque rolling element; 14. Thrust rolling element; 15. Secondary thrust disk; 15-2 secondary thrust ramp; 15-1 main thrust ramp; 16. Third support seat; 17. Secondary elastic component; 18. Main torque disk; 18-1 main torque ramp; 18-2 secondary torque ramp; 19. Third elastic component; 20. Fourth support seat; 21. Circumferential elastic component; 22. Forward rotation direction of power source; 23. Main thrust disk; 24. Secondary torque disk. Detailed Implementation

[0043] The following specific examples illustrate the implementation of this utility model. Those skilled in the art can easily understand other advantages and effects of this utility model from the content disclosed in this specification. This utility model can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of this utility model. It should be noted that the illustrations provided in the following embodiments are only schematic representations of the basic concept of this utility model. Unless otherwise specified, the following embodiments and features can be combined with each other.

[0044] The accompanying drawings are for illustrative purposes only and are schematic diagrams, not actual pictures. They should not be construed as limiting the present invention. To better illustrate the embodiments of the present invention, some parts in the drawings may be omitted, enlarged, or reduced, and do not represent the actual product dimensions. It is understandable to those skilled in the art that some well-known structures and their descriptions may be omitted in the drawings.

[0045] In the accompanying drawings of this utility model, the same or similar reference numerals correspond to the same or similar components. In the description of this utility model, it should be understood that if terms such as "upper," "lower," "left," "right," "front," and "rear" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting this utility model. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0046] Example 1

[0047] like Figure 1 As shown, a continuously variable transmission (CVT) includes a first-shaft cone disc unit, a second-shaft cone disc unit, a thrust unit, a torque unit, and an annular transmission component 3 for transmitting power between the first-shaft cone disc unit and the second-shaft cone disc unit; wherein the first shaft 1 is connected to the power source as the drive shaft, and the second shaft 8 is the driven shaft;

[0048] The single-axis conical disk unit includes a single-axis 1, a single-axis fixed conical disk 2, and a single-axis movable conical disk 5. The single-axis fixed conical disk 2 is sleeved and fixedly connected to the single-axis 1. The single-axis movable conical disk 5 is sleeved on the single-axis 1 in a manner that allows axial movement but is circumferentially fixed, and is arranged opposite to the conical surface of the single-axis fixed conical disk 2. It also includes a first elastic component 6 sleeved and connected to the single-axis 1. The first elastic component 6 presses against the non-conical end of the single-axis movable conical disk 5 and provides thrust to the single-axis movable conical disk 5. The other end abuts against a first support seat 7 fixedly connected to the single-axis 1. It should be noted that the first... The connection between the support base 7 and the shaft 1 can be integrally manufactured, fixed with a lock nut, or other non-rotatable and non-axially movable connection methods; it also includes an axial limiting part 4 disposed between the fixed cone disk 2 and the movable cone disk 5 of the shaft, the axial limiting part 4 being fixedly connected to the shaft 1; in the assembled state, the axial limiting part 4 restricts the axial position of the movable cone disk 5 of the shaft, thereby preventing the axial force of the first elastic component 6 from acting between the annular transmission component 3 and the shaft cone disk unit, and ensuring that the annular transmission component 3 is located at the maximum working radius of the shaft cone disk unit;

[0049] The two-axis conical disk unit includes two axes 8, a two-axis fixed conical disk 11, and a two-axis movable conical disk 12. The two-axis fixed conical disk 11 includes a bushing integrally manufactured with the conical disk and is sleeved on the two axes 8 in a circumferentially rotatable manner. The outer ring of the bushing of the two-axis fixed conical disk 11 is provided with a sliding spline, and the inner ring of the two-axis movable conical disk 12 is provided with a sliding spline and is sleeved on the bushing of the two-axis fixed conical disk 11, so that the two-axis movable conical disk 12 and the two-axis fixed conical disk 11 can move axially relative to each other but are circumferentially fixed.

[0050] The non-conical end of the dual-axis fixed conical disk 11 is connected to the outer ring of the thrust bearing 10. The inner ring of the thrust bearing 10 is sleeved on the dual shaft 8 and abuts against the second support seat 9, which is fixedly connected to the dual shaft 8. This allows the dual-axis fixed conical disk 11 and the dual shaft 8 to roll relative to each other, reducing rotational friction and restricting the axial movement of the dual-axis fixed conical disk 11. It should be noted that the connection between the second support seat 9 and the dual shaft 8 can be integrally manufactured, fixed with a lock nut, or other non-rotatable and non-axially movable connection methods. The relative rotation angle between the dual-axis fixed conical disk 11 and the dual shaft 8 is the same as the relative rotation angle between the auxiliary thrust disk 15 and the dual-axis moving conical disk 12.

[0051] like Figure 1 , Figure 4 , Figure 5 , Figure 6 and Figure 7As shown, the thrust unit includes an auxiliary thrust disk 15 with an auxiliary thrust ramp groove 15-2, a thrust rolling element 14, and a second elastic component 17. The auxiliary thrust disk 15 is axially movable and circumferentially fixed to the second shaft 8, and its non-ramp end face abuts against a third support seat 16 fixedly connected to the second shaft 8. It should be noted that the connection between the third support seat 16 and the second shaft 8 can be integrally manufactured, fixed with a locking nut, or other non-rotatable and non-axially movable connection methods. The non-conical end face of the second shaft moving cone disk 12 is provided with a main thrust ramp groove 15-1 that matches the auxiliary thrust ramp groove 15-2. One end of the second elastic component 17 abuts against the end face of the auxiliary thrust disk 15 and provides pressure toward the second shaft moving cone disk 12 to the auxiliary thrust disk 15, and the other end abuts against the end face of the main torque disk 18.

[0052] Both the secondary thrust ramp 15-2 and the main thrust ramp 15-1 are V-shaped ramp structures that rise symmetrically from the middle to both ends. The secondary thrust ramp 15-2 and the main thrust ramp 15-1 are arranged symmetrically around the clamping thrust rolling body 14, so that when the secondary thrust disk 15 and the two-axis moving cone disk 12 transmit torque, they will generate axial thrust on the two-axis moving cone disk 12, and the relative rotation of the secondary thrust disk 15 and the two-axis moving cone disk 12 can provide a speed-regulating stroke for the axial movement of the two-axis moving cone disk 12. In the installed state, the thrust rolling body 14 is set at the lowest point of the secondary thrust ramp 15-2, and the annular transmission component 3 is located at the minimum working radius of the two-axis cone disk unit. In this embodiment, a total of 3 sets of secondary thrust ramps 15-2 and main thrust ramps 15-1 are provided and are evenly arranged along the circumference of the two-axis moving cone disk 12.

[0053] The torque unit includes a main torque disc 18 with a main torque ramp groove 18-1, a torque rolling element 13, and a third elastic component 19. The main torque disc 18 is connected to the second shaft 8 via an axial sliding spline. The non-conical end face of the second shaft moving cone disc 12 is provided with a secondary torque ramp groove 18-2 that matches the main torque ramp groove 18-1. In the installed state, the torque rolling element 13 is clamped in the middle position between the main torque ramp groove 18-1 and the secondary torque ramp groove 18-2. One end of the third elastic component 19 abuts against the end face of the main torque disc 18 without the main torque ramp groove 18-1, and the other end abuts against the fourth support seat 20 fixedly connected to the second shaft 8. It should be noted that the connection between the fourth support seat 20 and the second shaft 8 can be integrally manufactured, fixed with a lock nut, or other non-rotatable and non-axially movable connection methods.

[0054] Both the secondary torque ramp 18-2 and the main torque ramp 18-1 are unidirectional ramps that rise from one end to the other, and the secondary torque ramp 18-2 and the main torque ramp 18-1 are arranged symmetrically around the clamped torque rolling body 13; the third elastic component 19 drives the power source connected to the first shaft 1 to rotate forward until the mechanical clearance is eliminated by pushing the main torque disk 18 to squeeze the torque rolling body 13 to roll, and the annular transmission component 3 forms a preload between the first shaft conical disk unit and the second shaft conical disk unit.

[0055] In this embodiment, there are 3 sets of secondary torque ramp grooves 18-2 and main torque ramp grooves 18-1; the first elastic component 6 is a 7-piece stacked butterfly spring, the third elastic component 19 is a 5-piece stacked butterfly spring, and the second elastic component 17 is a 3-piece stacked butterfly spring.

[0056] i is the transmission speed ratio; R1 is the rolling working radius of the annular transmission component on the first shaft; R2 is the rolling working radius of the annular transmission component on the second shaft; a1 is the cone angle of the conical disk; μ is the coefficient of friction between the annular transmission component and the conical disk; σ is the thrust ratio required to transmit torque between the first and second shafts. The value of σ is monotonically negatively correlated with the transmission speed ratio i, as determined by experiments.

[0057] σ = 0.266 * i^ 2 -1.02*i+2.02; R t η is the radius of rotation of the thrust rolling element around the second shaft; a2 is the continuously changing angle of the auxiliary thrust ramp and the main thrust ramp; η is the efficiency of the thrust provided by the thrust unit being transmitted to the first shaft through the annular transmission component; specifically, in this embodiment, the angles of the auxiliary thrust ramp and the main thrust ramp satisfy the following relationship:

[0058]

[0059] Taking a pure electric vehicle as an example, the typical operating conditions of Example 1 are analyzed and explained:

[0060] When the vehicle is not transmitting power, the main torque disc 18 drives the dual-axis moving cone disc 12 to rotate against the resistance of the power source under the thrust of the third elastic component 19, that is, the torque rolling element 13 rolls from position X0 / Y0 to X 0+ / Y 0+ Simultaneously, the thrust rolling element 14 rolls from position M0 / N0 to M 0+ / N 0+ To eliminate mechanical clearance and provide system preload to the annular transmission component 3; in the installed state, the single-shaft moving cone disk 5 abuts against the axial limiting part 4 under the thrust of the first elastic component 6, so that the axial thrust generated by the first elastic component 6 does not act on the annular transmission component 3, and the annular transmission component 3 is at the maximum working radius of the single-shaft cone disk unit, that is, the transmission speed ratio is at its minimum (e.g. Figure 7 (as shown);

[0061] When the vehicle wheel ends require maximum torque output, the driver depresses the accelerator pedal, and the motor torque increases from zero to maximum torque. During this process, the thrust rolling element 14 will move from position M. 0+ / N 0+ Climb to position M1 / N2, and drive the torque rolling element 13 from X 0+ / Y 0+ Rolling to position X1 / Y2, simultaneously the dual-axis moving cone disk 12 pushes the annular transmission component 3 to generate a pulling force on the primary moving cone disk 5, moving it away from the axial limiting part 4, and compressing the first elastic component 6 until the annular transmission component 3 is at its minimum working radius, i.e., the system is at its maximum transmission speed ratio, achieving maximum torque output at the wheel end (e.g., Figure 8 (as shown);

[0062] When the vehicle decelerates and transmits maximum torque in the reverse direction, this condition consists of two processes. In the first process, the motor torque decreases from maximum to zero. During this process, the first-axis moving cone disk 5 moves axially under the action of the first elastic component 6 until its movement is restricted by the axial limiting part 4. At the same time, the third elastic component 19 is compressed and absorbs energy. That is, the axial limiting part 4 and the torque unit can prevent the rapid decrease in torque from causing impact damage to the annular transmission component 3. At the same time, the thrust rolling element 14 will fall back from position M1 / N2 to position M. 0+ / N 0+ Torque rolling element 13 rolls from X1 / Y2 to position X 0+ / Y 0+ At this time, the annular transmission component 3 is at its maximum working radius, and the transmission ratio is at its minimum (e.g., Figure 7 (As shown); In the second process, the motor torque increases from zero until the maximum reverse torque is output. During this process, the thrust rolling element 14 will move from position M. 0+ / N 0+ Climb to position M2 / N1, and drive the torque rolling element 13 from X 0+ / Y 0+ As the device rolls to position X2 / Y1, the dual-axis moving cone disk 12 simultaneously pushes the annular transmission component 3, generating a pulling force that acts on the primary moving cone disk 5 away from the axial limiting part 4, and compresses the first elastic component 6 until the annular transmission component 3 is at its minimum working radius (e.g., ...). Figure 9 (As shown).

[0063] Example 2

[0064] like Figure 2 As shown, this embodiment is an alternative structure for the torque unit. The difference from embodiment 1 is that the torque unit uses a circumferential elastic component 21 between the main torque disk 18 and the dual-axis moving cone disk 12 to replace the auxiliary torque ramp groove 18-2, the torque rolling element 13 and the main torque ramp groove 18-1, thereby providing a positive rotation torque to the power source. Figure 3 This is a schematic diagram showing the connection arrangement of the circumferential elastic component 21 between the main torsion disk 18 and the dual-axis moving cone disk 12.

[0065] Example 3

[0066] This embodiment discloses an electric drilling machine equipped with the continuously variable transmission device of Embodiment 1. The first shaft 1 is connected to the output end of the electric drilling machine motor, and the second shaft 8 is connected to the drill bit end of the electric drilling machine. The transmission speed ratio is automatically adjusted by the torque change of the drilling load.

[0067] Example 4

[0068] This embodiment discloses a three-wheeled or two-wheeled electric motorcycle equipped with the continuously variable transmission device of Embodiment 1. The first shaft 1 is connected to the power source output end, and the second shaft 8 is connected to the wheel end. By changing the torque of the power source, the transmission ratio can be adaptively adjusted.

[0069] Example 5

[0070] This embodiment discloses a wind turbine gearbox equipped with the continuously variable transmission device of Embodiment 1. The second shaft 8 is connected to the shaft on which the wind turbine (blades) is installed, and the first shaft 1 is connected to the shaft on which the generator is installed. The torque when the wind turbine rotates can be amplified by the continuously variable transmission in this embodiment, thereby reducing the minimum wind speed for starting the generator.

[0071] Example 6

[0072] This embodiment discloses an electric cutting machine equipped with the continuously variable transmission device of Embodiment 1. The second shaft 8 is connected to the output shaft of the cutting machine, and the first shaft 1 is connected to the motor shaft of the cutting machine. When the cutting resistance increases and the motor outputs a large torque, the transmission ratio of the continuously variable transmission device in Embodiment 1 will increase to output a larger torque to ensure the continuous operation of the cutting machine.

[0073] It should be noted that the embodiments are only used to illustrate the technical solutions of this utility model and are not intended to limit it. Although this utility model has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions to the technical solutions of this utility model without departing from the spirit and scope of this technical solution should all be covered within the scope of the claims of this utility model.

[0074] Example 7

[0075] like Figure 10 As shown, the difference between this embodiment and Embodiment 1 is that a main thrust disk 23 and a secondary torque disk 24 are respectively provided on the end face of the non-conical side of the dual-axis moving cone disk, and the main thrust disk 23 and the secondary torque disk 24 are coaxially and fixedly connected to the dual-axis moving cone disk 12; and the... Figure 4The main thrust ramp 15-1 and the secondary torque ramp 18-2 are respectively mounted on the main thrust disk 23 and the secondary torque disk 24. The value of this structure lies in designing and manufacturing the two-axis moving cone disk 12 with different adaptation requirements as common components as possible to achieve greater cost advantages in large-scale production.

Claims

1. A continuously variable transmission (CVT) device, comprising a primary shaft conical disc unit, a secondary shaft conical disc unit, an annular transmission component, and a first elastic component sleeved and connected to a primary shaft; the primary shaft conical disc unit comprises a primary shaft and a primary shaft fixed conical disc and a primary shaft movable conical disc arranged coaxially with their conical surfaces opposite each other; the primary shaft fixed conical disc is fixedly sleeved and connected to the primary shaft, the primary shaft movable conical disc is sleeved on the primary shaft in a circumferentially fixed and axially sliding manner, and the first elastic component presses against the non-conical end of the primary shaft movable conical disc and provides thrust to the primary shaft movable conical disc; the secondary shaft conical disc unit comprises two shafts and a secondary shaft fixed conical disc and a secondary shaft movable conical disc arranged with their conical surfaces opposite each other, the secondary shaft fixed conical discs are sleeved on the secondary shafts in a manner that allows them to rotate relative to each other and are fixed in at least one axial direction, and the secondary shaft movable conical discs are sleeved on the secondary shaft fixed conical discs in a circumferentially fixed and axially sliding manner; the primary shaft is connected to a power source, characterized in that: It also includes an axial limiting part disposed between a fixed cone disk and a movable cone disk, the axial limiting part being fixedly connected to a shaft; in the assembled state, the axial limiting part prevents the axial force of the first elastic component from acting on the annular transmission component by limiting the axial position of the movable cone disk, and realizes that the annular transmission component is at the maximum working radius of the cone disk unit. It also includes a torque unit mounted on the two shafts, the torque unit including a main torque disc that is axially sliding and circumferentially fixed on the two shafts; in the installed state, the main torque disc is used to provide a positive rotational torque to the power source and to provide a preload force to the annular transmission component.

2. The continuously variable transmission (CVT) device according to claim 1, characterized in that: The non-conical end face of the dual-axis moving cone disk is provided with a secondary torque disk and a main thrust disk, which are coaxially and fixedly connected to the dual-axis moving cone disk.

3. The continuously variable transmission (CVT) device according to claim 2, characterized in that: The torque unit further includes a torque rolling element and a third elastic component; The main torque disk is arranged on one side of the non-conical end of the dual-axis moving cone disk, and the main torque ramp groove and the auxiliary torque ramp groove are respectively provided in the circumferential direction of the main torque disk and the auxiliary torque disk, which are symmetrically distributed around the center to hold the torque rolling body. The main torque ramp groove and the auxiliary torque ramp groove are both unidirectional ramp grooves that rise from one end to the other. One end of the third elastic component abuts against the end face of the main torque disc on the side opposite to the main torque ramp groove and provides axial pressure toward the auxiliary torque disc to the main torque disc.

4. The continuously variable transmission (CVT) device according to claim 3, characterized in that: At least two sets of secondary torque ramps and primary torque ramps are provided, evenly distributed along the circumference; in the assembled state, the torque rolling element is positioned in the middle of the secondary torque ramp.

5. A continuously variable transmission (CVT) device according to claim 4, characterized in that: It also includes a thrust unit disposed on the two shafts. The thrust unit includes an auxiliary thrust disk and a thrust rolling element. The auxiliary thrust disk is disposed on the non-conical side of the two-shaft moving cone disk and is connected to the two shafts in a circumferentially fixed and axially movable manner. The auxiliary thrust disk and the main thrust disk are respectively provided with auxiliary thrust ramp grooves and main thrust ramp grooves that are centrally symmetrical to clamp the thrust rolling element. This allows the auxiliary thrust disk to generate axial thrust on the two-shaft moving cone disk when transmitting torque, and to form the clamping force required for the annular transmission component to transmit torque. Furthermore, the axial travel generated by the mutual rotation between the auxiliary thrust disk and the two-shaft moving cone disk matches the axial travel required for the speed adjustment of the two-shaft moving cone disk.

6. A continuously variable transmission (CVT) device according to claim 5, characterized in that: The thrust unit further includes a second elastic component, which is sleeved on the second shaft and arranged on the side of the auxiliary thrust disk away from the second shaft moving cone disk, so as to provide an axial thrust to the auxiliary thrust disk in the direction of the second shaft moving cone disk, and the end face of the auxiliary thrust disk away from the second shaft moving cone disk abuts against a third support fixedly connected to the second shaft.

7. A continuously variable transmission (CVT) device according to claim 6, characterized in that: At least two sets of secondary thrust ramps and main thrust ramps are evenly distributed along the circumference of the secondary thrust disk, and both the secondary thrust ramps and main thrust ramps are V-shaped slope groove structures that rise symmetrically from the low point to both ends.

8. A continuously variable transmission (CVT) device according to claim 7, characterized in that: In the installed state, the thrust rolling element is positioned at the lowest point in the main thrust ramp groove, and the annular transmission component is located at the minimum working radius of the two-axis cone disk unit.

9. A continuously variable transmission (CVT) device according to claim 8, characterized in that: The elastic coefficient of the first elastic component is greater than that of the third elastic component, and the elastic coefficient of the third elastic component is greater than that of the second elastic component; in the assembled state, the system preload of the annular transmission component and the first-axis conical disk unit and the second-axis conical disk unit is provided by the torque unit.

10. A continuously variable transmission (CVT) device according to claim 9, characterized in that: The angles of the secondary thrust ramp and the main thrust ramp satisfy the following relationship: In the above formula, i is the transmission speed ratio; The rolling working radius of the annular transmission component on one shaft; The rolling working radius of the annular transmission component on the two shafts; The coefficient of friction between the annular transmission component and the conical disk; This is the thrust ratio required to transmit torque between the first and second shafts. The value is monotonically negatively correlated with the transmission ratio i. The radius of rotation of the body about two axes; The angles of the continuously changing secondary thrust ramp and main thrust ramp; The efficiency of transmitting the thrust provided to the thrust unit to the shaft through the annular transmission component.

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